COMPRESSION SOURCINGCOMPRESSION SOURCING 2017 TECHNOLOGY SUPPLEMENT TECHNOLOGY SUPPLEMENT Ratings Ratings••Specs Specs••Information Information The TheIndustry’s Industry’sLeading LeadingReference ReferenceTool ToolFor ForPackagers, Packagers, Purchasers PurchasersAnd AndTraining TrainingProviders Providers CTSSnet.net CTSSnet.net COMPRESSION COMPRESSION TECHNOLOGY TECHNOLOGY SOURCING SOURCING SUPPLEMENT SUPPLEMENT COMPRESSOR COMPRESSOR Dedicated Dedicated To Gas To Gas Compression Compression Products Products & Applications & Applications Technology That Transforms. Gas Compression Ratings Gross Horsepower (kW) w/o Fan E NGINE C ONTINUOUS R ATING HP ( K W) @ RPM M ODEL C/R 1200 1500 1800 2200 10.5:1 – – 49 (37) – G5.9 (2, 4, 6) 10.5:1 – – 84 (63) 99 (74) GTA5.9 (3) 8.5:1 – – 116 (87) – 10.5:1 – – 99 (74) – G8.3 (2, 4, 6) 10.5:1 – 99 (74) 118 (88) 135 (101) 8.5:1 – – 175 (130) – GTA8.3 (3) 8.5:1 – – 190 (142) – GTA8.3SLB (3, 5) 8.5:1 – 145 (108) 175 (130) – QSL9G (1, 4) 9.7:1 – – 175 (130) – G855 (2, 4) 10:1 – 157 (117) 188 (140) – G855E (1, 4) 10:1 – 157 (117) 188 (140) – GTA855 (2, 4) 8.5:1 – – 225 (168) – 8.5:1 – – 225 (168) – GTA855E (1, 4) 8.5:1 – – 256 (191) – GTA855 (3) 8.5:1 – 238 (177) 286 (213) – KTA19GCE (2, 4) 8.5:1 265 (198) – – – KTA19GCE (2, 4, 6) 8.5:1 – – 380 (283) – KTA19GCE (3) 8.5:1 – – 420 (313) – Notes (1) COMPLIANT-CAPABLE – This engine is capable of meeting the SI NSPS regulations from the factory. However, the owner/operator is required to conduct site compliance testing and submit documentation per the EPA SI NSPS requirements. Engines with the “E” designation include a factory-supplied air/fuel ratio controller and a Cummins Emission Solutions Three-Way Catalyst (TWC). (2) CUSTOMER-COMPLIANT UPGRADEABLE – This engine is capable of operating with a TWC at this rating. It is the responsibility of the owner/operator to upgrade the engine with an air/fuel ratio controller and a TWC capable of meeting the SI NSPS regulations. The owner/operator is required to conduct site compliance testing and submit documentation per the EPA SI NSPS requirements. (3) This engine is not capable of meeting the EPA SI NSPS regulations, and is offered only for use outside the U.S. (4) Catalyst rating. (5) This engine emits 2.0 gr/hp-hr NOx, 4.0 gr/hp-hr CO, 1.0 gr/hp-hr VOC. This engine does not meet the revised EPA SI NSPS requirements for non-emergency engines, and is offered only for use outside the U.S. (6) Factory integrated Murphy Engine Integrated Control System (EICS) available. In the gas compression industry, you need an engine that will run every minute of every day for years. That’s Cummins. We offer a full lineup of naturally aspirated and turbocharged gas-fueled engines. Every engine is built with many of the same rugged components used in our high-compression diesel engines, and is backed by the dependable parts and service capabilities of Cummins worldwide distribution network. To learn more, contact your local Cummins distributor, call us at 1-800-268-6467 or visit our web site at CumminsOilandGas.com. ©2017 Cummins Inc., Box 3005, Columbus, IN 47202-3005 U.S.A. 2017 COMPRESSION SOURCING PUBLICATION STAFF TECHNOLOGY SUPPLEMENT Associate Publisher ................... Mark Thayer Senior Editor ................................... DJ Slater CONTENTS Senior Editor ................. Michael J. Brezonick n Index To Manufacturers’ Sections And Products ................................3 Associate Editor ........................... Klinton Silvey n Product Directory and Buyers’ Guide ...............................................16 Associate Editor ............................... Jack Burke Associate Editor ............................Chad Elmore Copy Editor ............................... Jerry Karpowicz COMPRESSORS Publication Manager .................. Katie Bivens Including: Centrifugal, Reciprocating And Rotary Compressors Circulation Manager ...................... Sue Smith And Turboexpanders Graphic Artist ...........................Brenda Burbach n Centrifugal Compressor Specifications ............................................33 Graphic Artist .................................Carla Lemke n Turboexpander Specifications .........................................................41 Graphic Artist ............................... Alyssa Loope n Reciprocating & Rotary Compressor Specifications .........................44 PUBLICATION HEADQUARTERS n Tech Brief: Compressors And Expanders .........................................71 20855 Watertown Road, Suite 220 n SI Units… The International Standards System ...............................132 Waukesha, Wisconsin 53186-1873 Telephone: (262) 754-4100 Fax: (262) 754-4175 n Conversion Factors SI – Metric/Decimal System ............................133 HOUSTON, USA PRIME MOVERS Mark Thayer, Associate Publisher 12777 Jones Road, Suite 225 Including: Reciprocating Engines, Turbines And Electric Motors Houston, Texas 77070 n Natural Gas Engine Specifications .................................................145 Telephone: (281) 890-5287 n Mechanical Drive Gas Turbine Specifications .................................149 GERMANY n Mechanical Drive Steam Turbine Specifications .............................153 Lisa Hochkofler, Advertising Manager n Electric Motor Specifications ........................................................155 Gabriele Dinsel, Advertising Manager n Variable Speed Drive Specifications ..............................................157 Niemöllerstr. 9 73760 Ostfildern, Germany n Tech Brief: Prime Movers For Mechanical Drives ...........................162 Telephone: +49 711 3416 74 0 Fax: +49 711 3416 74 74 UNITED KINGDOM INSTRUMENTATION & CONTROLS Ian Cameron, Regional Manager/Editor Including: Monitoring And Engineering Services Linda Cameron, Advertising Manager n Tech Brief: Un-Balancing Act ........................................................193 40 Premier Avenue Ashbourne, Derbyshire, DE6 1LH, United Kingdom Telephone: +44 20 31 79 29 79 Fax: +44 20 31 79 29 70 COMPONENTS Including: Heat Exchangers, Lubrication, Filters, Seals, Valves, Etc. ITALY n Tech Brief: Nontraditional Vibration Mitigation Methods Roberta Prandi, Regional Manager/Editor For Reciprocating Compressor Systems .....................................202 Via Cerere 18 38062 Arco, Italy n Tech Brief: Slow Rolling Centrifugal Compressors ..........................210 Telephone: +39 0464 014421 n Tech Brief: Lube Reduction In Reciprocating Compressors ............212 SWEDEN Bo Svensson, Field Editor/Business Manager SYSTEM REPAIR Dunderbacksvagen 20 Including: Overhaul And Service 612-46 Finspong, Sweden n Tech Brief: Case Study: Packing Vent Monitoring ..........................218 Telephone: +46 70 2405369 Fax: +46 122 14787 n Tech Brief: Creating The Perfect Impeller Shape By Scalloping ......228 JAPAN n Compressor Horsepower Selection Chart ......................................229 Akiyoshi Ojima, Branch Manager 51-16-301 Honmoku Sannotani, Naka-ku Yokohama, 231-0824 Japan PACKAGERS Telephone: +81 45 624 3502 Fax: +81 45 624 3503 Including: Compression And Power Generation n Packager Guide 2017 ...................................................................233 KOREA D. S. Chai, Sales Manager n Directory Of Advertisers ...............................................................240 Dongmyung Communications Inc. Published March 2017 by Diesel & Gas Turbine Publications, 20855 Watertown Road, Suite 220, 82 Pyeongchangmunhwa-ro, Jongno-gu Waukesha, WI 53186-1873, USA. Copyright 2017. All Rights Reserved. This book or parts thereof may Seoul, 03011 Korea not be reproduced in any form without written permission of the Publisher. Telephone: +82 2 391 4254 Fax: +82 2 391 4255 Additional copies of the COMPRESSION TECHNOLOGY SOURCING SUPPLEMENT are available for DIESEL & GAS TURBINE PUBLICATIONS $35.00/copy postpaid. Send order to the Publisher’s Circulation Office: 20855 Watertown Road, Suite President ................................. Michael J. Osenga 220, Waukesha, WI 53186-1873, USA. When ordering from outside the United States, remit in U.S. funds. Executive Vice President ....Michael J. Brezonick Printed in USA. 2017 EDITION 1 WWW.CTSSNET.NET CTSS 2016 EDITION XX WWW.CTSSNET.NET CTSS INDEX TO MANUFACTURERS’ SECTIONS AND PRODUCTS A ATLAS COPCO (SHANGHAI) PROCESS EQUIPMENT CO. LTD. .........................140, 141 ANDREAS HOFER 16F China Venturetech Plaza HOCHDRUCKTECHNIK No.819 GMBH .............................142, 143 ATLAS COPCO GAS Nanjing West Road Ruhrorter Str. 45 AND PROCESS ..............140, 141 Shanghai, 200041 45478 Mülheim an der Ruhr Schlehenweg 15 CHINA GERMANY 50999 Cologne Tel: +86 021 22 08 48 76 Phone: +49 208 469 96-0 GERMANY Fax: +86 021 62 15 19 63 Fax: +49 208 469 96-11 Phone: +49 2236 9650 0 Email: atlascopco.energas@ For Product Listing Email:
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MIDC. Phone: +66 38 923 700 Compressors, Stationary Services, Engineering Fax: +66 38 896 182/3 Consulting Services, Failure-Analysis Email:
[email protected] Cylinder Lubrication Systems Website: www.neuman-esser.com Packages, Engine Compressor Packages, Engineering & Design Compressor Sets, Electrically Packages, Foundation, Platform Engine-Driven Deck, FPSO Module Design Compressors, Capacity Control SOLAR TURBINES INCORPORATED Packages, Motor Compressor Devices ................... PRIME MOVERS TAB Project Management Compressors, Diaphragm 9330 Sky Park Court Services & Training Compressors, Gas Mail Zone SP4-B Services, Compressors Overhaul Compressors, Oil-Free San Diego, California 92123 & Repair USA Compressors, Oil-Injected Services, Divider Block Lubrication Phone: +1 858-694-2444 Compressors, Piston Systems Fax: +1 619-544-2444 Compressors, Reciprocating Services, Engineering Email:
[email protected] Compressors, Skid-Mounted Services, Failure-Analysis Website: www.solarturbines.com Packages, Engineering & Design Packages, Piping, Structural Analysis S Compressor Sets, Gas Turbine- Packing Assemblies Driven Compressors, Centrifugal Compressors, Gas P SIAD MACCHINE IMPIANTI S.P.A. Engine Maintenance, Overhaul & COMPRESSORS DIVISION ....117 Parts Services Via Canovine 2/4 Engines, Gas Turbine 24126 Bergamo Packages, Engine Compressor PSE ENGINEERING GMBH ITALY Packages, Foundation, Platform COMPRESSION SYSTEMS Phone: +39 035 327611 Deck, FPSO Module Design ........................ PACKAGERS TAB Fax: +39 035 316131 Service Systems & Training, Gas Ahrensburger Strasse 1 Email:
[email protected] Turbines 30659 Hannover Website: www.siadmi.com Services & Training GERMANY Services, Compressors Overhaul Phone: +49 (0) 511 2614-20-0 Compressor Frame End Parts & Repair Fax: +49 (0) 511 2614-20-11 Compressor Sets, Electrically Services, Gas Turbine Overhaul Email:
[email protected] Engine-Driven & Repair Website: www.pse-eng.de Compressor Sets, Natural Gas Engine-Driven Compressor Condition Monitoring Compressors, Air STASSKOL GMBH ..............142, 143 Compressor Sets, Electrically Compressors, Gas Maybachstrasse 2 Engine-Driven Compressors, Oil-Free 39418 Stassfurt Compressor Sets, Natural Gas Compressors, Oil-Injected GERMANY Engine-Driven Compressors, Piston Phone: +49 3925 288 100 Compressors, Gas Compressors, Reciprocating Fax: +49 3925 288 105 Compressors, Oil-Free Compressors, Reconditioned Email:
[email protected] Compressors, Oil-Injected Compressors, Skid-Mounted Website: www.stasskol.de Compressors, Piston Compressors, Stationary Compressors, Portable Cylinders, Reconditioning Packings, Intermediate Compressors, Reciprocating Services & Training Packings, Oil Wiper Compressors, Reconditioned Services, Compressors Overhaul Packings, Piston Rod Compressors, Skid-Mounted & Repair Rings, Compressor 2017 EDITION 14 WWW.CTSSNET.NET CTSS Rings, Floating-Sealing For Product Listing VOITH TURBO INC. ....................113 Rings, Guide See Voith Turbo BHS Getriebe 11700 Katy Freeway Rings, Packing GmbH Energy Tower, Suite 250 Rings, Piston Houston, Texas 77079 Rings, Rider USA VOITH TURBO BHS Email: www.voith.com/vsd Rings, Sealing GETRIEBE GMBH ..................113 Website:
[email protected] Rings, Wiper Hans-Boeckler-Strasse 7 Seals, Shaft 87527 Sonthofen Sleeves, Shaft Actuators, Electric GERMANY Valves, Overhaul Actuators, Hydraulic Phone: +49 8321 802 0 Controls, Compressor Fax: +49 8321 802 689 Controls, Fuel Consumption Email:
[email protected] STASSKOL INC. ..................142, 143 Controls, Speed Website: www.voith.com/bhs 19911 Morton Road, Suite 200 Converters, Torque Katy, Texas 77449 Couplings, Flexible Bearings, Journal or Sleeve Type USA Couplings, Fluid Phone: +1 713 384-9489 Bearings, Tilting Pad Couplings, Gear-Type Fax: +1 713 384-0 Couplings, Diaphragm Couplings, Shaft Email:
[email protected] Couplings, Gear-Type Drives, Compressor Website: www.stasskol.com Couplings, Shaft Drives, Turbine Starting Drives, Gear Reduction Drives, Variable-Speed Packings, Intermediate Gear Systems Gears, Turbo Packings, Oil Wiper Gearboxes Services & Training Packings, Piston Rod Gears, Custom Servo Motors Rings, Compressor Gears, Epicyclic Shafts Rings, Floating-Sealing Gears, Helical Torque Converters Rings, Guide Gears, Increasers Rings, Packing Gears, Ring Rings, Piston Gears, Spur Z Rings, Rider Gears, Stationary Rings, Sealing Gears, Stationary/Industrial Drive Rings, Wiper Gears, Turbo Seals, Shaft Reducers, Gear ZOLLERN BHW GLEITLAGER Rotor Turning Gears Sleeves, Shaft GMBH & CO. KG Services & Training Valves, Overhaul PLAIN BEARING TECHNOLOGY ................226, 227 V Alte Leipziger Straße 117-118 VOITH TURBO GMBH & CO. KG 38124 Braunschweig INDUSTRY ...............................113 GERMANY Voithstrasse 1 Phone: +49 (5522) 3127-0 74564 Crailsheim Fax: +49 (5522) 3127-99 VOITH TURBO USA ....................113 GERMANY Email:
[email protected] 4357 Ferguson Drive Phone: +49 7951 32 0 Cincinnati, Ohio 45245 Fax: +49 7951 32 500 USA Email:
[email protected] Bearing Shells Phone: +1 513-797-8101 Website: www.voithturbo.com Bearings, Journal or Sleeve Type Fax: +1 513-797-8103 Bearings, Thrust Email:
[email protected] For Product Listing Bearings, Tilting Pad Website: www.usa.voithturbo.com See Voith Turbo Inc. Bushings 2017 EDITION 15 WWW.CTSSNET.NET CTSS PRODUCT DIRECTORY AND BUYERS’ GUIDE A AIR/FUEL RATIO CONTROLS Voith Turbo BHS HOERBIGER .................. 134, 135 Getriebe GmbH .................... 113 ACOUSTICAL PULSATION ZOLLERN BHW ANALYSIS ANALYSIS, SOFTWARE Gleitlager GmbH & Co. KG COMOTI - Romanian Research BORSIG ZM Plain Bearing & Development Compression GmbH ............ 119 Technology .................. 226, 227 Institute for Gas Turbines .... 123 APPARATUS BLADES & NOZZLES, HOERBIGER .................. 134, 135 CONSTRUCTION GAS TURBINES ACTUATORS, ELECTRIC MAN Diesel & Turbo SE COMOTI - Romanian Research & ...................................... 138, 139 Cozzani, Dott. Ing. Development Mario Cozzani Srl ................ 217 Institute for Gas Turbines .... 123 Dott. Ing Mario Cozzani Srl .... 217 B HOERBIGER .................. 134, 135 Voith Turbo Inc. ...................... 113 BEARING SHELLS BLADES, ROTARY ZOLLERN BHW COMPRESSOR ACTUATORS, Gleitlager GmbH & Co. KG ELECTRIC AIR FLSmidth Inc. Plain Bearing HOERBIGER .................. 134, 135 Pneumatic Transport ..... 125, 129 Technology .................. 226, 227 HOERBIGER .................. 134, 135 ACTUATORS, BEARINGS, JOURNAL Mitsubishi Heavy Industries HYDRAULIC OR SLEEVE TYPE Compressor International HOERBIGER .................. 134, 135 Voith Turbo BHS ...................................... 127, 201 Voith Turbo Inc. ...................... 113 Getriebe GmbH .................... 113 ZOLLERN BHW BLADES, TURBINE ACTUATORS, PNEUMATIC Gleitlager GmbH & Co. KG HOERBIGER .................. 134, 135 Cozzani, Dott. Ing. Plain Bearing Technology .................. 226, 227 Mitsubishi Heavy Industries Mario Cozzani Srl ................ 217 Compressor Dott. Ing Mario Cozzani Srl .... 217 BEARINGS, THRUST International ................. 127, 201 ZOLLERN BHW ACTUATORS, SOLENOID BLADES, Gleitlager GmbH & Co. KG Cozzani, Dott. Ing. TURBOCHARGER Plain Bearing Mario Cozzani Srl ................ 217 Technology .................. 226, 227 HOERBIGER .................. 134, 135 Dott. Ing Mario Cozzani Srl .... 217 BEARINGS, TILTING PAD BLOWERS ADAPTERS, COMOTI - Romanian Research COMOTI - Romanian Research INDICATOR VALVE & Development & Development HOERBIGER .................. 134, 135 Institute for Gas Turbines .... 123 Institute for Gas Turbines .... 123 2017 EDITION 16 WWW.CTSSNET.NET CTSS BUSHINGS HOERBIGER .................. 134, 135 NEUMAN & ESSER ZOLLERN BHW PSE Engineering GmbH Italia S.r.l. ..................... 142, 143 Gleitlager GmbH & Co. KG Compression Systems NEUMAN & ESSER Plain Bearing ............................ Packagers Tab RUS Ltd. ...................... 142, 143 Technology .................. 226, 227 NEUMAN & ESSER COMPRESSOR CYLINDER & South East Asia Ltd. .... 142, 143 PACKING LUBRICATION C HOERBIGER .................. 134, 135 NEUMAN & ESSER USA Inc. ....................... 142, 143 CASTINGS, CENTRIFUGAL COMPRESSOR DIVIDER NEUMAN & ESSER América Mitsubishi Heavy Industries BLOCK LUBRICATION do Sul Ltda. ................. 142, 143 Compressor International SYSTEMS NEUMAN & ESSER ...................................... 127, 201 FLSmidth Inc. Engineering (India) Pneumatic Transport ......125, 129 Pvt. Ltd. ........................ 142, 143 CASTINGS, COMPRESSOR PSE Engineering GmbH COMPRESSOR FRAME Mitsubishi Heavy Industries Compression Systems END PARTS Compressor International ............................ Packagers Tab ...................................... 127, 201 HOERBIGER .................. 134, 135 SIAD Macchine Impianti S.p.A. SIAD Macchine Impianti S.p.A. Compressors Division .......... 117 CASTINGS, TURBINE Compressors Division .......... 117 COMPONENT COMPRESSOR SETS, COMPRESSOR SETS, Mitsubishi Heavy Industries GAS TURBINE-DRIVEN ELECTRICALLY Compressor International COMOTI - Romanian Research ENGINE-DRIVEN ...................................... 127, 201 & Development Andreas Hofer Institute for Gas Turbines .... 123 CHILLERS Hochdrucktechnik GmbH ...................................... 142, 143 MAN Diesel & Turbo SE GEA Refrigeration Italy ...................................... 138, 139 Oil & Gas ............................. 237 BORSIG ZM Compression GmbH ............ 119 Mitsubishi Heavy Industries Compressor International COMPONENT COMOTI - Romanian Research ...................................... 127, 201 RECONDITIONING & Development Institute for Gas Turbines .... 123 Solar Turbines Incorporated Cozzani, Dott. Ing. .......................Prime Movers Tab Mario Cozzani Srl ................ 217 GEA Refrigeration Italy Dott. Ing Mario Cozzani Srl .... 217 Oil & Gas ............................. 237 COMPRESSOR SETS, HOERBIGER .................. 134, 135 Hofer Kompressoren ...... 142, 143 NATURAL GAS MAN Diesel & Turbo SE ENGINE-DRIVEN Mitsubishi Heavy Industries Compressor International ...................................... 138, 139 BORSIG ZM ...................................... 127, 201 Mitsubishi Heavy Industries Compression GmbH ............ 119 Compressor International COMOTI - Romanian Research COMPRESSOR CONDITION ...................................... 127, 201 & Development MONITORING NEUMAN & ESSER Institute for Gas Turbines .... 123 BORSIG ZM (Beijing) Co. Ltd. .......... 142, 143 GEA Refrigeration Italy Compression GmbH ............ 119 NEUMAN & ESSER Oil & Gas ............................. 237 COMOTI - Romanian Research Deutschland GmbH Mitsubishi Heavy Industries & Development & Co. KG Vertrieb und Compressor International Institute for Gas Turbines .... 123 Anlagentechnik ............ 142, 143 ...................................... 127, 201 2017 EDITION 17 WWW.CTSSNET.NET CTSS NEUMAN & ESSER Kobelco Compressors NEUMAN & ESSER (Beijing) Co. Ltd. .......... 142, 143 America Inc. ........... Fourth Cover América do Sul Ltda. ... 142, 143 NEUMAN & ESSER Leobersdorfer NEUMAN & ESSER América do Sul Ltda. ... 142, 143 Maschinenfabrik (LMF) 136, 137 Deutschland GmbH NEUMAN & ESSER & Co. KG Vertrieb und MAN Diesel & Turbo SE Deutschland GmbH Anlagentechnik ............ 142, 143 ...................................... 138, 139 & Co. KG Vertrieb und NEUMAN & ESSER Mitsubishi Heavy Industries Anlagentechnik ............ 142, 143 Gulf FZE ...................... 142, 143 Compressor International NEUMAN & ESSER ...................................... 127, 201 NEUMAN & ESSER Italia S.r.l. ..................... 142, 143 NEUMAN & ESSER Italia S.r.l. ..................... 142, 143 NEUMAN & ESSER (Beijing) Co. Ltd. .......... 142, 143 NEUMAN & ESSER RUS Ltd. ...................... 142, 143 NEUMAN & ESSER South East Asia Ltd. .... 142, 143 NEUMAN & ESSER América do Sul Ltda. ... 142, 143 NEUMAN & ESSER USA Inc. ....................... 142, 143 NEUMAN & ESSER USA Inc. ....................... 142, 143 Deutschland GmbH NEUMAN & ESSER NEUMAN & ESSER & Co. KG Vertrieb und Engineering (India) Anlagentechnik ............ 142, 143 Engineering (India) Pvt. Ltd. Pvt. Ltd. ........................ 142, 143 ...................................... 142, 143 NEUMAN & ESSER PSE Engineering GmbH Egypt Ltd. ..................... 142, 143 Compression Systems COMPRESSORS, ............................ Packagers Tab NEUMAN & ESSER CENTRIFUGAL Italia S.r.l. ..................... 142, 143 SIAD Macchine Impianti S.p.A. BORSIG ZM Compressors Division ............... 117 NEUMAN & ESSER Compression GmbH ............ 119 RUS Ltd. ...................... 142, 143 COMOTI - Romanian Research COMPRESSOR VALVE NEUMAN & ESSER & Development CONDITION MONITORING USA Inc. ....................... 142, 143 Institute for Gas Turbines .... 123 COMOTI - Romanian Research NEUMAN & ESSER Elliott Group & Development Engineering (India) Pvt. Ltd. ................. Third Cover, 115, 192 Institute for Gas Turbines .... 123 ...................................... 142, 143 GEA Refrigeration Italy HOERBIGER .................. 134, 135 SIAD Macchine Impianti S.p.A. Oil & Gas ............................. 237 Compressors Division .......... 117 Kobelco Compressors COMPRESSORS, AIR America Inc. .......... Fourth Cover Andreas Hofer COMPRESSORS, MAN Diesel & Turbo SE Hochdrucktechnik GmbH AIR-STARTING ...................................... 142, 143 ...................................... 138, 139 Elliott Group Atlas Copco Gas ................. Third Cover, 115, 192 Mitsubishi Heavy Industries and Process ................. 140, 141 Compressor International COMPRESSORS, AXIAL ...................................... 127, 201 BORSIG ZM MAN Diesel & Turbo SE Solar Turbines Incorporated Compression GmbH ............ 119 ...................................... 138, 139 .......................Prime Movers Tab COMOTI - Romanian Research & Development COMPRESSORS, CAPACITY Institute for Gas Turbines .... 123 COMPRESSORS, CONTROL DEVICES DIAPHRAGM Corken Inc. Cozzani, Dott. Ing. Andreas Hofer A Unit of IDEX Corporation ...................................... 238, 239 Mario Cozzani Srl ................ 217 Hochdrucktechnik GmbH FLSmidth Inc. Dott. Ing Mario Cozzani Srl .... 217 ...................................... 142, 143 Pneumatic Transport ... 125, 129 HOERBIGER .................. 134, 135 Hofer Kompressoren ...... 142, 143 2017 EDITION 18 WWW.CTSSNET.NET CTSS ..... 143 Leobersdorfer Maschinenfabrik (LMF) ........................ 143 FLSmidth Inc.................. 127.. 141 USA Inc........ 143 NEUMAN & ESSER Burckhardt Compression AG NEUMAN & ESSER South East Asia Ltd.................... 123 NEUMAN & ESSER Anlagentechnik ....................r...... 143 . 143 América do Sul Ltda.......................l. 143 PSE Engineering GmbH COMOTI ....... 192 COMPRESSORS...... GAS NEUMAN & ESSER GEA Refrigeration Italy Andreas Hofer Italia S.......... 143 MAN Diesel & Turbo SE Compressor International ..Mitsubishi Heavy Industries Hofer Kompressoren .... ..... 143 RUS Ltd....... 143 . 142............................ 237 Italia S. 142.. 142.... Ltd....................... Compressors Division ... 142................. Ltd....... . 119 ...... 138.... 143 Gulf FZE . 239 COMPRESSORS.......... 142.... 238....... 142............................. 119 Italia S.. GEA Refrigeration Italy NEUMAN & ESSER Pneumatic Transport ........ INTEGRAL Egypt Ltd......... 201 NEUMAN & ESSER Deutschland GmbH MAN Diesel & Turbo SE COMPRESSORS.... 237 Hochdrucktechnik GmbH NEUMAN & ESSER Hofer Kompressoren ..... 143 Corken Inc.. ....... ..... OIL-FREE & Co.r.. ........... 201 .. ............ 127........ 136................. Fourth Cover . 142............NET CTSS .. 143 2017 EDITION 19 WWW.... 144 (Beijing) Co.............................. .Compressors Tab South East Asia Ltd. . 238. 142. 142....... Ltd...Prime Movers Tab Elliott Group NEUMAN & ESSER .... KG Vertrieb und Solar Turbines Incorporated ..... . 142. Fourth Cover Mitsubishi Heavy Industries NEUMAN & ESSER Compressor International América do Sul Ltda.. 239 Anlagentechnik ..................CTSSNET.. Packagers Tab América do Sul Ltda. ............. 115.Romanian Research USA Inc................p.. 143 NEUMAN & ESSER BORSIG ZM NEUMAN & ESSER (Beijing) Co.... .............. 142........ 143 ....... 142....Romanian Research Compression Systems NEUMAN & ESSER & Development ...................... Burckhardt Compression AG ....................... 139 Engineering (India) Pvt... .... 143 NEUMAN & ESSER A Unit of IDEX Corporation Egypt Ltd....... 140........ 143 Institute for Gas Turbines . 142........................................ 127.......... 142........... 143 Leobersdorfer Maschinenfabrik Atlas Copco Gas NEUMAN & ESSER (LMF) . 142. 139 Anlagentechnik ... . 142.............. 143 Andreas Hofer Mitsubishi Heavy Industries Hochdrucktechnik GmbH NEUMAN & ESSER Compressor International ........... NEUMAN & ESSER Corken Inc............. 144 NEUMAN & ESSER NEUMAN & ESSER COMOTI ......... ......... 143 NEUMAN & ESSER ...... 142............................. ....... 143 Kobelco Compressors Ariel Corporation NEUMAN & ESSER America Inc.....l............ 138...................... 142....... 143 Deutschland GmbH & Development & Co....... 138....... 137 ...... 125................................ ........... 142...... 117 Deutschland GmbH A Unit of IDEX Corporation & Co........ 142... 123 SIAD Macchine Impianti S.......... Third Cover.............................. 139 Kobelco Compressors ... 143 Oil & Gas ..... 143 Compression GmbH .......... ..................... 143 .... 136....... 142.... KG Vertrieb und .................. 142...... 142......................l............................. 143 GEA Refrigeration Italy Kobelco Compressors NEUMAN & ESSER Oil & Gas ......... Engineering (India) Pvt..A. ..... ........... . 137 and Process ... 237 America Inc...... 142......... 129 Oil & Gas ........ 201 America Inc....... Fourth Cover RUS Ltd...................... 143 BORSIG ZM MAN Diesel & Turbo SE NEUMAN & ESSER Compression GmbH . 142..............................r... 142.. KG Vertrieb und Institute for Gas Turbines ................................. Ltd...... . 142............ 143 NEUMAN & ESSER NEUMAN & ESSER PSE Engineering GmbH Engineering (India) Pvt............ 142.p.. 141 PORTABLE Institute for Gas Turbines .... .....A........... BORSIG ZM Corken Inc.......... ......... 142...........NET CTSS ........... 142......... Packagers Tab .....r....... 142.... ......... 143 South East Asia Ltd..NEUMAN & ESSER NEUMAN & ESSER NEUMAN & ESSER South East Asia Ltd....... 137 Atlas Copco Gas América do Sul Ltda. 238.... Packagers Tab A Unit of IDEX Corporation GEA Refrigeration Italy .......... ...... 117 PSE Engineering GmbH Andreas Hofer Compression Systems Hochdrucktechnik GmbH COMPRESSORS.........................................r.......... NEUMAN & ESSER & Co........ 143 OIL-INJECTED Compressors Division ...... 143 NEUMAN & ESSER NEUMAN & ESSER NEUMAN & ESSER USA Inc..... 125.... 143 America Inc... 143 Deutschland GmbH Corken Inc......... 144 FLSmidth Inc.................. 142.. Ltd......... 143 ........... 123 Corken Inc..... 238. 142................................ 144 Egypt Ltd.. 143 Italia S.... 237 COMPRESSORS...................... 143 Oil & Gas .................... 143 RUS Ltd......... 142........ 142..Romanian Research Atlas Copco Gas COMPRESSORS...... 140.................. 143 ............. 140......... Compression GmbH ....... .... 142......... 142.... 142.. 117 ................ 142....... Fourth Cover Kobelco Compressors ................................... South East Asia Ltd........ Packagers Tab NEUMAN & ESSER PSE Engineering GmbH USA Inc..... ................CTSSNET.................. .. 143 NEUMAN & ESSER and Process ......... . Compression Systems NEUMAN & ESSER Compressors Division .. 143 América do Sul Ltda......... 142.................... 142.. 142........ Ltd.... 129 ............ ........... PISTON ... Ltd.................... Ltd.. 142. Burckhardt Compression AG Hochdrucktechnik GmbH Compressors Division ...... 143 Compression Systems .... 119 Anlagentechnik ............................... .......... 143 Anlagentechnik ....... ......................... .......... 238..................... 237 Andreas Hofer Kobelco Compressors Hochdrucktechnik GmbH Hofer Kompressoren .... 143 Burckhardt NEUMAN & ESSER NEUMAN & ESSER Compression AG .................... & Development and Process .....p. 144 .l......... 142............. 119 A Unit of IDEX Corporation A Unit of IDEX Corporation ..p.................................. KG Vertrieb und A Unit of IDEX Corporation Italia S....A..... 143 Andreas Hofer SIAD Macchine Impianti S......... 142.... . Fourth Cover Ariel Corporation (Beijing) Co.... 143 (India) Pvt........ 142. 142............A....... 143 RUS Ltd....... Pneumatic Transport ........... 238... 142..... Compressors Tab NEUMAN & ESSER (LMF) .. ....... KG Vertrieb und NEUMAN & ESSER Compression GmbH ........ 239 Burckhardt Compression AG .... 117 .... Compression Systems Corken Inc. GEA Refrigeration Italy RECIPROCATING Hofer Kompressoren ... 239 PSE Engineering GmbH ... SIAD Macchine Impianti S........................ ........... 143 BORSIG ZM Deutschland GmbH & Co... 142....... 143 NEUMAN & ESSER NEUMAN & ESSER NEUMAN & ESSER Engineering USA Inc........ . 143 Egypt Ltd......... Ltd...... 142...... Packagers Tab Engineering (India) Pvt............. 141 NEUMAN & ESSER (Beijing) Co..... 143 NEUMAN & ESSER America Inc........ COMPRESSORS.................. . 143 SIAD Macchine Impianti S... ... 136.... 143 COMOTI ... ... 142...... 143 Leobersdorfer Maschinenfabrik ..... 142......... .. 239 Oil & Gas ....... 239 2017 EDITION 20 WWW......l...... ........ 139 Kobelco Compressors NEUMAN & ESSER Gulf FZE .. 142............... ... ................. SKID- America Inc......... 123 MAN Diesel & Turbo SE GEA Refrigeration Italy .................... Ltd. Pneumatic Transport ...................... 142........ 237 South East Asia Ltd. 143 USA Inc........... SIAD Macchine Impianti S... 125................r...... Fourth Cover .. 142.......... 238.... 142.... ..p. 237 NEUMAN & ESSER Italia S...... 142.. .................... 134......... KG Vertrieb und Compressors Division ...... Egypt Ltd............ 143 Institute for Gas Turbines .......................... GEA Refrigeration Italy ROTARY SCREW Oil & Gas . SCREW NEUMAN & ESSER HOERBIGER ........... 134...... 143 . . 142......................... ..... .......GEA Refrigeration Italy NEAC Compressor Service Leobersdorfer Maschinenfabrik Oil & Gas ............. 137 HOERBIGER .....l................. 143 NEUMAN & ESSER Compression GmbH ... 139 Compression Systems NEUMAN & ESSER .r.. 143 Engineering (India) Pvt........................... 142..... ... 143 FLSmidth Inc.......... 143 NEAC Compressor GEA Refrigeration Italy NEUMAN & ESSER Service Ltda....... 237 Mitsubishi Heavy Industries Kobelco Compressors Compressor International NEUMAN & ESSER America Inc... 136.A....... 143 NEAC Compressor & Development NEUMAN & ESSER Service Ltd..... Fourth Cover USA Inc.. 142.........p... Packagers Tab COMPRESSORS...... 137 ................ 143 .. . 142.. 138..........r......... 142............... 136.. ...... 129 NEUMAN & ESSER COMPRESSORS..... 119 América do Sul Ltda.. ................. . Ltd......... 142.. . ................. KG Vertrieb und Corken Inc...... 143 COMPRESSORS.....l................ 143 COMPRESSORS.. 143 Oil & Gas ......... Packagers Tab & Co.... 139 NEUMAN & ESSER South East Asia Ltd..... 123 RUS Ltd......... 142..... 142. 142..... 143 (Beijing) Co......... 142........CTSSNET....... 127. 142.......... (Beijing) Co............. 136.. 143 A Unit of IDEX Corporation Compressors Division ..... 143 2017 EDITION 21 WWW........ 143 RECONDITIONED COMPRESSORS......... 142........ 143 Hochdrucktechnik GmbH NEUMAN & ESSER NEUMAN & ESSER ....l...... 136....... 142............................ Ltd.............. 143 NEUMAN & ESSER MAN Diesel & Turbo SE PSE Engineering GmbH América do Sul Ltda.. 117 .. 143 NEAC Compressor Kobelco Compressors NEUMAN & ESSER Service S... 137 NEUMAN & ESSER RUS Ltd...... KG ...Romanian Research Italia S......... 137 RUS Ltd. 143 PSE Engineering GmbH Burckhardt Compression AG NEUMAN & ESSER Compression Systems ................ 142.. 143 NEUMAN & ESSER NEUMAN & ESSER Leobersdorfer Maschinenfabrik Engineering (India) Pvt........... 239 NEUMAN & ESSER Egypt Ltd............. 142........... Ltd............... 144 Deutschland GmbH ..... ................... ... 142... 142.............. 142................... 142....... 135 NEAC Compressor Service MAN Diesel & Turbo SE Hofer Kompressoren . Anlagentechnik ............. ...... .... 143 Oil & Gas .......................... 143 (LMF) ........NET CTSS ............ 138.......... 117 Anlagentechnik ... 135 COMOTI ..A..... ..... 138.........................Romanian Research Leobersdorfer Maschinenfabrik & Development (LMF) ........ 142.......... 143 Institute for Gas Turbines .......... 142.... Deutschland GmbH SIAD Macchine Impianti S.... ...... BORSIG ZM .............. 142.. Fourth Cover MOUNTED Leobersdorfer Maschinenfabrik NEUMAN & ESSER Andreas Hofer (LMF) .. 143 (LMF) ......... 201 USA Inc...... .................. ................ 237 GmbH & Co. ROTARY SLIDING VANE & Co. ......................................... 143 COMOTI .... 143 America Inc............ ..... 136.............. ................... Third Cover... LUBE OIL PSE Engineering GmbH & Development GEA Refrigeration Italy Compression Systems Institute for Gas Turbines . 115.. FLUID ........ 134........ 119 NEAC Compressor Service Burckhardt Compression AG Elliott Group GmbH & Co. ...... SPEED CONDENSERS COUPLINGS...... SURGE Getriebe GmbH ................ 134.................................. 117 CONTROLS...p.... 192 Voith Turbo Inc.. 135 NEAC Compressor SIAD Macchine Impianti S....... TEMPERATURE Compressor International Elliott Group COUPLINGS......................................... ............. NEAC Compressor Compression Systems ENGINE SYSTEM Service Ltd..... 135 Institute for Gas Turbines . 237 SIAD Macchine Impianti S.. 142... 143 . 115.. INTERCOOLER MAN Diesel & Turbo SE ELECTROHYDRAULIC TYPE ............ 201 ............ 113 .......... 117 CONSUMPTION GEA Refrigeration Italy Voith Turbo Inc...... ..A.. 192 NEAC Compressor Service HOERBIGER ......NET CTSS ......... COMPRESSOR NEAC Compressor COMPRESSORS...................... BORSIG ZM Service S.CTSSNET................ DIAPHRAGM Voith Turbo Inc.............. 139 CONVERTERS................................. 142.......... 192 CONSULTING Voith Turbo Inc............ Third Cover..... 239 . KNOCK COOLING SYSTEMS COMOTI ...r. 123 .... Packagers Tab HOERBIGER .NEUMAN & ESSER PSE Engineering GmbH CONTROLS... 134. 127.. 127......... A Unit of IDEX Corporation MAN Diesel & Turbo SE .............. Packagers Tab Oil & Gas . 238... 113 Voith Turbo BHS Mitsubishi Heavy Industries Compressor International CONTROLS.. 142.. 113 (LMF) ............ COOLERS... 143 ..... FUEL COOLERS........ VIBRATION Engineering (India) Pvt......................... .. 135 USA Inc............... CONTROLS............ 201 COMOTI ...... 138......... 201 Elliott Group COUPLINGS..... 192 PSE Engineering GmbH CONTROLLERS.................................................. 139 HOERBIGER ....A............. 113 2017 EDITION 22 WWW...... Third Cover. 144 ... . .....................l..................................... Third Cover.......Romanian Research DETECTION & CONTROL & Development GEA Refrigeration Italy HOERBIGER . 143 . ... 137 CONTROLS... . 113 Voith Turbo Inc. 143 Corken Inc....... 143 STATIONARY Compression GmbH ................................ 142.... 143 Compressors Division ......................p........ 134.... 113 Mitsubishi Heavy Industries CONTROLS............................ 237 COMPUTER-CONTROLLED ENGINE TESTING CONTROLS.......... 115................ Packagers Tab . Compression Systems Elliott Group ........................................ 123 Oil & Gas . 142............ 135 GEA Refrigeration Italy Mitsubishi Heavy Industries Oil & Gas ....... WATER Compressors Division ....... TORQUE Leobersdorfer Maschinenfabrik Voith Turbo Inc............. .......... 142........ 127......... 115........................... Ltd......... FLEXIBLE ................ 237 CONTROLS................ KG ....Romanian Research COOLERS.......... 237 Compressor International CONTROLS...... 113 Oil & Gas ..... ELECTRONIC .... 138. Service Ltda...... ...... 135 Voith Turbo Inc........... 123 HOERBIGER ....... HYDRAULIC-PUMP MAN Diesel & Turbo SE Elliott Group CRANKSHAFTS.... & Development SLEEVES OVERHAUL & PARTS Institute for Gas Turbines ...........NET CTSS ........ 201 2017 EDITION 23 WWW........ 192 RECONDITIONING Solar Turbines Incorporated HOERBIGER ... .... CRANKSHAFTS Getriebe GmbH ................... 135 SERVICES Elliott Group Cummins Inc. ................... .. 115.. Oil & Gas Markets MAN Diesel & Turbo SE RECONDITIONING ... 135 COMOTI ....... 134............... 135 and Process . NATURAL GAS CYLINDER LUBRICATION (SPARK IGNITED) SYSTEMS DRIVES......... 138....... 139 ...... Third Cover.......... 134......... 134................ CONVERSION Elliott Group Voith Turbo Inc...... 127.. Second Cover ............... 135 Institute for Gas Turbines .... 140. 115....... 135 Mitsubishi Heavy Industries SIAD Macchine Impianti S. Packagers Tab Oil & Gas Markets EMISSIONS ANALYZERS ....... 113 Getriebe GmbH ........ MAN Diesel & Turbo SE Compressor International Compressors Division ..... TURBINE STARTING .. 134.........Romanian Research CYLINDERS...... 192 SYSTEMS/COMPONENTS MAN Diesel & Turbo SE HOERBIGER ... GAS TURBINE Voith Turbo BHS Voith Turbo Inc......................... 123 Atlas Copco Gas HOERBIGER ..... ......................... 135 DRIVES.... 117 .............. 134...... 113 Oil & Gas Markets HOERBIGER .............Prime Movers Tab Voith Turbo BHS DRIVES..A................. ENGINE & Development EMISSIONS CONTROLS Institute for Gas Turbines ....................... Second Cover CYLINDERS COMOTI .................... . LINERS & ENGINE MAINTENANCE.. COMPRESSOR Getriebe GmbH ................................ 135 COUPLINGS........... 134.. 113 ENGINES... 134............... GEAR-TYPE D Solar Turbines Incorporated ............CTSSNET...... 134........ .............. 138.................. 135 HOERBIGER ............. 134... 113 DRIVES.... 123 HOERBIGER ......... GEAR REDUCTION Institute for Gas Turbines . SHAFT .............Romanian Research HOERBIGER ...... 135 ..... VARIABLE-SPEED COMOTI ..Prime Movers Tab Voith Turbo Inc. Third Cover...........Romanian Research & Development EXPANDERS CYLINDERS......................Romanian Research & Development ENGINES................... 138.. 123 Voith Turbo BHS Cummins Inc. 139 HOERBIGER ...... LIGHT-ALLOY Institute for Gas Turbines ... 141 HOERBIGER .................................. 123 Compression Systems E Cummins Inc............ 138.. 139 ................................... 139 ENGINES.............. RESEARCH HOERBIGER ............... ..COUPLINGS....Romanian Research & Development Voith Turbo Inc.Romanian Research CYLINDERS... 134. 123 COMOTI ........... 192 CYLINDERS......... 135 COMOTI .....p............. 113 ENGINES..... 115..... 113 ............... 113 COMOTI ............. Third Cover. 113 & Development PSE Engineering GmbH Institute for Gas Turbines ......... ..... Second Cover DRIVES...... 134.... ........CTSSNET.... 201 USA Inc. 139 Voith Turbo BHS Getriebe GmbH ............ 138. 123 Getriebe GmbH ............... 113 MONITORS.. 135 GEARS....... TURBINE Compressor International COMPONENTS GEARS.... 201 Mitsubishi Heavy Industries GEARS. COMPRESSOR Getriebe GmbH .............................................l.. 113 NEAC Compressor & Development Voith Turbo Inc............... 113 HOERBIGER ............. .................. 134..................l....... 142. 113 MECHANICAL FASTENERS Compressor International .r........ 113 I NEAC Compressor GEARBOXES IMPELLERS....... INCREASERS M Voith Turbo BHS FORGINGS...... LOAD L HOERBIGER .. 201 Voith Turbo BHS Institute for Gas Turbines ..Romanian Research Compressor International GEARS....... CYLINDER NEAC Compressor Voith Turbo BHS Service Ltd. COMPRESSOR GAS TURBINES GEARS. 127............ 123 NEAC Compressor Voith Turbo BHS Service Ltda.. 127..... HELICAL LINERS....Romanian Research INLET COOLING SYSTEMS MONITORS......... TURBO MAN Diesel & Turbo SE GEAR SYSTEMS Voith Turbo BHS ........................... 201 Mitsubishi Heavy Industries Voith Turbo BHS Getriebe GmbH .. 127.... RECONDITIONING Service Ltda.. 143 Getriebe GmbH . STATIONARY/ SYSTEMS INDUSTRIAL DRIVE Burckhardt Compression AG COMOTI ................... .. 113 Mitsubishi Heavy Industries FORGINGS....... ENGINE SYSTEM & Development Institute for Gas Turbines ......... RING & Development . 113 MACHINING Mitsubishi Heavy Industries COMOTI ..................... 134.. 142................. 143 Getriebe GmbH ... 143 TURBOCHARGERS Voith Turbo BHS NEAC Compressor Service Getriebe GmbH .............. . 144 Institute for Gas Turbines .... 143 Compressor International NEAC Compressor Service GEARS......... ......... 142.......... STATIONARY Compressor International Voith Turbo BHS ...... 237 .. ....... 113 MONITORS.......... F GEARS..................... 135 Service S.. 142....... 142.............. 123 GEA Refrigeration Italy MAN Diesel & Turbo SE Oil & Gas ..r....... 135 NEAC Compressor GEARS..... 113 Mitsubishi Heavy Industries GmbH & Co.... CUSTOM ....... 143 Institute for Gas Turbines .................... 113 HOERBIGER ...................................... 113 Service Ltd... SPUR ................... 142............ 143 Voith Turbo BHS CYLINDER NEAC Compressor Getriebe GmbH ....... 139 COMOTI ..... 127....... 201 G Getriebe GmbH ..................... 143 COMOTI .................. EPICYCLIC LINERS...........Romanian Research & Development Voith Turbo BHS ................ KG .......... 134.............. 127........ 138.................... 135 GEARS.......NET CTSS ............. 113 HOERBIGER ............ 134.............. 142.......................... 142. ................ .. 123 Getriebe GmbH ..........Romanian Research Getriebe GmbH ............ 143 2017 EDITION 24 WWW.... TURBINE & Service S........... .... ........ GAS TURBINE NEAC Compressor COMPRESSOR Solar Turbines Incorporated Service Ltd.. NEAC Compressor & Development PLATFORM DECK........................... Packagers Tab USA Inc.............. ENGINEERING & DESIGN NEAC Compressor PACKAGES. 143 ............. 142...... 142........... 129 Mitsubishi Heavy Industries NEAC Compressor GEA Refrigeration Italy Compressor International Service Ltd................. CAP NEUMAN & ESSER USA Inc......CTSSNET. 142...... Oil & Gas ....... 134.. 143 Oil & Gas ... 142........ ....... 134............. 143 NEAC Compressor P PSE Engineering GmbH Service Ltd.......................... 142......... 138.... 143 PSE Engineering GmbH NEAC Compressor Service NEUMAN & ESSER Compression Systems USA Inc...... 135 Pvt...................... 143 América do Sul Ltda.............. 237 Service Ltda..... 143 Compressor International NEAC Compressor Service NEUMAN & ESSER ........ 125......... ............. 239 .. 143 Elliott Group ........ PRESSURE ... MOTOR Service S......Romanian Research Institute for Gas Turbines ................ ................. 123 FPSO MODULE DESIGN NEAC Compressor Service GEA Refrigeration Italy PSE Engineering GmbH GmbH & Co...... 237 HOERBIGER . .Prime Movers Tab Compression Systems HOERBIGER . 142.l......... 142.. 142. Packagers Tab NEAC Compressor COMPRESSOR Service Ltda......Romanian Research COMPRESSOR & Development NEAC Compressor Service COMOTI ... 143 Institute for Gas Turbines .......... KG ..r.. KG Vertrieb und Mitsubishi Heavy Industries Service S.. 142..... Ltd..........l......... ........................... 142... 143 Italia S....... 142......... ... 142. 143 Oil & Gas ..... 143 NEAC Compressor Service NUTS......... KG .......................................r......NEAC Compressor Service N NEUMAN & ESSER GmbH & Co.. TEMPERATURE PSE Engineering GmbH .. 143 Compressor International NEUMAN & ESSER MONITORS..... .... 127.... ... 143 PACKAGES. ........... 143 Deutschland GmbH ..... 143 South East Asia Ltd. 142. KG .... 201 Engineering (India) HOERBIGER .. 142. 142..... KG . 142....... Packagers Tab 2017 EDITION 25 WWW......... 143 Mitsubishi Heavy Industries USA Inc.. 142.. 142...r............... 238................... 192 MONITORS. 237 Compression Systems NEAC Compressor Service MAN Diesel & Turbo SE ................... .................. FOUNDATION. .................. 143 ... 127.. 127................. ................... 201 NEAC Compressor MAN Diesel & Turbo SE NEUMAN & ESSER Service Ltda.. 142.. 142........ 139 Solar Turbines Incorporated MONITORS............. 201 GmbH & Co... . .............. 123 NEAC Compressor Service A Unit of IDEX Corporation USA Inc................ 143 Compression Systems PACKAGES...... 123 GmbH & Co...... 143 & Development Corken Inc... Packagers Tab PACKAGES..... 143 COMOTI .. ...............NET CTSS ..... 134.... 135 Pneumatic Transport .............r.l.... ...................... 142. .. Institute for Gas Turbines .............Romanian Research PACKAGES.. 143 Anlagentechnik .... 139 NEAC Compressor & Co...Prime Movers Tab GEA Refrigeration Italy NEAC Compressor Oil & Gas ...l.. Service S.................................. Third Cover....... VIBRATION GEA Refrigeration Italy FLSmidth Inc....... 138........................... 142........ 237 .......... ENGINE ... 115.... 142. 143 COMOTI ..................... 135 ..... 143 ..... ............................. ... 238.. INTERMEDIATE Service Ltda...................... 192 América do Sul Ltda......... RECONDITIONING NEUMAN & ESSER A Unit of IDEX Corporation (Beijing) Co.............. 142. 142................. 143 COMOTI ...... Packagers Tab Compressor International . ...... 143 STASSKOL Inc........... 143 BORSIG ZM NEAC Compressor Service PACKAGES.... 139 Hochdrucktechnik GmbH .......... .. Engineering (India) NEAC Compressor Service A Unit of IDEX Corporation Pvt........l......... 119 USA Inc..... 115........ Ltd............ ..... 239 Anlagentechnik ..... PIPING. 142.. 134. KG Vertrieb und USA Inc... 142..... 134........ 143 NEAC Compressor USA Inc.. 143 TURBINE COMPRESSOR STASSKOL GmbH ...... 135 .... 142.................................. 142. 143 NEUMAN & ESSER STASSKOL GmbH .. 142. CONDENSATE OR Egypt Ltd................................................. 127...... STEAM Compression GmbH ... 143 NEAC Compressor Service CONDENSATE RETURN GmbH & Co............. OIL WIPER GmbH & Co..........PACKAGES.......... 142. 142. 135 Corken Inc.. 138.... 142..... KG ........................... NEUMAN & ESSER POWER TURBINES STRUCTURAL ANALYSIS Italia S. 142..... 143 .......... .........r... 135 PUMPS. Ltd.................... 127.... PISTON ROD .. 142...... 143 NEAC Compressor PACKINGS. 134.. 143 ..... 123 Oil & Gas ...... 134....... 201 STASSKOL GmbH ............. 143 NEAC Compressor Service Ltd.... 142...... .l............. .............. 143 PROTECTIVE CONTROLS PACKING ASSEMBLIES MAN Diesel & Turbo SE Andreas Hofer PISTONS .......... KG ..l. 143 Anlagentechnik . ................... 138...... 143 STASSKOL Inc..... 142.. 139 & Co... 143 USA Inc......r..... .... ..... 142............................... 143 NEUMAN & ESSER PUMPS....... 143 STASSKOL Inc.......... 201 NEUMAN & ESSER South East Asia Ltd............ 143 Pvt........... Elliott Group ..... 142.................. KG Vertrieb und . 239 2017 EDITION 26 WWW. 142.... 192 PSE Engineering GmbH Mitsubishi Heavy Industries Compression Systems PACKINGS. 142.... 135 ..... 142.... 142... .... PISTONS.............. ........... 143 HOERBIGER ..... BOILER-FEED HOERBIGER .. 239 NEUMAN & ESSER NEAC Compressor América do Sul Ltda.. 238............. 142.. 237 RUS Ltd. 143 NEUMAN & ESSER Corken Inc...................... 143 A Unit of IDEX Corporation & Co. 142....l.. ............... .......... 142. 143 NEAC Compressor Service S............ 143 PUMPS...........Romanian Research GEA Refrigeration Italy & Development NEUMAN & ESSER Institute for Gas Turbines .... 142...... 143 Elliott Group NEUMAN & ESSER NEUMAN & ESSER .. .............. .... ..... 238......... 142.......... CHEMICAL NEUMAN & ESSER NEAC Compressor Corken Inc.... 143 South East Asia Ltd. 142... 115............... . 143 HOERBIGER ..r.... 142. 143 Service Ltd.... ............NET CTSS ...... 143 MAN Diesel & Turbo SE NEUMAN & ESSER Deutschland GmbH NEUMAN & ESSER ... ..............r... Third Cover........ 142...... .......... . 142................CTSSNET...................... Third Cover... 143 Compressor International HOERBIGER ... 143 NEUMAN & ESSER NEAC Compressor Service Engineering (India) PACKINGS......... 142.......... ........ Deutschland GmbH Service Ltda....... 143 Service S.... Ltd........ 142...... 142... 143 PROJECT MANAGEMENT NEUMAN & ESSER PACKING CASES Mitsubishi Heavy Industries Italia S.... . ........... LUBRICATING-OIL Mitsubishi Heavy Industries RINGS.. ........... 143 STASSKOL GmbH .. 142...... HYDRAULIC STASSKOL GmbH .............................. .............. 134......... LABYRINTH PUMPS.... 239 ... 135 GmbH & Co..... SEALING A Unit of IDEX Corporation HOERBIGER ... 143 USA Inc... 239 & Development Service Ltda.... 239 STASSKOL Inc......... 143 A Unit of IDEX Corporation ..... 142......... 142. MAGNET DRIVE Corken Inc. 143 RINGS.............. ............... Service Ltda... 239 NEAC Compressor Service STASSKOL Inc.......... . 143 BREAKER A Unit of IDEX Corporation ............. HOERBIGER .... 123 NEAC Compressor PUMPS..... 135 HOERBIGER .... 239 STASSKOL GmbH .. 142........ 143 HOERBIGER . RINGS............. 142............ 143 ... HIGH-PRESSURE DEVELOPMENT Service Ltd... 238..........PUMPS............ 135 ....... 143 RINGS........ Service S... 143 Corken Inc. 142...... 239 NEAC Compressor STASSKOL GmbH . 142....... COMPRESSOR NEAC Compressor Service Corken Inc....... 238........... 142. 143 PUMPS. 142... FLOATING-SEALING Corken Inc. 143 HIGH-TEMPERATURE RINGS......... R NEAC Compressor Service HAZARDOUS-LIQUID USA Inc.......... 142...... 143 Corken Inc.. 142....... 142.. 238....... 143 STASSKOL GmbH ..... 143 Institute for Gas Turbines .... Voith Turbo BHS A Unit of IDEX Corporation RINGS..... Service Ltd. 142. 113 ..r..... 142............... COMOTI ................. 142..... .... ............ 143 POSITIVE-DISPLACEMENT NEAC Compressor Corken Inc.. 138. 127. 142....................... 142. 142. 142. 142.. HOERBIGER .......... PISTON Getriebe GmbH ........... KG ......... 239 HOERBIGER .....l... RINGS.......................... ............................ 142............... . 238.....NET CTSS . 143 RINGS. ....... 143 Corken Inc........................................ 143 A Unit of IDEX Corporation STASSKOL GmbH ...... 134...... 238............ 142. 143 STASSKOL Inc.......... RIDER Compressor International Corken Inc. 238....... ................. .. . 134................... STASSKOL Inc......... 239 Service S.... . 238................................. GEAR STASSKOL Inc. A Unit of IDEX Corporation NEAC Compressor TURBOCHARGER-SEALING ................ 134.... HYDRAULIC RINGS. 135 .... 238..... 143 PUMPS. ......... 201 A Unit of IDEX Corporation .... POWER PUMPS....... 142.. PACKING RINGS.......... 134........ GUIDE HOERBIGER ....... 135 GEAR-TYPE STASSKOL GmbH ........... ...........CTSSNET....l.... 134......... PRESSURE STASSKOL Inc.................. 135 2017 EDITION 27 WWW............. 142.. 238.r.... REACTOR SYSTEMS NEAC Compressor Service GmbH A Unit of IDEX Corporation MAN Diesel & Turbo SE & Co......... 143 STASSKOL Inc........... 135 RINGS....... 135 RESEARCH & NEAC Compressor PUMPS.. 134.Romanian Research NEAC Compressor A Unit of IDEX Corporation . HEAVY-DUTY REDUCERS........ ... 143 .. 143 PUMPS....................... KG . 142.. 143 STASSKOL Inc........... 139 STASSKOL GmbH ................. 134.............. 142. 239 HOERBIGER ... 143 PUMPS..... 143 Corken Inc....... ...... 142..... 192 NEAC Compressor Service SERVICES....... 142......... ..RINGS.... .... .... 138. Third Cover............... Ing Mario Cozzani Srl ...Prime Movers Tab USA Inc.... 143 SEATS.......... 115............................ 144 COMOTI .... 134..................................... 117 & Development SAFETY SYSTEMS Institute for Gas Turbines .............. GAS TURBINES GmbH & Co.......... 138... Service Ltda... 143 Solar Turbines Incorporated NEAC Compressor Service STASSKOL GmbH ........... 129 ...... 113 EQUIPMENT ..... 142........................ . .. 142. 142....... 135 Elliott Group FLSmidth Inc............................ KG .r....... 134.... MAN Diesel & Turbo SE Pneumatic Transport . 143 MAN Diesel & Turbo SE NEUMAN & ESSER ............Romanian Research Compressors Division .. ..... 142.. 113 Institute for Gas Turbines ..... 134..............l... COMPRESSORS GmbH & Co...... 115.r.... 192 ...... VALVE Mitsubishi Heavy Industries NEAC Compressor Compressor International Cozzani... 119 ........................ ... 142. 201 Mario Cozzani Srl ............ 142.............. 142... 127....... Packagers Tab SIAD Macchine Impianti S............... 143 TURBOMACHINERY . 135 .. 134......... 123 NEAC Compressor Service S..................... 125......... WIPER SERVICE SYSTEMS & NEAC Compressor Service HOERBIGER ............ NEAC Compressor ROTORS... Solar Turbines Incorporated Service Ltd... 127...... 143 2017 EDITION 28 WWW........ 143 ROTOR TURNING GEARS PSE Engineering GmbH Voith Turbo BHS Compression Systems SERVICE TOOLS & Getriebe GmbH ..... 123 Elliott Group BORSIG ZM Elliott Group ......................... 237 SEALS............................ 217 Service S. ............ 142............... 115... 142............. 143 & Development Getriebe GmbH ... 143 Voith Turbo Inc. 139 .... 139 USA Inc... 143 .......................A................ 139 GEA Refrigeration Italy Mitsubishi Heavy Industries Oil & Gas ........................... 135 NEAC Compressor Service Andreas Hofer MAN Diesel & Turbo SE USA Inc..... DRY GAS Pvt..................... 201 MAN Diesel & Turbo SE STASSKOL Inc.. 142............ 143 NEAC Compressor .... 138............................. 113 Elliott Group .. 135 TRAINING..... 143 HOERBIGER .................... KG . .. 127.......CTSSNET.......... Ing... Third Cover.. 142.. ........... 142....... 143 OVERHAUL & REPAIR HOERBIGER .... 192 Compression GmbH . .. 142.......................................l................ 142......... 142...........NET CTSS ........ 143 HOERBIGER ...............Romanian Research Voith Turbo BHS Service Ltda..... 143 Mitsubishi Heavy Industries SERVICES & TRAINING BORSIG ZM Compressor International BORSIG ZM Compression GmbH .... ............ ........Prime Movers Tab NEAC Compressor COMOTI .......... 201 Compression GmbH ........................... 217 NEAC Compressor NEAC Compressor Dott.... 119 Burckhardt Compression AG Burckhardt Compression AG .. 192 GEA Refrigeration Italy Engineering (India) Oil & Gas ........ SHAFT Compressor International STASSKOL GmbH ........ 115........... 144 S ................. 143 Service Ltd... 138.... ... 119 .............. 143 STASSKOL Inc................... Third Cover..... Third Cover...................p........... 237 SEALS...... 143 .................... 143 Hochdrucktechnik GmbH ....... 139 Service Ltd.... Ltd... Dott.......... 142..... ..... DIAGNOSTICS COMOTI ....p....Romanian Research NEAC Compressor COMOTI .................. Packagers Tab HOERBIGER ......... 192 GmbH & Co.................................................... 142......... 117 Compressors Division .............. 143 USA Inc. ........... ................... 143 GmbH & Co.. 134...r............... 142. ........................ .............................p.......... 142... 143 FAILURE-ANALYSIS NEAC Compressor Service Elliott Group SERVICES.... ....... KG . 142........... 119 NEAC Compressor Deutschland GmbH Service Ltd...... 142................ 117 .... 143 NEUMAN & ESSER Elliott Group NEAC Compressor Service RUS Ltd.... 142. 142........... 142..... Third Cover... 143 NEUMAN & ESSER Institute for Gas Turbines ........ 142....... GmbH & Co......... 139 Solar Turbines Incorporated SERVICES.. KG ..... 143 & Co............. ....Romanian Research & Development Service Ltd...........l. 115..... 142..... Ltd...... ENGINEERING Compressor International ... KG .NEAC Compressor NEAC Compressor PSE Engineering GmbH Service Ltda.....l..... .. 142... 142......................... .. 143 GmbH & Co.. 143 SIAD Macchine Impianti S..... ... 143 NEAC Compressor ..........r....... ...................... 143 ...... 142.. 192 LUBRICATION SYSTEMS NEUMAN & ESSER GEA Refrigeration Italy PSE Engineering GmbH NEUMAN & ESSER Oil & Gas ........ 143 Service Ltda. 142....... ...... 142.......... 143 PSE Engineering GmbH GEA Refrigeration Italy PSE Engineering GmbH Compression Systems Oil & Gas ... 142..... 142........... ... .......... ..... 144 Service Ltda...........r.. 143 ...................... 143 USA Inc...... FIELD Mitsubishi Heavy Industries . 143 .......... 143 Mitsubishi Heavy Industries Mitsubishi Heavy Industries Compressor International NEAC Compressor Compressor International .................. 135 NEUMAN & ESSER Mitsubishi Heavy Industries América do Sul Ltda........... Compressor International ........... ............... .. 142.............................. 134........CTSSNET............ 142...... 143 Compressors Division ............. 142..... 142... 201 NEUMAN & ESSER BORSIG ZM Compression GmbH ....r..... 143 & Development Service S. 143 & Development Institute for Gas Turbines ... 123 Institute for Gas Turbines .............. 123 NEAC Compressor HOERBIGER .. ......... 142........ Packagers Tab . 142...... 115. 135 SIAD Macchine Impianti S...... 143 NEAC Compressor NEAC Compressor Service NEAC Compressor Service Ltda. ...Prime Movers Tab PULSATION... 201 VIBRATION-ANALYSIS SERVICES............... 143 ...... . 237 Compression Systems ..... Third Cover........ KG Vertrieb und Burckhardt Compression AG Anlagentechnik ....... Packagers Tab HOERBIGER ....... .............. 134...... 201 NEAC Compressor NEAC Compressor Service NEAC Compressor Service Ltd...... ..... 142. 127.. Packagers Tab NEAC Compressor Service S.... 143 Compression Systems NEAC Compressor Service ...... 143 NEUMAN & ESSER COMOTI .......l.............. 135 Service Ltda.. 143 Service S........ 117 USA Inc...........................A. 237 Compression Systems (Beijing) Co..NET CTSS ......... KG ......... MAN Diesel & Turbo SE Compressors Division ...... 143 2017 EDITION 29 WWW........ 201 Service S.......................l...... 143 Service Ltd.... 138....... 142.Romanian Research NEAC Compressor Egypt Ltd... 143 SERVICES.. 142...... DIVIDER BLOCK USA Inc. 123 NEAC Compressor Service Gulf FZE ..A... 127........p... 142... 127....... NEAC Compressor Service NEAC Compressor Service SERVICES......A. 127......................... SIAD Macchine Impianti S.. ... 127.... 143 NEAC Compressor Service SILENCERS................... Third Cover....l.......... .... 138... KG .. 142.. 142........................ 127....... ......... 201 NEAC Compressor COMOTI ............ 142... 123 NEAC Compressor Service NEUMAN & ESSER USA Inc............ 143 HOERBIGER . 201 STUD BOLTS Service S....... 142......... 143 Voith Turbo Inc..... 119 STEAM TURBINES Solar Turbines Incorporated COMOTI ... Ltd..l.... 142........................ 143 COMOTI ....Romanian Research & Development Institute for Gas Turbines .. KG ........ 143 SERVICES..................... Ltd.. 142......... 142.... 115... 142...Prime Movers Tab & Development ................... 192 NEAC Compressor Mitsubishi Heavy Industries Service Ltd...................... USA Inc........ .... KG ........l... 143 COMOTI ............ .... .... 115. ACOUSTICAL TURBOCHARGERS.Romanian Research Service S........ 201 Service Ltda................. .......................Romanian Research NEAC Compressor Service NEUMAN & ESSER & Development GmbH & Co............. 142............ 127... 138.. 143 SHAFTS Mitsubishi Heavy Industries T SERVICES.. .... GAS TURBINE NEUMAN & ESSER COMOTI ...... 143 Institute for Gas Turbines ... 115.. EXHAUST Service S.......................... 127........ 113 Compressor International NEAC Compressor Service Ltda........... 142......NEAC Compressor NEUMAN & ESSER SILENCERS....... 143 Mitsubishi Heavy Industries Voith Turbo Inc............NET CTSS ... 123 SERVICES.... .... 115...... ...... ......... ........ SHAFT Elliott Group TURBOMACHINERY STASSKOL GmbH . Third Cover....... LASER MAN Diesel & Turbo SE MEASUREMENTS Elliott Group ......... 192 2017 EDITION 30 WWW........... 143 Institute for Gas Turbines .......... 113 GmbH & Co......... 142.. 192 Institute for Gas Turbines . 143 TORQUE CONVERTERS & Development NEAC Compressor Service Institute for Gas Turbines .............. 143 .... 113 ........ 139 ..................... 143 Institute for Gas Turbines .. 142... ..............Romanian Research OVERHAUL & REPAIR Engineering (India) & Development Pvt...... 123 SERVICES.... ..... 142.... 142........... Third Cover............. 201 Service Ltd.. 143 SILENCERS ...r.... 143 Gulf FZE ........................... 142. ....... SHUTDOWN Compressor International TILTING PADS NEAC Compressor .......... INTAKE AIR RUS Ltd.................. 142.. 123 .... 123 Voith Turbo Inc......... 143 Mitsubishi Heavy Industries SERVO MOTORS Compressor International NEAC Compressor Service USA Inc... 192 OVERHAUL & REPAIR STASSKOL Inc.. 127........ Third Cover. 123 COMOTI . 143 SILENCERS........ 143 MAN Diesel & Turbo SE BORSIG ZM . . 142.r..Romanian Research Elliott Group ................. 142.. 134. . ... 201 NEAC Compressor Service GmbH & Co. 142... 139 Compression GmbH ...... SLEEVES.........r.....Romanian Research REPAIRS NEUMAN & ESSER & Development Elliott Group (Beijing) Co........ 143 Egypt Ltd..... 135 Compressor International NEAC Compressor Mitsubishi Heavy Industries .... 142....CTSSNET........ ..................... 143 Compressor International NEAC Compressor ................ .... ............. 141 Cozzani......... 142......TURBOEXPANDER Burckhardt Compression AG NEAC Compressor Service Atlas Copco Gas .. ......................... Dott...... ..... 143 VALVES.. 142. SEATS & RINGS Pvt..... 142.CTSSNET. .. 135 Gulf FZE ..... 142.. SHUT-OFF NEAC Compressor Hofer Kompressoren ........ 135 NEUMAN & ESSER HOERBIGER .....l. 217 NEUMAN & ESSER Institute for Gas Turbines . 142....r... 135 América do Sul Ltda...... FUEL Hofer Kompressoren ....... 134...... Dott.... .l..................... 143 NEAC Compressor Service Ltd....... ..... 134. Ing.................. ........... 143 & Development Dott.... ... .................... 135 2017 EDITION 31 WWW. 142.. 142.... 143 NEAC Compressor Service HOERBIGER ............. 143 Pvt... 143 VALVES... 142..... 142....... 142. 142.... ...........r.... 143 VALVES.... 142................... GmbH & Co......... 143 Mitsubishi Heavy Industries NEAC Compressor NEUMAN & ESSER Compressor International Service Ltd.. KG Vertrieb und NEAC Compressor Anlagentechnik .... CRANKCASE NEUMAN & ESSER RELIEF RUS Ltd....... RELIEF & SAFETY NEAC Compressor Service VALVES...........r....... 143 BORSIG ZM Hofer Kompressoren ........... .......l....... 217 (Beijing) Co... 142.... 143 HOERBIGER ... 142... 143 NEUMAN & ESSER Compression GmbH . 217 HOERBIGER . 143 NEUMAN & ESSER VALVES. Ing Mario Cozzani Srl ............ 142.. 143 VALVE SPRINGS NEUMAN & ESSER NEAC Compressor Service Engineering (India) Cozzani.. 135 USA Inc....... 134... .. ...... 142......................... 143 Italia S........ 143 Cozzani. 127.... 217 Cozzani............. EXPLOSION STASSKOL GmbH . 143 Service S. ....... 142......... 143 Mario Cozzani Srl ...... 143 Dott......... Ltd................ 217 Egypt Ltd..... 142... Ltd.............. ........ 143 Gulf FZE ...... 142...... 217 USA Inc........ 123 HOERBIGER ..........l.............. 143 VALVES....... 135 USA Inc. 142................. STARTING AIR Compression GmbH ...... 143 NEUMAN & ESSER V NEAC Compressor Egypt Ltd. Dott............ 143 HOERBIGER ........ 142. 135 NEAC Compressor VALVES.Romanian Research Mario Cozzani Srl ......... ... 142..r. OVERHAUL HOERBIGER . KG .... 134.... 143 HOERBIGER . Ing....... PRESSURE Service S............. .. ............ KG .... 134........ Ing...... 135 GmbH & Co.. CHECK NEUMAN & ESSER Gulf FZE .. 143 VALVES............... 217 NEUMAN & ESSER Service Ltd................ 142... 143 Mario Cozzani Srl .. 143 NEAC Compressor Dott. ............... KG .... 119 Engineering (India) Cozzani. 217 NEAC Compressor Service NEUMAN & ESSER Dott..... Dott...... 217 VALVES..... ....... 142...... 143 NEUMAN & ESSER NEAC Compressor RUS Ltd... ... 143 BORSIG ZM NEAC Compressor Service VALVES............. 134.. 143 RELIEF STASSKOL Inc.... Ing Mario Cozzani Srl ....... 143 and Process ....... Ing Mario Cozzani Srl . Ing Mario Cozzani Srl ... 140................... 143 Service S....NET CTSS ........ 142......... 143 NEAC Compressor Service Ltda.... Ing Mario Cozzani Srl .. 144 USA Inc.. 142.. 142.......... 134...... 134.. 142... Ing....... Ltd............... VALVES..... Mario Cozzani Srl ...... 201 & Co.... 142.... 142....... 143 Deutschland GmbH .... . 119 GmbH & Co....... ..... 142......... NEUMAN & ESSER Dott... Dott............ 142........... 217 Mario Cozzani Srl ..... Ing. COMPRESSOR Service Ltda... 142....... 142.. NEUMAN & ESSER COMOTI ... 143 Service Ltda.... SUBSCRIBE TODAY www. From wellhead to city gate.COMPRESSOR Dedicated To Gas Compression Products & Applications COMPRESSORtech2 is the premier resource for gas compression news and information. COMPRESSORtech2 keeps you informed with in-depth coverage of compression machinery and technologies.CTSSNET. we’re the publication of choice in the gas compression machinery world.NET CTSS .compressortech2.com/subscribe/ Free For Qualified Readers | Available In Print Or Digital Versions 2016 EDITION 2017 XX 32 WWW. That’s why every Ariel compressor we produce is manufactured to order based on your needs and requirements.When it comes to choosing a compressor.com/For-You/ . Learn more about Ariel compressors www.arielcorp. a one-size-fits-all solution isn’t always the best choice. ARIEL IS COMMITTED TO YOU. field location. ARIEL IS COMMITTED TO YOU. Learn more about Ariel compressors www.arielcorp. a one.com/For-You/ .size-fits-all solution isn’t always the best choice. and online assistance to our customers around the globe. That’s why Ariel offers tailored in-house.When it comes to supporting customers. 300 14.000 833 21.000 45.NET CTSS .CTSSNET.370 586.000 legacy and Rolls-Royce Energy Division legacy.000 167 6670 290 20 40.000 100.700 2900 200 80.000 45.000 37.700 102 7 134.500 5330 8000 101 7 2.6 33.000 6000 BORSIG ZM 119 BTC Series X X X X OF 5000 2176 150 2. CENTRIFUGAL COMPRESSORS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min Compression Ratio (Per Stage) Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Catalog Page Reference Multiple Stage Fixed Stator Vanes Variable Stator Vanes min max min max psig bar hp kW min max ATLAS COPCO 140.000 45.200 30.000 (Includes Siemens CP STC-SV X X X OF 140 283.000 20.700 93.000 9000 STC-SR X X X X X X OF 29.600 34.000 37.000 725 50 124.400 66 1400 1810 125 45.000 13.000 100.25 8000 6000 3600 RT-Series X OF 188.200 30.500 1000 134.525 25.000 282.000 SPCP X X X OF 2330 49.500 60.000 COMPRESSION GMBH COMOTI 123 CCAE 9-125 X X X X X OF 65 87 10 700 CCAE 9-144 X X X X X OF 75 100 10 700 CCAE 9-300 X X X X X OF 150 200 10 1100 CCAE 12-300 X X X X X OF 150 200 13 1450 33 CCAE 21-300 X X X X X OF 150 200 22 1800 CCAE 15-300 X X X X X OF 160 215 15 1600 CRYOSTAR SAS * CM 400 / CM 300 X X X OF 58 666 6 2 1000 11.000 (Continues) Pipeline PDI X X OF 0 60.400 766.700 232 16 134. STC-SX X X X X OF 29.000 52.000 100.000 833 21.5 2 800 30.000 37.000 STC-ECO X X X OF 140 6000 4 167 3190 220 8300 6200 13.000 6750 16.000 0 45.000 GAS AND PROCESS 141 T-Series X OF 8830 38.000 of Siemens Power & Gas STC-GC X X OF 5900 236. GT-Series X X X OF 150 282.000 20.000 67.000 25 8000 870 60 40.000 4 10.000 DRESSER-RAND BUSINESS * STC-GV X X OF 880 590.000 CM 4-200 X X X OF 100 11.000 6000 STC-GVT X X OF 880 283.000 25 16.500 4 8000 2900 200 4 50.600 116 8 90.000 Division) * This company is not represented in the 2017 Supplement with a section describing its products.000 4 8000 14. part STC-SH X X X OF 140 353.5 50.400 766.500 WWW.000 1700 1500 103 50.000 9000 STC-SI X X OF 238.000 CM 6-200 X X X OF 75 25 2 1000 30.000 CM 2-200 / 300 X X X OF 42 100 10 2 700 30.000 250 1080 580 40 1. 2 175. CENTRIFUGAL COMPRESSORS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min Compression Ratio (Per Stage) Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Catalog Page Reference Multiple Stage Fixed Stator Vanes Variable Stator Vanes min max min max psig bar hp kW min max DRESSER-RAND BUSINESS * DATUM X X X OF 360.800 RFA. RCB.000 7200 10.000 13.000 10.000 27.3 up to 2.5 450 336 2950 3600 129 PAP Plus A1 X X X X OF 1500 3400 42 96 197 13.000 130.000 2500 725 50 40.6 up to 3. LLC 125.2 1250 932 2960 3600 PAP Plus CH X X X X OF 5500 11.000 156 312 207 14.000 93.000 56.000 PH X X OF 75.000 30.300 90 6.000 1671 3000 207 50.1 up to 2.000 20.000 1000 69 225.000 170.500 725 120. 115.710 62.150 17.5 4000 2980 1450 3600 PAP Plus EH X X X X OF 15.1 up to 2. PAP Plus BH X X X X OF 3500 5700 94 162 190 13.000 FIMA MASCHINENBAU GMBH * F1 Series X X X OF 3 6600 100 3 6800 5000 35.000 2100 800 55 15.000 DATUM C X X X X OF 59.000 1671 3000 207 27. RFBB X X X OF 12.250 8400 RBB.NET CTSS .800 34 ELLIOTT GROUP Third A X X X OF 400.000 DATUM P X X OF 59.000 13.000 6513 10.5 450 336 2950 3600 (Continues) Polaris P400+ X X X X OF 1600 3350 45 95 197 13.6 up to 3.500 Centrifugal X X X OF 230.000 Axial X X X OF 40.000 20.000 1133 24.000 56. M X X OF 530.000 18.000 8025 Cover.000 15.CTSSNET.000 FS-ELLIOTT CO.000 11.500 439 695 350 24.000 510 4900 338 20.000 135.000 192 MB X X OF 250.100 15.500 170 1005 4500 310 75.1 up to 2.200 15.520 38.500 TC X X OF 90.000 11.000 10.000 170. REB X X X OF 6000 35.000 1000 181.000 DATUM ICS X X X X OF 18.2 700 522 2960 3600 WWW.000 24.7 2000 1492 2960 3600 PAP Plus D X X X X OF 10.000 283 510 190 13.000 875.1 up to 3.5 5000 3700 1450 3600 Polaris P300+ X X X X OF 900 2090 25 59 175 12.2 700 520 2960 3600 * This company is not represented in the 2017 Supplement with a section describing its products.1 up to 2.300 17.700 360 1775 3220 222 75.000 17.000 20.000 13.000 690 225.000 37.000 F2 Series X X X OF 3 240 100 3 408 300 45. RDB.000 89.000 F3 Series X X X OF 3 5000 100 3 6800 5000 35. PAP Plus S1 X X X X OF 900 2200 25 59 175 12.777 80 5 125. 000 SRL (Overhung.000 16 651 1740 120 1.000 1500 15.000 3000 15.400 15.000 27 10.000 1500 20.000 1000 20.1 up to 2.000 3000 8000 AN (LNG Service) X X OF 58.150 1667 10.000 * This company is not represented in the 2017 Supplement with a section describing its products.000 3014 205 18.600 14.000 3000 11. X X OF 950 350. Blue-C X X X OF 52.1 up to 3.500 525.620 14.7 3000 2240 2960 3600 GARO * VC X X X OF 17 833 2 1 536 400 3000 6000 VAP X X X OF 17 833 90 1 2682 2000 3000 6000 CC (Galileo) X X X X OF 17 833 90 3 2682 2000 4000 42.500 1000 40.200 70.000 ICL Single Stage X X X OF 560 23.3 up to 2.860 1667 1890 130 54.860 353.200 16 290 3330 230 19.800 17.200 70.000 Single Stage) ICL X X X OF 560 10.5 1000 746 2960 3600 129 Polaris P600+ X X X X OF 4000 6500 113 184 190 13.000 675 46.290 8333 580 40 95.000 360 25 95.000 Single Stage) D-DH (Overhung.400 40.600 1500 18.5 22.6 19.000 PCL X X X OF 58.000 7000 18.600 14.400 40. CENTRIFUGAL COMPRESSORS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min Compression Ratio (Per Stage) Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Catalog Page Reference Multiple Stage Fixed Stator Vanes Variable Stator Vanes min max min max psig bar hp kW min max FS-ELLIOTT CO.500 320.500 170 326 207 14. Polaris P500+ X X X X OF 2600 4500 74 127 190 13.CTSSNET.000 35 BCL-LP/MP X X OF 29.600 1500 18.000 SRL X X X OF 206.NET CTSS .2 1500 1119 2960 3600 Polaris P700+ X X X X OF 6000 11.800 30.860 176.430 833 5075 350 54.000 3000 20.000 GE OIL & GAS * AN (Air Service) X X OF 58. LLC 125.000 3000 8000 BCL-HP (>350 bara) X X OF 6003 170 14.000 (<350 bara) MCL X X OF 294.000 HANWHA TECHWIN * SM6000 X X X OF 8200 12.550 1667 5000 360 25 95.000 3600 13. X OF 58.200 233 350 360 25 3200 2400 3600 SM5000 X X X OF 4700 8200 133 233 360 25 2130 1600 3600 SM4000 X X X OF 3000 4700 83 142 360 25 1280 955 3600 SM3000 X X X OF 1800 3000 50 84 360 25 850 635 3600 (Continues) SM2000 X X X OF 810 1800 23 50 145 10 350 260 3600 WWW.860 1667 1380 95 20.000 5833 1890 130 43.200 70.000 1500 50. 200 233 350 360 11 3200 2400 3600 SME5000 X X X OF 4700 8200 133 233 360 11 2130 1600 3600 SME4000 X X X OF 3000 4700 83 142 360 11 1280 955 3600 SME3000 X X X OF 1800 3000 50 84 360 11 850 635 3600 36 SA3100 X X X X OF 1880 3235 53 92 160 11 540 780 3600 SA2000 X X X X OF 770 1500 22 42 145 10 350 260 3600 SE-32 X X X X OF 76 60 1070 800 3600 SE-45 X X X X OF 336 60 4430 3300 3600 SE-65 X X X X OF 550 60 6970 5200 1800 SE-82 X X X X OF 833 60 11. CENTRIFUGAL COMPRESSORS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min Compression Ratio (Per Stage) Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Catalog Page Reference Multiple Stage Fixed Stator Vanes Variable Stator Vanes min max min max psig bar hp kW min max HANWHA TECHWIN * SM6100 X X X OF 8800 15.000 3000 18.000 250 417 188 13 3200 2500 3600 SM5100 X X X OF 5300 8800 150 250 188 13 2130 1500 3600 SM4100 X X X OF 3250 5300 92 150 188 13 1200 930 3600 SM3100 X X X OF 2000 3250 55 92 188 13 780 580 3600 SME6000 X X X OF 8200 12.000 2500 18.000 * This company is not represented in the 2017 Supplement with a section describing its products.800 1800 HITACHI LTD.000 WWW.800 1800 SE-110 X X X X OF 2320 60 29.000 3500 18.200 8350 1800 SE-90 X X X X OF 1390 60 18.CTSSNET.200 21.500 13.000 3MCH X X OF 8 6000 45 5 50.NET CTSS .000 2MCH X X OF 8 6000 45 5 50.000 3000 18.000 PCH X X X OF 8 6000 120 5 30. * 2BCH X X OF 3 1700 750 10 50. 3BCH X X OF 3 1700 750 10 50.000 3000 14.000 MCH X X X OF 8 6000 45 10 50.000 3000 18.000 3500 18.000 BCH X X X OF 3 1700 750 10 50. 713 25.000 15.427 360 720 29 2 3 2146 1600 5000 33.757 1260 2400 29 2 3 6705 5000 5000 33.000 Howden ČKD RMX X X OF 2000 88.000 Howden SG60 X X X OF 14.000 INGERSOLL RAND * Centac CH 5 X X X OF 1300 3000 42 80 35 3 3 350 270 3600 Centac CH 6 X X X OF 3000 6000 90 160 35 3 3 350 600 3600 Centac C400 X X X OF 1500 2350 42 67 125 8.595 120 300 29 2 3 671 500 5000 33.497 84.189 40.000 Howden SG92 X X X OF 33.000 Howden SG45 X X X OF 8476 19.903 63.6 max of 3 500 400 3600 (Continues) Centac C700 X X X OF 2000 4100 60 120 150 10 max of 3 900 700 3600 WWW.000 30 370 23 2 1350 1000 12.832 31.000 20.000 Howden ČKD RLV X X X OF 1000 13.951 33.CTSSNET.832 180 420 29 2 3 1073 800 5000 33.000 10 370 2900 2 9400 7000 3000 27.070 240 540 29 2 3 1341 1000 5000 33.500 10.000 Periflow X X X OF 60 3026 2 86 3000 200 3 1340 1000 500 6000 Howden ČKD RL X X X OF 2500 70.903 480 960 29 2 3 2682 2000 5000 33.000 3000 27.000 Howden ČKD RP X X OF 1800 88.000 Howden ČKD RD X X X OF 50.000 3000 37.000 Howden SG30 X X X OF 4238 8476 120 240 29 2 3 603 450 5000 33.784 420 900 29 2 3 2414 1800 5000 33.000 3000 27.000 280.000 Howden ČKD RKB X X OF 7000 70.000 Howden SG52 X X X OF 12.000 * This company is not represented in the 2017 Supplement with a section describing its products.000 Howden ČKD RS X X OF 350 13.000 Howden SG40 X X X OF 6357 14.000 Howden SG70 X X X OF 21.000 3000 27.100 12.000 60 2500 145 2 16.000 Howden SG105 X X X OF 44.000 50 8000 508 2 33.973 720 1500 29 2 3 4023 3000 5000 33.NET CTSS . Howden ČKD RMX X X OF 1800 280.000 200 200 2900 2 27.000 70 2000 26 2 3350 2500 3000 27.000 1400 8000 20 1 13. CENTRIFUGAL COMPRESSORS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min Compression Ratio (Per Stage) Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Catalog Page Reference Multiple Stage Fixed Stator Vanes Variable Stator Vanes min max min max psig bar hp kW min max HOWDEN * Howden SG26 X X X OF 4238 6357 120 180 29 2 3 268 200 5000 33.000 50 2500 508 2 20.000 3000 27.500 25.427 52.567 960 1800 29 2 3 5364 4000 5000 33.259 600 1140 29 2 3 3487 2600 5000 33.000 27.000 37 Howden SG80 X X X OF 25.000 Howden SG65 X X X OF 16.000 Howden SG35 X X X OF 4238 10. 7 275 19 max of 3 3500 2600 3600 TA20000 X X X OF 12.3 226.000 1800 (Continues) MSG 18 X X X OF 45.2 509.1 150 10.000 1274.000 59.000 7500 1800 MSG 12/16 X X X OF 30.7 1160 80 max of 3 5500 4100 3600 TA2040 X X X OF 1500 1800 42.000 141. TA-NX 8000 X X X OF 5000 11.2 1450 100 max of 3 10.8 1450 100 max of 3 6500 4900 3600 MSG 8/9 X X X OF 16.6 311.750 232.0 610 42 max of 3 800 600 3600 TA6040 X X X OF 4500 6000 127.6 600 41 max of 3 20.000 467.CTSSNET.5 max of 3 2250 1700 3600 TA-NX 12000 X X X OF 7500 18.000 24.4 509.3 991.500 30.000 1800 WWW.500 35.000 80.1 150 10 max of 3 350 250 3600 TAC2000 X X X OF 550 1700 15.6 1670.000 849.000 339.000 212.8 679.5 51.9 1450 100 max of 3 15.2 48.000 350 850 150 10 max of 3 6000 4500 1800 Centac 2CIISB X X X OF 3000 4600 90 130 350 24 max of 3 1750 1300 3600 Centac C750 X X X OF 1800 2100 50 60 610 42 max of 3 1000 700 3600 Centac C1050 X X X OF 3800 3800 115 115 610 42 max of 3 1500 1150 3600 38 Centac 3C X X X X OF 5000 10.000 142 285 375 26 max of 3 3000 2250 1800 Centac 4C X X X X OF 9000 15.NET CTSS .000 255 425 375 26 max of 3 4500 3350 1800 TA2000 X X X OF 500 1700 14.000 15.000 198.0 max of 3 4500 3350 3600 MSG 2/3 X X X OF 2500 10.6 150 10 max of 3 1750 1300 3600 TA11000 X X X OF 8200 14.3 max of 3 350 250 3600 TA3000 X X X OF 2000 4000 56.5 210 14.4 169.6 48.000 70.8 580 40.9 610 42 max of 3 2250 1700 3600 * This company is not represented in the 2017 Supplement with a section describing its products.000 255 425 150 10 max of 3 3500 2600 1800 Centac 5CII X X X X OF 12.000 11.4 2265.2 417.3 150 10 max of 3 800 600 3600 TA6000 X X X OF 4000 8000 113.2 1450 100 max of 3 5500 4100 3600 MSG 4/5 X X X OF 7000 18.6 113.8 283. CENTRIFUGAL COMPRESSORS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min Compression Ratio (Per Stage) Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Catalog Page Reference Multiple Stage Fixed Stator Vanes Variable Stator Vanes min max min max psig bar hp kW min max INGERSOLL RAND * Centac C800 X X X OF 2300 5300 65 150 185 13 max of 3 1250 900 3600 Centac C950 X X X OF 4150 6500 120 185 150 10 max of 3 1500 1150 3600 Centac C1000 X X X OF 4500 7500 127 212 150 10 max of 3 1750 1300 3600 Centac 3CII X X X X OF 6000 9000 170 255 175 12 max of 3 2000 1500 3600 Centac C3000 X X X X OF 9000 15. 000 AR X X X X X OF 29.000 50.000 833.000 900.000 50.3 290 20 max of 3 25.000 MITSUBISHI HEAVY 127.000 DH Series X X OF 1059 105. 139 BERLIN) AG.000 835 25.000 5000 18. CENTRIFUGAL COMPRESSORS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min Compression Ratio (Per Stage) Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Catalog Page Reference Multiple Stage Fixed Stator Vanes Variable Stator Vanes min max min max psig bar hp kW min max INGERSOLL RAND * MSG 25 X X X OF 50.000 870 60 2.000 1500 100.000 2900 200 2.000 15.000 900.0 125 8.0 583.000 835 25.CTSSNET.450 362 25 165.0 833.151 30 5670 700 50 21.000 3000 60.100 100.000 6000 14.600 334.000 80.0 1500.6 max of 3 6000 4500 1800 MSG LMAC 50 X X X OF 29.000 24.200 30. RIO X X OF 10. ZÜRICH.000 1416.900 30 3000 1300 90 33.5 40. A.750 50 7500 1420 100 67.000 150 3300 29 2 5400 RG X X X X OF 1000 400.000 RV X X X OF 450 50.500 25.800 1160 80 80.000 * This company is not represented in the 2017 Supplement with a section describing its products.400 583.000 3600 250 80.000 1500 20. RIKT.000 39 VG / VGP Series X X X OF 1765 264.500 53.000 Integrally Geared X X X OI 600.0 134. AK.500 300 21 100.000 135.000 1000 18.000 15.000 3000 MOPICO (RM) X X X X OF 1100 18.600 29.000 30 500 2200 150 18.000 HOFIM X X X OF 350 18.951 30 1670 5000 350 28.000 900.000 RH X X X OF 450 417.100 100.000 MAN DIESEL & TURBO SE 138.000 3 5400 14.000 3000 20.000 17.0 3823.000 1800 MSG LMAC 20 X X X OF 11.000 1800 KOBE STEEL (KOBELCO) Forth VH Series X X OF 1059 58.500 440.6 max of 3 15.800 20.000 11. RIK.000 50.000 Cover VGS/VGSP Series X X X OF 1765 264. AV X X X OF 29.000 INDUSTRIES COMPRESSOR 201 INTERNATIONAL V-Type X X X OF/OI 212.000 5000 18.000 (OBERHAUSEN.450 220 15 125.000 50.0 134.500 1000 2.0 125 8.000 20.000 10 500 4350 300 18.750 50 7500 1420 100 67.000 WWW.000 300 12.NET CTSS .000 12.6 max of 3 4000 3000 3600 MSG LMAC 30 X X X OF 20.000 3000 40.000 V-VS-VSS Series X X X OF 1059 200. AKF X X X OF 29.000 835 25.000 28 12.450 362 25 120.000 TURBAIR (RC) X X OF 5300 115.0 125 8.000 RB X X X OF 95 190.000 13 1400 2175 150 67.000 19.000 13 11. H-Type X X X OF/OI 424.500 1000 107. 500 283 524 450 31 17.500 C45 Pipeline X X X 3800 18.000 21 510 3750 259 41.000 26 311 1600 186 16.000 SHIPBUILDING V Series X X OI 353 35.640 65.000 61 680 1600 110 34.800 Mover Tab C33 X X X 800 9000 23 269 2700 186 17.000 C65 Pipeline X X X 5000 24.000 14.500 44 481 1600 124 35.800 8055 9410 M_55B X X OF 10.450 M_38A X X OF 7000 12.900 32.800 14.000 18.300 C41 X X X 750 18.000 * This company is not represented in the 2017 Supplement with a section describing its products.000 MA Series X X OI 353.000 20 991 3000 207 87.900 7000 SUNDYNE CORP.900 M_26A X X OF 3300 5600 94 159 600 41 5000 3730 13.968 26.100 10.200 198 346 600 41 10.000 12.000 170 20. CENTRIFUGAL COMPRESSORS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min Compression Ratio (Per Stage) Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Catalog Page Reference Multiple Stage Fixed Stator Vanes Variable Stator Vanes min max min max psig bar hp kW min max MITSUI ENGINEERING & * H Series X X OI 353 177.610 M_26B X X OF 2100 3900 60 110 600 41 5000 3730 16.270 12.400 4400 304 4 4000 3000 5000 50.976 31.000 68 850 2250 155 76.100 100.000 C40 X X X 1000 9500 18 269 2500 172 29. * LMC X X X OF 50 8000 85 13.300 12.000 115 1274 1600 110 77.300 14.900 32.481 22.980 M_25A X X OF 1000 2650 28 75 600 41 2500 1865 20.CTSSNET.915 23.300 C50 X X X 2000 20.900 19.000 SOLAR TURBINES INC.000 12 708 3000 207 52.223 12.500 C75 Pipeline X X X 2420 30.333 39.000 C61 X X X 2800 35.600 2160 149 4 400 300 2950 34.200 C40 Pipeline X X X 1500 11. YORK/FRICK (JCI) * M_25B X X OF 400 1800 11 51 600 41 2500 1865 24.000 40 C51 X X X 2000 25.097 9800 23.000 Pinnacle X X X X OF 100 12.000 10 5000 725 50 42.900 7720 WWW.800 8055 11.707 57.300 12.100 15.206 26.930 M_38B X X OF 4600 8400 130 238 600 41 10.000 BMC X X X OF 50 8000 85 13.NET CTSS .600 2160 149 4 400 300 2950 34.300 10 1000 9400 650 42. Prime C16 X X 150 1800 4 62 3500 241 13.000 9200 145 10 7 134.000 57 566 1500 103 31.730 8860 C85 Pipeline X X X 4100 45.138 56.400 10. 000 1305 90 -196 to 60 9655 7200 4800 14. 115.05 TC 500 X X X OI 300 8100 8 230 100.000 37.000 1.832 5500 180.000 4700 TH-140 X 1.500 6700 Cover.05 MTC 200 X X X OF 30 630 1 18 6500 158.300 30.05 TC 120 X X X OI 30 630 1 18 6500 158.000 793.500 360.220 50 3.18 1.000 23.18 WWW.000 .500 360.000 800.4 600 3000 200 -220 to 500 18 30.4 760 18.CTSSNET.05 TC 200 X X X OI 50 1600 1 45 12.05 TC 400 X X X OI 210 5600 6 160 66.000 396.000 1015 70 -196 to 60 1234 920 11.000 13.05 41 TP 200 X X X OI 30 260 1 8 6500 66.500 (Continues) .000 870 60 -196 to 60 1234 920 21.05 MTC 400 X X X OF 115 2800 3 80 32.696 30.18 1.000 501.000 3000 30.05 TP 300 X X X OI 30 260 1 8 6500 66.000 1450 100 -196 to 60 8046 6000 7000 35.000 396.000 30. Radial Inflow X X X 50 20.000 1015 70 -196 to 60 215 160 5700 8200 .000 1450 100 -196 to 60 4573 3410 12.000 . 1.18 1.832 5500 180.000 3000 30.000 3000 30.000 . TURBOEXPANDERS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range Mass Flow 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min lb/hr kg/h Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Multiple Stage Fixed Stator Vanes Variable Stator Vanes Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Temp (°C) Catalog Page Reference Expansion Ratio (Per Stage) min max min max min max min max psig bar hp kW min max ATLAS COPCO GAS 140.18 1.4 760 60.000 19.000 1015 70 -196 to 60 939 700 11.000 325.000 38.700 .696 30.18 1.000 1.18 1.05 MTC 500 X X X OF 210 5600 6 160 66.663 14.000 .000 45.000 1450 100 -196 to 60 7510 5600 9700 32.000 AND PROCESS 141 Expanders ELLIOTT GROUP Third TH-85 X X 467.663 14.05 MTC 300 X X X OF 50 1600 1 45 12.000 2.000 3000 100.000 1.821 45.18 1.110 50 3.05 TC 300 X X X OI 115 2800 3 80 32.000 .763.400 .000 1015 70 -196 to 60 268 200 10.05 TP 120 X X X OI 30 260 1 8 6500 66.105.600 .500 66.733 3000 72.000 4000 CRYOSTAR SAS * 1.000 793.4 760 40.830 50 3.000 800.680 50 3.000 771.000 1.000 1305 90 -196 to 60 5364 4000 7600 21.18 * This company is not represented in the 2017 Supplement with a section describing its products.000 1015 70 -196 to 60 268 200 5800 22.763.600 .000 5800 192 TH-120 X 1.NET CTSS .18 1.4 760 25.260.777.733 3000 72.700.600 .000 66.000 211.000 1160 80 -196 to 60 9655 7200 1400 12. TH-100 X X 718.18 1.18 1. 500 360.18 1.000 80.000 441.000 18.000 800.000 1.3 65.836 13.800 .18 1.500 45.000 53 3.000 580 40 -196 to 60 17.000 1015 70 -196 to 60 916 683 11.000 760.000 1.05 42 TG 500 X X X X OI 300 8100 8 230 100.CTSSNET.000 95.000 218 15 760 15 15.500 3600 WWW.000 345.05 TG 300 X X X X OI 115 2800 3 80 32.000 2.000 35 2.5 760 3.000 53 3.3 25.05 TG 2/200 X X X X OI -196 to 60 2682 2000 23.400 6000 E-138 X 249.821 45.000 350.000 52.000 .000 35 2.7 760 5.000 580 40 -196 to 60 3084 2300 3000 12.000 27.000 20.000 120.500 75.18 1.663 14.0 20.000 992.000 793.000 44.000 4.930 BUSINESS (Part of Siemens Power E-520 X X 98.696 30.900 7500 * This company is not represented in the 2017 Supplement with a section describing its products.000 354.5 760 3.05 TG 120 X X X X OI 30 630 1 18 6500 158.200. E-132 X 60.05 MTC 600 X X X OF 300 8100 8 230 100.000 730.18 1.609.000 364.000 218 15 760 15 23.000 1.777.000 113.000 200.000 35 2.000 298.260.900.000 20.000 7.18 1.18 DRESSER-RAND * E-516 X X 58.05 TG 200 X X X X OI 50 1600 1 45 12.000 26.500 10.000 14.600 33.5 760 3.05 TG 2/500 X X X X OI -196 to 60 2193 1635 23.223.260.000 17.000 1015 70 -196 to 60 3621 2700 7400 30.800 4000 E-156 X 780.000 1305 90 -196 to 60 10.000 44.100 66.000 1.000 11.7 760 5.000 22.000 1.850 .763.000 .000 2.777.000 218 15 760 15 28.000 396.000 159.000 53 3.000 272.000 2.200 8400 E-238 X X 351.0 60.600 6000 E-248 X X 600.3 15.0 30.000 236.000 364.18 1.000 165.733 3000 72.000 580 40 -196 to 60 8583 6400 3000 13.900 7100 E-232 X X 115.700 4000 E-148 X 520.200 8400 E-526 X X 265.3 40.000 1015 70 -196 to 60 1502 1120 11.NET CTSS .000 35 2.000 29.600 27. TURBOEXPANDERS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range Mass Flow 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min lb/hr kg/h Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Multiple Stage Fixed Stator Vanes Variable Stator Vanes Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Temp (°C) Catalog Page Reference Expansion Ratio (Per Stage) min max min max min max min max psig bar hp kW min max CRYOSTAR SAS * 1.18 1.18 1.000 135.000 48.000 11.862 8100 4850 10.500 .000 165.000 450.200 8780 & Gas Division) E-522 X X 209.000 165.832 5500 180.300 3471 3471 .821 45.600 .000 771.000 .05 TG 400 X X X X OI 210 5600 6 160 66.000 218 15 760 15 10.5 760 3.05 TG 800 X X X X OI 360 9712 10 275 175.500 .600 27.7 760 5.000 555. TURBOEXPANDERS 2017 Basic Specifications Axial Flow Radial Flow Thermal Inlet Flow Range Mass Flow 2017 EDITION Manufacturer Maximum Input Power Speed Range (rpm) MAWP Maximum Allowable Working Pressure acfm m3/min lb/hr kg/h Single Stage Multiple Stage Horizontally Split Vertically Split Integral Gear Integral Electric Multiple Stage Fixed Stator Vanes Variable Stator Vanes Model Designation OF = Oil Free OI = Oil Injected Single Stage Multiple Stage Temp (°C) Catalog Page Reference Expansion Ratio (Per Stage) min max min max min max min max psig bar hp kW min max GE OIL & GAS * ED X X X X OF 177 2943 5 83 3335 230 -270 to 315 12.0 8046 6000 1500 120,000 NUOVO PIGNONE EC X X X OF 177 64,744 5 1833 3335 230 -271 to 316 12.0 20,115 15,000 1500 120,000 EG X X X X X OF 177 64,744 5 1833 3335 230 -272 to 317 12.0 46,936 35,000 1500 120,000 1.5 - FEX81 X X OF 162,000 342,000 73,482 155,129 50 3.45 760 6798 5000 7000 3.3 1.5 - FEX97 X X OF 198,000 468,000 89,811 212,281 50 3.45 760 13,500 10,000 6500 3.3 1.5 - FEX107 X X OF 288,000 900,000 130,635 408,233 50 3.45 760 22,950 17,000 5100 3.3 43 1.5 - FEX125 X X OF 396,000 1,044,000 179,623 473,550 50 3.45 760 33,750 25,000 4000 3.3 1.5 - FEX142 X X OF 540,000 1,600,000 244,940 725,748 50 3.45 760 59,400 44,000 3600 3.3 HANWHA TECHWIN * SG-ST2400 X OI 180 420 5 12 35,700 128,600 16,200 58,300 728 50 [-92/-163] 7 1215 905 25,600 32,000 SG-ST2800 X OI 210 500 6 14 23,800 85,800 10,800 38,900 728 50 [-92/10] 7 1480 1105 28,000 35,000 L.A. TURBINE * L1000 350 3000 206 -195 to 260 1070 800 105,000 L2000 880 3000 206 -195 to 260 2000 1500 52,000 L3000 2350 3000 206 -195 to 260 4000 3000 31,000 L4000 4400 3000 206 -195 to 260 8000 6000 29,000 * This company is not represented in the 2017 Supplement with a section describing its products. L5000 5900 3000 206 -195 to 260 13,400 10,000 18,000 L6000 9400 3000 206 -195 to 260 18,700 14,000 15,000 MAN DIESEL & 138, EN X X 926,000 420,000 232 16 575 15 40,000 30,000 20,000 TURBO SE 139 (OBERHAUSEN) EH X X 794,000 360,000 58 4 760 10 30,000 22,000 24,000 ER X X X X 1,235,000 560,000 348 24 to 500 5 67,000 50,000 50,000 SIEMENS * STC-GT X X X X X OI 5297 353,146 150 10,000 218 15 550 16 60,345 45,000 4400 25,000 WWW.CTSSNET.NET CTSS RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max ABC COMPRESSORS * HA X X X OI/OF 20 90 2465 170 5500 24,500 4 600 450 370 750 HP X X X OI/OF 50 300 2465 170 22,000 98,000 4 1900 1400 370 750 ARIEL CORPORATION JGM:P X X X X OI 9000 621 7000 31,138 170 127 1800 JGN:Q X X X X OI 9000 621 11,000 48,930 280 209 1800 JG:A X X X X OI/OF 9000 621 11,000 48,930 840 626 1800 Compressor Tab JGR:J X X X X OI/OF 9000 621 23,000 102,309 1860 1387 1800 JGH:E X X X X OI 10,000 690 32,000 142,343 3210 2394 1500 JGK:T X X X X OI/OF 10,000 690 40,000 177,929 3900 2908 1500 44 JGC:D:F X X X X OI/OF 10,000 690 60,000 266,893 6210 4631 1400 KBU:Z X X X X OI/OF 10,000 690 80,000 355,858 7800 5816 1200 KBB:V X X X X OI/OF 10,000 690 100,000 444,822 10,000 7457 900 ATLAS COPCO GAS 140, HX/HN / HNX (1) X X OF 25 6000 0.7 167 2175 150 15,700 70,000 4 750 560 400 1000 AND PROCESS 141 DM X OF 3 38 0.1 1.1 6480 447 2240 10,000 4 50 37 1000 1450 (1) Engineered product CU/CT X OI 138 936 3.9 26.5 7000 480 7194 32,000 4 255 190 570 1230 option with up to 6 throws above 560 kW. Intermech BBR/ X X OI 15 220 0.4 6.2 4525 312 22,000 97,900 4 600 450 1200 1800 FBR/VIP GG X OI 45 400 1.25 11.7 232 16 16 175 130 1200 4500 BAUER KOMPRESSOREN * VERTICUS 5 Series GMBH, GERMANY X OI 3 7 0.1 0.2 7250 500 20 15 985 1485 (Air Cooled) VERTICUS 5 * This company is not represented in the 2017 Supplement with a section describing its products. Booster Series X OI 7 28 0.2 0.8 5000 350 20 15 985 1485 (Air Cooled) K22 to K28 Series X OI 30 240 0.9 6.8 7250 500 150 110 985 1485 (Air Cooled) IB23 Series X OI 46 53 1.3 1.5 5000 350 50 37 985 1485 (Air / Water Cooled) GIB23 Booster Series X OI 47 220 1.3 6.2 5000 350 50 37 985 1485 (Continues) (Air / Water Cooled) WWW.CTSSNET.NET CTSS RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max BAUER KOMPRESSOREN * I24 Series X OI 74 74 2.1 2.1 5000 350 75 55 985 1485 GMBH, GERMANY (Water Cooled) GIB24 Booster Series X OI 78 424 2.2 12.0 5000 350 122 90 985 1485 (Water Cooled) I26 Series X OI 80 120 2.3 3.4 5800 400 122 90 985 1485 (Water Cooled) GIB26 Booster Series X OI 173 720 6.5 14.3 5800 400 340 250 985 1485 (Water Cooled) I52 Series X OI 160 240 4.5 6.8 5000 350 218 160 985 1485 (Water Cooled) GIB52 Booster Series X OI 346 826 9.8 23.4 5000 350 428 315 985 1485 45 (Water Cooled) BLACKMER * HD162/HD163 X OF 7 17 335 23 2650 5 10 400 825 HD172/HD173 X OF 4 8 600 41 2650 5 10 400 825 HDL172/HDL173 X OF 4 8 600 41 2650 5 10 400 825 (Water Cooled) HD362/HD363 X OF 15 36 335 23 3400 5 15 400 825 HDL362/HDL363 X OF 15 36 335 23 3400 5 15 400 825 (Water Cooled) HDL322 X OF 4 9 985 68 3400 5 15 400 825 (Water Cooled) HDL342/HDL343 X OF 7 16 750 51 3400 5 15 400 825 (Water Cooled) HD372/HD373 X OF 10 24 600 41 3400 5 15 400 825 * This company is not represented in the 2017 Supplement with a section describing its products. HDL372/HDL373 X OF 10 24 600 41 3400 5 15 400 825 (Water Cooled) HD602/HD603 X OF 27 64 335 23 5000 5 40 400 825 HDL602/HDL603 X OF 27 64 335 23 5000 5 40 400 825 (Water Cooled) HDL642/HDL643 X OF 13 32 735 51 5000 5 40 400 825 (Water Cooled) (Continues) HD612/HD613 X OF 23 54 400 28 5000 5 40 400 825 WWW.CTSSNET.NET CTSS RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max BLACKMER * HDL612/HDL613 X OF 23 54 400 28 5000 5 40 400 825 (Water Cooled) HD942/HD943 X OF 52 125 335 23 7000 5 50 400 800 HDL942/HDL943 X OF 52 125 335 23 7000 5 50 400 800 (Water Cooled) NG162/NGS162 X OF 7 17 335 23 2650 5 10 400 825 NG172/NGS172 X OF 4 8 600 41 2650 5 10 400 825 NG362/NG362 X OF 15 36 335 23 3400 5 15 400 825 NG372/NGS372 X OF 10 24 600 41 3400 5 15 400 825 NG602/NGS602 X OF 27 64 335 23 5000 5 40 400 825 46 NG642/NGS642 X OF 13 32 500 34 5000 5 40 400 825 NG612/NGS612 X OF 23 54 400 28 5000 5 40 400 825 NG942/NGS942 X OF 52 125 335 23 7000 5 50 400 800 BORSIG ZM 119 BX15 X X X OF/OI 333 1450 100 51,931 231,000 4 6656 4964 800 1200 COMPRESSION GMBH BX22 X X X OF/OI 14,500 1000 29,000 129,000 4 1418 1058 400 750 BX32 X X X OF/OI 14,500 1000 64,745 288,000 4 3901 2909 270 600 BX40 X X X OF/OI 14,500 1000 129,940 578,000 4 9459 7054 200 450 BX45 X X X OF/OI 14,500 1000 207,723 924,000 4 16,080 11,991 150 400 BX50 X X X OF/OI 2000 14,500 1000 332,268 1,478,000 4 28,280 21,089 110 350 BURCKHARDT 144 BY X X X OF/OI 2300 60 14,500 1000 20,000 90,000 4 1000 800 425 850 COMPRESSION AG * This company is not represented in the 2017 Supplement with a section describing its products. CY X X OF/OI 2300 60 14,500 1000 20,000 90,000 4 1000 800 425 850 BS X X X OF/OI 7100 200 14,500 1000 45,000 200,000 4 3200 2320 300 750 PROCESS GAS CS X X OF/OI 4700 130 14,500 1000 45,000 200,000 4 3200 2320 300 600 COMPRESSOR API 618 BX X X X OF/OI 10,600 300 14,500 1000 78,500 350,000 4 7200 5400 260 520 BA X X X OF/OI 15,900 450 14,500 1000 124,000 550,000 4 12,700 9500 250 500 BC X X X OF/OI 19,400 550 14,500 1000 202,000 900,000 4 21,700 16,000 300 450 (Continues) BE X X X OI 23,000 650 14,500 1000 337,000 1,500,000 4 42,100 31,000 300 429 WWW.CTSSNET.NET CTSS RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max BURCKHARDT 144 1D130 X OF 300 10 4640 300 4 100 76 450 750 COMPRESSION AG LABY COMPRESSORS 1D150 X OF 300 10 730 50 4 160 120 360 600 2D100 X X OF 300 10 730 50 4 160 120 600 1000 2D140 X X OF 400 10 290 20 4 233 174 450 750 2D160 X X OF 700 20 1160 80 4 407 304 450 750 2D200 X X OF 1000 30 750 52 4 643 480 360 600 2DL200 X X OF 2200 60 290 20 4 643 480 360 600 2D205 X X OF 800 20 3630 250 4 938 700 360 600 47 2D250 X X OF 2500 70 1740 120 4 2279 1700 312 520 2DL250 X X OF 2700 80 360 25 4 2370 1770 312 520 3D200 X X OF 1900 50 1020 70 4 657 490 360 600 4D225 X X OF 2700 80 810 56 4 973 726 360 600 4D250 X X OF 4700 130 3050 210 4 1374 1025 312 520 4D300 X X OF 4000 110 1280 88 4 2055 1533 270 450 4D375 X X OF 4800 140 730 50 4 2755 2055 228 380 6D375 X X OF 5400 150 870 60 4 2755 2055 228 380 2K90 X X OF 300 10 610 42 4 154 115 600 1000 * This company is not represented in the 2017 Supplement with a section describing its products. 2KL90 X X OF 300 10 610 16 4 154 115 600 1000 2K105 X X OF 500 10 1160 80 4 252 188 600 1000 2K140 X X OF 800 20 730 50 4 406 303 450 750 2KL140 X X OF 800 20 232 16 4 406 303 450 750 2K158 X X OF 700 20 460 32 4 665 485 450 750 (Continues) 2K160 X X OF 1200 30 2180 150 4 665 485 450 750 WWW.CTSSNET.NET CTSS 5/10 X Ol 1 3 10 10 30 1450 3600 ECS 10/10 X Ol 4 8 10 10 37 1050 2000 ECS 15/10 X Ol 4 11 10 10 75 1050 3200 ECS 20/10 X Ol 4 13 10 10 90 1050 3700 (Continues) ECS 25/10 X Ol 7 17 10 10 110 1000 1700 WWW.850 20.760 3500 4 10.NET CTSS . RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max BURCKHARDT 144 2K250 X X OF 800 20 1670 115 4 2226 1660 300 500 COMPRESSION AG 3K140 X X OF 700 20 580 90 4 665 485 450 750 3K160 X X OF 1800 950 640 44 4 665 485 450 750 4K165 X X OF 2000 60 960 66 4 1397 1042 450 750 HYPER COMPRESSORS H X X X OI 14.100 2410 50.760 3500 4 26.600 1210 50. 275 X X X OI 300 21 40 30 900 2400 312 X X X OI 300 21 40 30 900 2400 350 X X X OI 1100 76 150 112 900 2400 410 X X X OI 1100 76 225 168 900 2400 500 X X X OI 1100 76 338 252 900 2400 700 X X X OI 1100 76 900 671 900 1800 1000 X X X OI 1100 76 2910 2170 900 1200 * This company is not represented in the 2017 Supplement with a section describing its products.000 139 231 K X X X OI 85.760 3500 4 51.CTSSNET. 1400 X X X OI 1200 83 4500 3356 600 900 COMOTI 123 ECS 2.000 129 215 LABY GI LP190 X X X OF/OI 45 4988 344 30 135 4 2330 1750 450 750 48 LP250 X X X OF/OI 110 4988 344 72 322 4 5320 4000 312 520 COMBINED HEAT & * 250 X X X OI 300 21 30 22 900 2400 POWER INC.200 400 50.000 38.700 8000 154 257 F X X X OI 42. 6 400 825 Vertical Series Model 291 X OF 335 23 3600 1633 15 11 400 825 Vertical Series Model 491 X OF 335 23 4000 1814 15 11 400 825 Vertical Series Model 491-3 X OF 600 41 4000 1814 15 11 400 825 (Continues) Vertical Series WWW.361 75 55.5/16 X Ol 1 3 16 16 40 1450 3600 ECS 20/25 X Ol 2 7 25 25 75 1700 5100 ECS 15/30 X Ol 3 10 30 30 132 1200 3600 ECS 20/30 X Ol 2 6 30 30 132 1600 4800 ECS 30/30 X Ol 2 5 30 30 160 1600 4600 ECS 35/30 X Ol 17 24.5 5. 239 Horizontal Series Model 91 X OF 335 23 3600 1633 7.5 30 15 250 2000 3000 49 ECS 60/30 X X Ol 27 42 30 30 450 2000 3000 ECS 80/30 X Ol 40 56 30 30 500 2000 3000 ECS 5/40 B X Ol 2 7 40 14 90 2000 3000 CU 64G X Ol 1 4 26 26 52 2296 9182 CU 90G X Ol 2 8 26 26 98 1632 6529 CU 128G X Ol 4 16 26 26 193 1148 4591 CU 64 HP(GM) X Ol 2 7 45 20 90 2296 9182 CU 90 HP X Ol 2 10 45 20 130 1632 6529 CU 200 X Ol 25 50 45 20 500 1148 4591 CORKEN INC.9 400 1200 * This company is not represented in the 2017 Supplement with a section describing its products. 238.CTSSNET.NET CTSS . RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max COMOTI 123 ECS 30/10 X Ol 7 23 10 10 132 1000 2100 ECS 60/10 X Ol 13 42 10 10 250 600 1700 ECS 75/10 X Ol 42 52 6 6 315 2000 3000 ECS 2. HG600/THG600 X X X OI/OF 1650 21 7500 33. 000 146.000 356.NET CTSS .880 4 7200 5369 500 1500 HOSS (Super HOS) X X X OF/OI 11.100 4 180 134 300 450 (Continues) BDC-I2H X X OF/OI 12.000 333.000 758 60.000 200.500 4 1300 969 750 1800 BUSINESS (Part of Siemens Power & BVIP X X X OF/OI 11.000 827 10.CTSSNET.000 758 24.000 827 80. Model 691 X OF 335 23 7000 3175 35 26 400 825 239 Vertical Series Model 691-4 X OF 600 41 7000 3175 35 26 400 825 Vertical Series D891 Vertical X 450 31 7000 3175 45 34 400 825 T891 Vertical X OF 450 31 7000 3175 15 11 400 825 Model 151 X OF 1200 83 3600 1633 15 11 400 825 Vertical Series Model 191 X OF 600 41 3600 1633 15 11 400 825 Vertical Series Model 351 50 X OF 1200 83 4000 1814 15 11 400 825 Vertical Series Model 391 X OF 600 41 4000 1814 15 11 400 825 Vertical Series Model 551 X OF 1000 69 7000 3175 35 26 400 825 Vertical Series Model 591 X OF 600 41 7000 3175 35 26 400 825 Vertical Series D791 Vertical X 600 41 7000 3175 45 34 400 825 T791 Vertical X OF 600 41 7000 3175 45 34 400 825 DRESSER-RAND * AVIP X X X OF/OI 11.600 96.000 758 33.200 45.000 758 15. MOS X X X OF/OI 11. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max CORKEN INC.000 758 75.600 4 8700 6488 500 1200 7"ESH/ESV X OF/OI 12.000 266.000 827 21.000 4 8200 6115 300 600 WWW.100 4 4440 3281 500 1500 HOS X X X OF/OI 11.780 4 2880 2148 600 1800 * This company is not represented in the 2017 Supplement with a section describing its products.000 758 45.640 4 2125 1585 600 1500 Gas Division) CVIP X X X OF/OI 11.400 68.400 4 70 52 466 600 11"ESH X OF/OI 12.200 107. 238. 500 4 2250 1678 277 600 HHE-VB X X OF/OI 12.750 670.NET CTSS .200 45.000 310 SHM X X X X OF/OI 80.000 133.800 4 1000 746 390 600 PHE X X OF/OI 12. * AM.690 7980 1200 SHMB X X X X OF/OI 80.928 634 473 300 440 WWW.265 236.600 514 HG X X X X OF/OI 348.800 21.928 800 597 300 440 (Continues) AJAX DPC 2803 STD X X X OI 5500 379 40.300 800 HF X X X X OF/OI 256.600 122.000 55.000 33.500.000 514 OA X X X OF/OI 26. M X X OF/OI 6000 414 12.400 4 5000 3729 277 600 HHE-VG X X OF/OI 12.000 46.100 4 10.000 53.000 1.000 580 435 800 PK X X X OI 562.565 358.500 16.000 4 22. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max DRESSER-RAND * BDC-18H3 X X OF/OI 12.378 120 89 900 1800 H X X OF/OI 6000 414 20.P.500 1.000 80.A.000 88.000 467.000 827 30.928 845 630 300 440 AJAX DPC 2804 LE X X X OI 5500 379 40.400 4935 3680 800 HD X X X X OF/OI 72.630 7927 277 450 HHE-VL X X OF/OI 12.964 400 298 900 1800 A X X OF/OI 6000 414 27.500 15.500 600 HE-S X X X X OF/OI 150.700 2840 2120 1000 51 HB X X X X OF/OI 59.500 10.065 10.065 7130 5320 1200 * This company is not represented in the 2017 Supplement with a section describing its products.500 2.556 277 450 BUSINESS HHE-FB X X OF/OI 12.000 827 27.565 358.557 144. AB X X X OF 140 3000 4 83 190 13 5 1340 1000 580 3600 GE OIL & GAS * HA X X X X OF/OI 32.000 177.530 60.030 41.200 4 240 179 500 720 GARO S. ASM.750 1.000 28.557.360 34.000 827 200.460 7800 700 HE X X X X OF/OI 119.000 827 350.000 177.225 533.000 827 105.000 827 50.000 177.000 890.562 322.000 20.000 4 45.000 222.550.CTSSNET.000 177.000 120.102 800 596 900 1800 AJAX DPC 2804 STD X X X OI 5500 379 40.325 117.140.000 827 10.778 277 450 HSE X X OF/OI 12.928 800 597 300 440 AJAX DPC 2804 ULE X X X OI 5500 379 40. OI 8250 568 65.NET CTSS .000 133.446 192 143 300 440 AJAX DPC 2801 ULE X X X OI 5500 379 30.446 300 224 260 455 CFA 34 X X X X OI 5808 400 13.306 2720 2028 600 1200 CFR X X X X OF/OI 2200 152 48.000 133.CTSSNET.928 2375 1772 600 1500 * This company is not represented in the 2017 Supplement with a section describing its products.000 133.928 600 448 300 440 AJAX DPC 2803 ULE X X X OI 5500 379 40. OI 8250 568 65.133 1800 1343 250 1200 WH64 X X X X OF.306 1800 1343 250 1200 MH64 X X X X OF.446 148 110 300 440 AJAX C-302 X X X X OI 5500 379 30.514 3400 2535 600 1500 RAM52 X X X X OI 2200 152 40. OI 8250 568 52.000 133.446 384 286 300 440 AJAX DPC 2801 STD X X X OI 5500 379 30.000 133.000 133.133 3600 2685 250 1200 (Continues) WH66 X X X X OF.000 57. OI 8250 568 52.000 231.000 177. MH62 X X X X OF.000 289.000 133.000 213.827 580 432 850 1800 CFA 32 X X X X OI 5808 400 13.000 133.000 133.000 177.306 5400 4027 250 1200 WH62 X X X X OF.133 5400 4027 250 1200 WWW. OI 8250 568 52. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max GE OIL & GAS * AJAX DPC 2803 LE X X X OI 5500 379 40.446 192 143 300 440 52 AJAX DPC 2202 STD X X X OI 5500 379 30.000 57.446 296 221 300 440 AJAX DPC 2201 STD X X X OI 5500 379 30.000 177.928 1190 887 600 1500 RAM54 X X X X OI 2200 152 40.928 600 448 300 440 AJAX DPC 2802 STD X X X OI 5500 379 30.827 290 216 850 1800 CFH X X X X OF/OI 8250 569 52.000 231.000 231.000 133.446 422 315 300 440 AJAX DPC 2802 LE X X X OI 5500 379 30.446 192 143 300 440 AJAX DPC 2801 LE X X X OI 5500 379 30.306 3600 2685 250 1200 MH66 X X X X OF.000 289.000 133.000 289.000 177. OI 8250 568 65.000 231.446 296 221 300 440 AJAX DPC 2202 LE X X X OI 5500 379 30.446 384 286 300 440 AJAX DPC 2802 ULE X X X OI 5500 379 30.446 148 110 300 440 AJAX DPC 2201 LE X X X OI 5500 379 30. 01 5 44. OI 8250 568 75.000 667. OI 8250 568 75.000 6000 56. X X X X OF.000 333. OI 15.000 1034 150.097 2250 1678 264 330 GMV10 Cooper Bessemer X X X OF.000 289.4 60.000 1034 85.35 15 0.097 2700 2014 264 330 GMV12 Cooper Bessemer X X X OF. OI 8250 568 65.000 3000 31.000 378.000 333. OI 8250 568 75.000 1034 150. OI 15.000 333.230 6000 4476 264 330 12W330 Cooper Bessemer X X X OF.097 8250 6152 327 600 KM Cooper Bessemer * This company is not represented in the 2017 Supplement with a section describing its products.35 2300 0.615 9000 6711 200 1200 WG72 X X X X OF.230 4000 2984 264 330 8W330 Cooper Bessemer X X X OF. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max GE OIL & GAS * WH72 X X X X OF.000 333.000 1034 85. OI 8250 568 65. OI 15.000 1034 150.000 378.500 350.615 7500 5593 200 1000 53 Cooper Bessemer X X X OF.000 667.000 378.000 5 900 670 250 720 143 TK X X X X OF 0.000 8 270 200 8 40 WWW.200 250. OI 15. OI 8250 568 65.01 0.CTSSNET.NET CTSS . OI 15.000 333.133 1700 1268 250 1000 WH74 X X X X OF.133 5100 3803 250 1000 WG62 X X X X OF. OI 8250 568 75. OI 15.000 1034 85.000 8 335 250 250 720 TKH X X X X OF 0.000 1034 150.35 175 0.000 333.615 5000 3728 200 1000 WG76 X X X X OF.000 8948 327 450 LM HAUG KOMPRESOREN AG * Oil-Free Piston X X X X X OF 0 700 0 20 4350 300 150 110 750 1800 Compressors HOFER 142.230 8000 5968 264 330 16W330 Cooper Bessemer X X X X OF.000 289.01 65 90.615 3000 2237 200 1200 WG64 X X X X OF. KK X X X X OI 0.35 2300 0. OI 8250 568 75.000 667.000 289.000 4000 78. OI 8250 568 75.01 65 3600 250 56.500 140.615 2500 1864 200 1000 WG74 X X X X OF.230 12.000 5 900 670 250 720 MK X X X X X OF 0.000 667.615 6000 4474 200 1200 WG66 X X X X OF.133 3400 2535 250 1000 WH76 X X X X OF.200 250. OI 15. 01 357 0.NET CTSS .0003 10 43.5 20.92 305 21 10 200 150 3000 5000 Howden XRV127/R3 X OI 283 8 305 21 10 200 150 1800 3600 Howden XRV127/R4 X OI 348 9.34 870 60 3 4690 3500 1250 4000 * This company is not represented in the 2017 Supplement with a section describing its products.CTSSNET.000 0.86 305 21 10 200 150 1800 3000 54 Howden X OI 421 11.26 350 24 12 1028 766 1500 4500 (Continues) WRV(H)204/145 WWW. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max HOWDEN * Burton Corblin X X X OF 3. Howden X OI 484 13.000 12 1766 1300 200 750 D Series Burton Corblin HPD X X OF 35 2925 1 83 6500 450 49.1 568 5100 350 112.72 350 24 12 470 350 1500 4500 WRV(H)163/145 Howden X OI 601 17.28 305 21 10 350 260 1800 3600 XRV163/193 Howden X OI 578 16.32 350 24 12 1028 766 1500 4500 WRV(H)204/110 Howden X OI 786 22.38 305 21 10 600 450 1800 3600 XRV204/110 Howden X OI 786 22.26 305 21 10 600 450 1800 3600 XRV204/145 Howden X OI 867 24.57 305 21 10 600 450 1800 3600 XRV204/165 Howden X OI 976 27.000 3 2649 1950 200 500 Hybrid Series Howden XRV127/R1 X OI 209 5.64 305 21 10 600 450 1800 3600 XRV204/193 Howden M127 X OI 348 9.93 305 21 10 350 260 1800 3600 XRV163/165 Howden X OI 504 14.86 305 21 10 200 150 1800 3600 Howden XRV127/R5 X OI 342 9.33 350 24 12 470 350 1500 4500 WRV(H)163/180 Howden X OI 718 20.500 220.86 320 22 10 223 166 1500 6000 Howden GTV 228 X OI 683 19.500 220.500 3000 49.000 4 3400 2500 200 1000 P Series Burton Corblin X X X X OF 0.400 500. CTSSNET.1 350 24 12 5814 4335 1500 3600 WRVi365/193 Howden X OI 5420 153.57 350 24 12 1028 766 1500 4500 WRV(H)204/165 Howden X OI 976 33.6 350 24 12 6700 5000 700 2000 (Continues) WRVT510/132 WWW.NET CTSS .99 350 24 12 1542 1150 1500 3600 WRVi255/193 Howden X OI 2258 63.48 350 24 12 1542 1150 1500 3600 WRVi255/145 Howden 55 X OI 1694 48 350 24 12 1542 1150 1500 3600 WRVi255/165 Howden X OI 1905 53. Howden X OI 4144 117.4 350 24 12 5814 4335 1500 3600 WRVi365/145 Howden X OI 4783 135.5 350 24 12 5814 4335 1500 3600 WRVi365/165 Howden X OI 5580 158.89 200 14 8 1542 1150 1500 3600 WRV255/220 Howden X OI 2710 76.55 350 24 12 1028 766 1500 4500 WRV(H)204/193 Howden X OI 1129 32 350 24 12 1542 1150 1500 3600 WRVi255/110 Howden X OI 1270 36 350 24 12 1542 1150 1500 3600 WRVi255/130 Howden X OI 1535 43.8 350 24 12 2741 2044 1500 3600 WRVi321/132 Howden X OI 3388 96 350 24 12 2741 2044 1500 3600 WRVi321/165 Howden X OI 3811 108 350 24 12 2741 2044 1500 3600 WRVi321/193 Howden X OI 4517 128 200 14 8 2741 2044 1500 3600 WRV321/220 * This company is not represented in the 2017 Supplement with a section describing its products. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max HOWDEN * Howden X OI 867 24. C-45 Howden Thomassen X X X OF/OI 8700 600 5 44.000 10.266 4 624 465 300 1000 WWW.5 350 24 12 6700 5000 700 2000 WRVT510/193 Howden H127/165 X OF 882 25 126 9 4 286 213 7500 15.950 15.913 33.400 250 500 * This company is not represented in the 2017 Supplement with a section describing its products.185 392.397 351 130 10 4 4000 2985 2000 3750 Howden Thomassen X X X OF/OI 8700 600 5 1090 800 300 600 C-7 Howden Thomassen X X X OF/OI 8700 600 5 3130 2300 300 600 C-12 Howden Thomassen X X X OF/OI 8700 600 5 7620 5600 300 600 C-25 Howden Thomassen X X X OF/OI 8700 600 5 14.266 5 367 274 300 1000 (Continues) Howden KD TSKB X X OF 60 1737 2 49 2391 165 88.332 292.185 392.185 392.CTSSNET.000 Howden HP204/110 X OF 1490 42 201 14 4 800 600 4750 9500 Howden H204/165 X OF 2236 63 126 9 4 800 600 4750 9500 Howden HP255/110 X OF 2300 65 201 14 4 1250 935 4000 7500 Howden H255/165 X OF 3450 98 126 9 4 1250 935 4000 7500 Howden HP408/110 X OF 5899 167 201 14 4 3050 2275 2300 4700 56 Howden H408/165 X OF 8845 250 126 9 4 3050 2275 2300 4700 Howden HP510/110 X OF 8266 234 200 15 4 4000 2985 2000 3750 Howden H510/165 X OF 12.300 250 500 C-35 Howden Thomassen X X X OF/OI 8700 600 5 20.000 190 375 C-85 Howden Thomassen X X X OF/OI 8700 600 5 6254 4600 500 1200 CHS Howden KD JSKB X X OF 113 1561 3 44 435 30 88.266 6 362 270 300 1000 Howden KD DSKB X X OF 99 1137 3 32 435 30 88.NET CTSS . RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max HOWDEN * Howden X OI 6775 192 350 24 12 6700 5000 700 2000 WRVT510/165 Howden X OI 10. 14 600 4700 5 20 400 825 * This company is not represented in the 2017 Supplement with a section describing its products.74 800 6300 5 40 400 825 AN20E X OF 13.45 23.82 3.73 600 6300 5 40 400 825 WWW.95 16.18 16. AN44 X OF 29.09 8.05 600 3700 5 11 400 825 WN10C X OF 6.09 8.98 200 3700 5 11 400 825 WN26 X OF 17.05 600 3700 5 11 400 825 AN26 X OF 17.84 5.185 392.43 600 2800 5 8 400 825 WN07 X OF 0.185 392.98 600 6300 5 40 400 825 WN20E X OF 13.87 200 2800 5 8 400 825 AN6C X OF 4. * AN3A X OF 1.98 600 6300 5 40 400 825 AN27E X OF 17.99 750 3700 5 11 400 825 AN10C X OF 6.08 26.09 18.75 1000 2800 5 8 400 825 AN4A X OF 2.266 5 456 340 300 1000 Howden KD (T)SKM X X OI 11 706 1 20 3623 250 88.45 0.81 36.81 14.81 14. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max HOWDEN * Howden KD JSKM X X OI 441 1811 13 51 652 45 88.CTSSNET.71 200 4700 5 20 400 825 AN14E X OF 9.185 392.73 600 6300 5 40 400 825 (Continues) WN27E X OF 17.74 800 6300 5 40 400 825 WN14E X OF 9.58 32.266 5 282 210 300 1000 Howden KD DSKM X X OI 162 2147 5 61 652 45 88.86 1000 2800 5 8 400 825 AN6A X OF 4.08 26.99 750 3700 5 11 400 825 WN6C X OF 4.44 35.44 60.44 35.98 200 3700 5 11 400 825 AN12D X OF 7.09 18.86 1000 2800 5 8 400 825 WN4A X OF 2.4 1000 4700 5 20 400 825 AN17D X OF 11.81 36.61 600 4700 5 20 400 825 AN23D X OF 15.43 1000 2800 5 8 400 825 AN6 X OF 4.NET CTSS .36 8.84 5.266 4 429 320 300 1000 HYCOMP INC.36 8.94 1500 2800 5 8 400 825 57 AN12 X OF 8. 65 400 11.03 1500 3700 5 11 400 825 2AN10C X OF 5.86 1000 2800 5 8 400 825 2AN6B X OF 4.68 13.18 4.87 250 11.04 22.22 500 4700 5 23 400 825 (Continues) 2WN35 X OF 22.48 500 2800 5 8 400 825 2AN3C X OF 2.72 13.700 5 66 400 700 WN98 X OF 60.44 60.06 99.13 600 6300 5 40 400 825 WN90 X OF 60.91 600 6300 5 40 400 825 WN28F X OF 19.08 87.06 99.86 750 4700 5 23 400 825 2AN15D X OF 10.22 500 4700 5 23 400 825 WWW.84 5.19 33.59 700 11.5 1500 3700 5 11 400 825 2AN5C X OF 3.21 178. 2WN10C X OF 6.39 500 11.700 5 66 400 700 WN75F X OF 50.59 700 11.08 105.700 5 66 400 700 AN28F X OF 19.43 500 2800 5 8 400 825 2AN8 X OF 5.08 123.41 7.700 5 66 400 700 58 WN55F X OF 36.700 5 66 400 700 WN44F X OF 29.NET CTSS .76 11.97 600 6300 5 40 400 825 AN44E X OF 29.700 5 66 400 700 AN154 X OF 102.9 47.07 50.77 500 3700 5 11 400 825 2AN17 X OF 11.13 600 6300 5 40 400 825 WN72 X OF 48.88 650 11.88 650 11.18 20.07 50.700 5 66 400 700 2AD4A X OF 2.77 500 3700 5 11 400 825 2AN10D X OF 6.71 600 6300 5 40 400 825 AN72 X OF 48.09 8. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max HYCOMP INC.19 33.56 11. * AN35E X OF 23.700 5 66 400 700 AN44F X OF 29.14 300 11.26 47.88 500 3700 5 11 400 825 * This company is not represented in the 2017 Supplement with a section describing its products.8 64.53 36.99 750 4700 5 23 400 825 2AN26 X OF 17.CTSSNET.15 500 4700 5 23 400 825 2AN35 X OF 22.9 47. 82 750 11.36 750 6300 5 43 400 825 59 2AN61 X OF 40. * 2AN40 X OF 26.CTSSNET.99 1000 6300 5 43 400 825 2WN17E X OF 11.700 5 72 400 700 2WN28F X OF 18.700 5 72 400 700 2AN137 X OF 90.2 750 11.11 105.44 60.700 5 72 400 700 2AN28F X OF 18.31 500 11.97 500 4700 5 23 400 825 2WN40 X OF 26.700 5 72 400 700 2AN58F X OF 38.18 750 11.36 750 6300 5 43 400 825 2WN22E X OF 14.24 750 11.86 159 200 11.71 57.700 5 72 400 700 2WN150H X OF 101.31 400 11.700 5 72 400 700 2WN22F X OF 14.89 84.71 500 4700 5 23 400 825 WWW.33 350 6300 5 43 400 825 2AN76 X OF 51.41 350 6300 5 43 400 825 2AN22F X OF 14.4 32.97 500 4700 5 23 400 825 2WN13E X OF 8.36 1000 6300 5 43 400 825 2AN17E X OF 11.11 105.41 350 6300 5 43 400 825 2WN76 X OF 51.72 30.39 67.63 23.9 18.17 53.99 1000 6300 5 43 400 825 2AN22E X OF 14.32 177.700 5 72 400 700 * This company is not represented in the 2017 Supplement with a section describing its products.700 5 72 400 700 2WN150L X OF 101.63 23.44 1000 11.04 43.72 30.2 1000 11.54 25.89 84.NET CTSS .54 25.700 5 72 400 700 2WN38F X OF 25.44 1500 11.4 32. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max HYCOMP INC. 2WN49F X OF 32.17 53.32 177.33 350 6300 5 43 400 825 2WN61 X OF 40.700 5 72 400 700 3AN44 X OF 29. 916 440.000 80.737 70.000 40.5 212 15 6-8 50 37 R-Series 45-75 X X OI 263 478 7.861 75.000 3 778 580 450 1200 Mobile Systems X X X OF/OI 10.729 110.3 6.000 4 2380 650 45 10 13.861 75.000 44.000 80.5 567 1500 100 20 13.5 74 175 13 475 355 Screw WWW.3 1.000 1000 5500 LEOBERSDORFER 136.4 212 15 2-4 500 350 60 Sierra / Nirvana Oil X X OF 200 425 6 12 150 10 2-5 100 75 Free 50-100 Sierra / Nirvana Oil X X OF 570 920 16 26 150 10 2-6 225 160 Free 125-225 Sierra / Nirvana X X OF 1200 1550 34 43.000 30.000 4 8160 6000 450 1800 * This company is not represented in the 2017 Supplement with a section describing its products.480 4 200 150 300 650 R-Series 4-11 X X OI 12 58 0.150 700 98. Process Gas X X X OF/OI 10.000 4 1743 1300 450 1800 CNG X X OF/OI 5076 350 16. (API 11P) EcoPET X X OF 580 40 15.5 212 15 6-8 100 75 R-Series 90-160 X X X OI 590 1030 16.000 6 800 1200 600 1800 Applications Electric Rotary X X X OI 15 2600 0.150 700 350.500 10.CTSSNET.500 10.000 Oil-Injected Screw X X X OI 120 20.000 1500 24.150 700 16.9 150 10 2-4 400 300 Oil Free 250-400 KOBE STEEL (KOBELCO) Forth KR Series X X X OF/OI 400 10.885 600.000 4 800 1200 450 1800 Industrial X X X OF/OI 5800 400 24.7 29.000 3.070 3 750 560 340 514 PHE 9 X X OF 900 2400 1500 4000 1500 100 18.9 3.150 700 134.000 3 8300 6200 300 1200 MASCHINENFABRIK 137 (API 618) GMBH (LMF) Process Gas X X OF/OI 10. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max INGERSOLL RAND * PS-4 X X OF 950 1800 1500 3300 650 45 18.2 212 15 6-8 225 160 SSR 200-350 X X X OI 1250 2450 35.NET CTSS .000 160.4 13.6 212 15 6-8 15 11 R-Series 15-22 X X OI 68 113 1.070 4 400 300 300 514 PHE 7 X X OF 100 800 150 1400 1200 83 10.2 212 15 6-8 30 22 RS 30-37 X X OI 186 230 5.4 69.000 250 1000 Cover Dry Screw X X X OF 140 84. 700 8 35 26 560 1200 55-LRG9-DP X X 0 300 0 8.5 2500 172 6000 26.5 350 24 25 90 67 1600 5480 COMPRESSORS HGF10000 X X OI 0 160 0 4.000 (OBERHAUSEN) 139 SKUEL X OF 2331 60.700 8 55 41 560 1200 MAN DIESEL & TURBO SE 138.7 350 24 25 125 93 750 4500 HGFS17000 X X OI 0 530 0 15 350 24 25 180 134 1100 3920 HGF17000 X X OI 0 530 0 15 350 24 25 180 134 1100 3920 HGS17XXX X X OI 0 560 0 16 350 24 25 180 134 1640 5560 61 HG17000 X X OI 0 780 0 22 350 24 25 180 134 540 3920 HG17XXX X X OI 0 780 0 22 350 24 25 180 134 540 4300 HG20000 X X OI 0 1040 0 30 350 24 25 300 224 500 3300 HGF20000 X X OI 0 1040 0 30 350 24 25 300 224 500 5000 HG20XXX X X OI 0 1040 0 30 350 24 25 300 224 500 6600 HHG24XXX X X OI 0 1530 0 43 300 21 22 350 261 500 5870 LG30XXX X X OI 0 2840 0 80 250 17 15 600 447 350 3470 LGL30XXX X X OI 0 3750 0 106 150 10 12 900 671 350 2400 LGT24XXX X X OI 0 1550 0 44 150 10 8 400 298 500 3400 LGT30XXX X X OI 0 2900 0 82 150 10 8 600 448 950 3300 HGT17XXX X X OI 0 750 0 21 500 34 15 400 298 950 3350 * This company is not represented in the 2017 Supplement with a section describing its products.NET CTSS . CP X OF 120 12.000 66 1700 230 16 10 13.7 350 24 25 125 93 2250 5540 HGF12000 X X OI 0 270 0 7.5 2500 172 6000 26.000 3000 25.7 350 24 25 125 93 1500 3690 HG12XXX X X OI 0 270 0 7.410 10.5 350 24 25 90 67 1100 3650 HG12000 X X OI 0 270 0 7. HGT24XXX X X OI 0 1550 0 44 500 34 15 600 448 500 3680 35-LRG9-DP X X 0 300 0 8.410 10.069 9000 1500 3600 WWW. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max LEROI GAS * HG10000 X X OI 0 160 0 4.CTSSNET.065 8 285 360 40 25 12.000 3 340 725 50 10 13.000 1500 8900 CPO X OI 283 10. CTSSNET.500 1000 75 55 250 400 MRE 1300 X X OF 14.500 1000 220 160 250 400 (Continues) MLZ 300 X X OF 14. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max MEHRER COMPRESSION * TRE 200 X X OF 214 15 7 5 380 750 GMBH TRZ 200 X X OF 355 25 7 5 380 750 TRE 300 X X OF 426 30 13 10 380 750 TRZ 300 X X OF 426 30 13 10 380 750 TZL 40 X X OF 298 21 15 11 480 700 TEL 80 X X OF 355 25 30 22 400 735 TEW 90 X X OF 327 23 74 55 400 690 TEW 110 X X OF 227 16 74 55 400 690 TZW 50 X X OF 369 26 20 15 400 710 62 TZW 60 X X OF 313 22 74 55 380 725 TZW 70 X X OF 313 22 74 55 380 725 TRZ 850 X X OF 355 25 168 125 380 940 TRZ 1000 X X OF 355 25 168 125 380 940 TRZ 700 X X OF 625 44 168 125 380 850 TRE 700 X X OF 355 25 168 125 380 850 TRB 700 X X OF 640 45 168 125 380 850 TRD 700 X X OF 1237 87 168 125 380 850 TVZ 900 X X OF 910 64 268 200 380 1100 TVE 900 X X OF 227 16 268 200 380 1100 * This company is not represented in the 2017 Supplement with a section describing its products.500 1000 40 30 250 400 MRE 500 X X OF 14.NET CTSS . TVB 900 X X OF 910 64 268 200 380 1100 TVD 900 X X OF 896 63 268 200 380 1100 MRE 300 X X OF 14.500 1000 15 11 250 400 MRE 400 X X OF 14.500 1000 15 11 250 400 WWW. 6 27.138 18.6 3050 210 20.2 39.000 500 SHIPBUILDING MB Series X X X OF/OI 14. 11L X X OI 232 986 6.3 80 5 5 15 11 865 2200 5CC X X OI 24 110 0.000 712.000 4 100/150 74/111 900 2200 PEDRO GIL S.125 21.500 1000 75 55 250 400 MHx 1300 X X OF 14.6 3050 210 16.000 4 175/300 130/223 800 1800 63 CiP PVT2 X X X X OF/OI 3 270 0.9 80 5 5 15 11 865 2200 4CC X X OI 10 80 0.25 2.7 3.200 600 7 134 1000 700 NATURAL GAS SERVICES * CiP PHT2 X X X X OI 5 585 0.14 16.NET CTSS .1 80 5 5 103 77 450 1300 11S X X OI 204 862 5.l * Rotary Piston Blower X X OF 1 170 0.500 1000 40 30 250 400 MHx 500 X X OF 14.65 2000 138 7500 34.000 4 250/400 186/298 800 1800 GROUP/CIP CiP PXT2 X X X X OI 5 585 0.1 80 5 5 345 257 310 760 17L X X OI 393 1594 11.500 1000 15 11 250 400 MHx 400 X X OF 14. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max MEHRER COMPRESSION * MLZ 400 X X OF 14.200 600 7 24.14 16.1 45.2 80 5 5 15 11 865 2200 7D X X OI 53 198 1.4 80 5 5 162 121 400 1000 * This company is not represented in the 2017 Supplement with a section describing its products.500 1000 220 160 250 400 MITSUI ENGINEERING & * C Series X X X OF/OI 14.500 1000 40 30 250 400 GMBH MHx 300 X X OF 14.125 400 21.7 80 5 5 415 309 275 640 (Continues) 19L X X OI 560 2165 15.14 0.8 24.9 80 5 5 168 125 400 1000 12S X X OI 252 1024 7.CTSSNET.7 80 5 5 47 35 600 1465 8DE X X OI 107 446 3 12.9 32.000 890.4 80 5 5 415 309 275 640 WWW.2 80 5 5 400 298 310 760 19S X X OI 497 1895 14.8 80 5 5 222 166 380 920 17S X X OI 325 1378 9.1 53.5 150 29 2 422 315 4800 RO-FLO COMPRESSORS * 2CC X X OI 5 30 0.08 7.5 5.1 29 80 5 5 213 159 380 920 12L X X OI 280 1159 7.6 19.6 80 5 5 60 45 600 1465 10G X X OI 126 674 3.9 61.6 80 5 5 33 25 690 1465 8D X X OI 87 343 2.5 9. 6 54.7 64.5 4 150 10 7 340 254 450 1300 211M X X OI 48 245 1.6 8.1 24 150 10 5 450 336 400 1000 12S-212M X X OI 278 886.5 30 0.66 7.76 8.4 2.9 150 10 5 600 447 275 640 19L-219M X X OI 622 1930 17.4 150 10 5 50 37 865 1465 7D-207 X X OI 60 165.8 2.1 150 10 5 450 336 380 920 * This company is not represented in the 2017 Supplement with a section describing its products.7 150 10 5 96 72 690 1465 8D-208B X X OI 92 289.7 1.01 0.2 150 10 5 96 72 600 1465 8DE-208B X X OI 115 377 3.8 63.8 13.88 11. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max RO-FLO COMPRESSORS * 19LE X X OI 880 2286 20.7 80 5 5 415 309 275 640 206 X X OI 0.9 38.5 150 10 5 450 336 400 1000 11L-211M X X OI 252 848.9 150 10 7 96 72 600 1465 207 X X OI 7 50 0.7 150 10 5 600 447 275 640 19LE-219M X X OI 700 2254 19.9 150 10 7 474 353 310 760 64 219M X X OI 97 474 2.6 48.4 7 150 10 7 450 336 400 1000 212M X X OI 58 276 1.7 150 10 5 96 72 600 1465 10G-210M X X OI 138 556.4 21.4 150 10 7 478 356 275 640 4CC-206 X X OI 15 34 0.4 1 150 10 5 50 37 865 1465 5CC-206 X X OI 24 50 0.NET CTSS .9 150 10 5 500 373 310 760 19S-219M X X OI 550 1725 15.88 10. 12L-212M X X OI 306 975.8 150 10 5 340 254 450 1300 11S-211M X X OI 226 758.7 27.9 25.CTSSNET.6 7.2 150 10 7 96 72 600 1465 210M X X OI 19 140 0.66 7.2 6.4 1.54 4 15.6 150 10 5 450 336 380 920 17S-217M X X OI 368 1200.3 10.4 34 150 10 5 500 336 310 760 17L-217M X X OI 420 1371.8 150 10 5 600 447 275 640 WWW.2 1.7 4.5 10.8 150 10 7 450 336 380 920 217M X X OI 88 383 2.4 150 10 7 96 72 600 1465 208B X X OI 15 79 0. 000 4 110 550 1500 * This company is not represented in the 2017 Supplement with a section describing its products. Hydraulic series X X X OI 15 300 4 75 SAUER COMPRESSORS * MISTRAL WP 15L X OI 580 40 2 980 1780 MISTRAL WP 22L X OI 580 40 2 980 1780 MISTRAL WP 33L X OI 510 35 2 980 1780 MISTRAL WP 45L X OI 580 40 2 980 1780 MISTRAL WP 65L X OI 580 40 2 980 1780 (Continues) MISTRAL WP 146L X OI 150 10 2 980 1780 WWW.000 4 500 550 1500 ST X X X OI 8 250 35.CTSSNET. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max ROTORCOMP * EVO2-Gas X X OI 2 15 11 2000 9300 VERDICHTER GMBH EVO3-Gas/Geared X X OI 3 15 19 2000 9000 EVO6-Gas/Geared X X OI 6 15 37 1500 7000 EVO9-Gas/Geared X X OI 9 15 55 1500 6600 EVO15-Gas/Geared X X OI 14 15 90 1000 5500 EVO28-Gas/Geared X X OI 25 15 160 1000 4000 EVO40-Gas-Geared X X OI 40 17 260 1000 5000 EVO76-Gas/Geared X X OI 76 17 540 1000 3000 EVO105-Gas- 65 X X OI 105 14 670 1000 3000 Geared EVO2-NK-Gas X X OI 2 15 11 2000 9300 EVO3-NK-Gas/ X X OI 3 15 19 2000 9000 Geared EVO6-NK-Gas/ X X OI 6 15 37 1500 7000 Geared EVO9-NK-Gas/ X X OI 8 15 55 1500 6300 Geared NK200-Gas/Geared X X OI 10 15 75 1500 4000 SAFE SPA * S7-S9 X X OI 4 300 22.000 4 75 550 1500 SW X X X OF/OI 18 300 50.NET CTSS . CTSSNET. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max SAUER COMPRESSORS * MISTRAL WP 226L X OI 150 10 2 980 1780 MISTRAL WP 33L X OI 580 40 1 980 1780 B4-8 MISTRAL WP 65L X OI 580 40 1 980 1780 B4-8 PASSAT WP 81L X OI 640 44 3 980 1780 PASSAT WP 101L X OI 640 44 3 980 1780 PASSAT WP 121L X OI 640 44 3 980 1780 PASSAT WP 151L X OI 640 44 3 980 1780 PASSAT WP 271L X OI 640 44 3 980 1780 66 PASSAT WP 311L X OI 640 44 3 980 1780 PASSAT WP 66L X OI 1160 80 3 980 1780 PASSAT WP 126L X OI 1160 80 3 980 1780 PASSAT WP 206L X OI 1160 80 3 980 1780 PASSAT WP 156L X OI 580 40 3 980 1780 PASSAT WP 276L X OI 580 40 3 980 1780 PASSAT WP 316L X OI 580 40 3 980 1780 HURRICANE WP X OI 5800 400 4 980 1780 4331 HURRICANE WP X OI 5800 400 4 980 1780 4341 * This company is not represented in the 2017 Supplement with a section describing its products. HURRICANE WP X OI 5080 350 4 980 1780 4351 TORNADO WP 3215 X OI 5080 350 3 980 1780 TORNADO WP 3325 X OI 5800 400 3 980 1780 B3-5 TORNADO WP 4325 X OI 5800 400 4 980 1780 HARMATTAN WP X OF 150 10 2 980 1780 (Continues) 68LON WWW.NET CTSS . CTSSNET. 5000 WP 5000 X OI 5080 350 4 980 1780 6000 WP 6305 X OI 730 50 3 980 1780 6000 WP 6310 X OI 1450 100 3 980 1780 6000 WP 6442 X OI 5800 400 4 980 1780 6000 WP 6550 X OI 7250 500 5 980 1780 WWW. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max SAUER COMPRESSORS * HARMATTAN WP X OF 150 10 2 980 1780 101LON HARMATTAN WP X OF 150 10 2 980 1780 154LON HARMATTAN WP X OF 150 10 2 980 1780 222LON HARMATTAN WP X OF 220 15 2 980 1780 65LOM HARMATTAN WP X OF 220 15 2 980 1780 97LOM HARMATTAN WP X OF 220 15 2 980 1780 67 143LOM HARMATTAN WP X OF 220 15 2 980 1780 215LOM TYPHOON WP 100 X OI 440 30 2 980 1780 TYPHOON WP 200 X OI 440 30 2 980 1780 TYPHOON WP 240 X OI 440 30 2 980 1780 TYPHOON WP 400 X OI 440 30 2 980 1780 TYPHOON WP 3100 X OI 1450 100 3 980 1780 5000 WP 5500 X OI 5080 350 4 980 1780 * This company is not represented in the 2017 Supplement with a section describing its products.NET CTSS . 000 4 620 450 300 750 W Series X X X OI/OF 5075 350 10.000 85.000 4 475 350 300 750 P Series X X X OI/OF 5075 350 30.000 240.900 8700 300 500 IMPIANTI S.000 350.000 625.000 4 3275 2400 300 750 HP Series X X X X OI/OF 8700 600 37.34 300 21 12 50 36 900 2100 350 LP X X X OI 91 425 2.58 12 350 24 6 180 132 900 2100 SIAD MACCHINE 117 HT Series X X X X OI/OF 8700 600 140.000 4 280 200 300 1200 T Series X X X OI/OF 5075 350 3500 15.000 4 1500 1100 300 750 M Series X X X OI/OF 5075 350 20.58 12 350 24 6 150 110 900 2100 632 HP X X X OI 91 425 2.000 4 8700 6400 520 1200 HSD Series X X X X OF/OI 8700 600 55.000 4 5600 4100 600 1500 HD Series X X X X OI/OF 8700 600 55.000 4 105 75 300 1200 I Series X X X OI/OF 1450 100 1350 6000 4 14 10 300 1200 SULLAIR * PDX10 X X OI 75 251 200 14 PDX12 X X OI 136 453 200 14 PDX16 X X OI 217 724 200 14 PDX20L X X OI 348 1160 200 14 * This company is not represented in the 2017 Supplement with a section describing its products.000 95.000 4 11.A. PDR20X X X OI 450 1501 200 14 PDR25L X X OI 521 1738 200 14 PDR25X X X OI 710 2367 200 14 PDX32S X X OI 609 2030 200 14 PDX32L X X OI 843 2810 200 14 PDX32X X X OI 1168 3893 200 14 (Continues) PDR32LDD X X OI 863 2878 100 7 WWW.000 240.000 133.58 12 125 9 6 125 92 900 2100 350 HP X X X OI 91 425 2.500 45.4 3. HSF Series X X X X OF/OI 8700 600 78.CTSSNET.P.000 4 1950 1400 300 750 68 HM Series X X X X OI/OF 5075 350 22.500 165.NET CTSS . RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max SERTCO * 98 HP X X X OI 51 118 1. 7 20 30 2500 6500 NG10 X X OI 1.5 20 70 2000 9000 NG14 X X OI 3. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max SULLAIR * PDR32LGD X X OI 863 2810 150 10 PDR32XDD X X OI 1168 3893 100 7 PDR32XGD X X OI 1168 3893 150 10 PDH1217 X X OI 136 453 400 28 PDH1211-G2 X X OI 86 288 500 35 PC16L X X OI 220 733 400 28 PC20S X X OI 235 784 400 28 PC20L X X OI 348 1160 400 28 69 PC25S X X OI 368 1226 400 28 PC25M X X OI 407 1357 400 28 PC25L X X OI 541 1803 400 28 PC40L X X OI 1392 4640 350 24 DC16 X X OI 330 500 200 14 DC20 X X OI 500 900 200 14 DC20XL X X OI 900 1050 200 14 DC25 X X OI 1200 200 200 14 TM.5 2. NG13 X X OI 2.5 2.1 13 20 110 2000 6500 NG20 X X OI 8 25 20 180 1500 5000 NG22 X X OI 8 25 20 200 1500 4000 NG30 X X OI 15 50 20 500 1000 3500 NG twin X X OI 50 100 20 950 1000 3500 WWW.7 20 25 3000 10. BARE SHAFT * NG8 X X OI 0.3 8.P.5 7.NET CTSS .2 20 30 2000 9000 * This company is not represented in the 2017 Supplement with a section describing its products.500 COMPRESSOR NG9 X X OI 1.CTSSNET. 25 15 16 15 110 6000 GMBH WV X X X OI 1 130 80 25 3000 3600 WF X X X OI 1 15 26 25 250 9000 WCV X X X OI 1 130 80 25 3000 3600 WCF X X X OI 1 15 26 25 250 9000 WST X X X OF 10 150 60 4 3000 24.NET CTSS .9 535 37 20 2000 1491 3800 VPT KOMPRESSOREN * RS Compact X X X OI 0.7 950 65 20 600 448 4800 VSSG 451 X OI 483 13.3 515 35 20 600 448 4800 VSSG 291 X OI 291 8.3 725 49 20 865 645 3800 VSG 1551 X OI 1547 43. VSG 3001 X OI 2962 83.2 535 37 20 2000 1491 3800 VSG 2601 X OI 2607 73.7 515 35 20 600 448 4800 VSG 701 X OI 680 19.6 515 35 20 400 298 4800 VSG 501 X OI 495 14 515 35 20 600 448 4800 VSG 601 X OI 590 16.8 535 37 20 2000 1491 3800 * This company is not represented in the 2017 Supplement with a section describing its products.7 950 65 20 600 448 4800 70 VSSG 601 X OI 568 16.000 WWW.1 515 35 20 400 298 4800 VSG 401 X OI 408 11.7 725 49 20 865 645 3800 VSG 1201 X OI 1210 34.2 950 65 20 600 448 4800 VSSG 341 X OI 341 9.CTSSNET.3 485 33 20 865 645 4000 VSG 1051 X OI 1085 30.1 950 65 20 600 448 4800 VSG 751 X OI 789 22.8 535 37 20 2000 1491 3800 VSG 2801 X OI 2772 78.3 485 33 20 865 645 4000 VSG 901 X OI 892 25.4 535 37 20 1400 1044 3800 VSG 2101 X OI 2048 58 535 37 20 1400 1044 3800 VSG 2401 X OI 2374 67.8 515 35 20 400 298 4800 LLC VSG 361 X OI 356 10.8 535 37 20 1400 1044 3800 VSG 1851 X OI 1815 51. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max VILTER MANUFACTURING * VSG 301 X OI 310 8. 986 lb mole °R displacement Cp = specific heat at constant pressure.7 psia and 60°F High speed reciprocating units — 0. 13th edition. The complete Engineering Data Book can be ordered from GPSA. MMSCFD s = suction t = total or overall 1 = inlet conditions 2 = outlet conditions 2017 EDITION 71 WWW. °R F = an allowance for interstage pressure drop. in sm = surge margin d = piston rod diameter. P2/P1 Cv = specific heat at constant volume.73 lb mole °R Ap = cross sectional area of piston. percent conditions W = work. psia contract PR = reduced pressure. 6526 East 60th Street. °R p = polytropic process Q = inlet capacity (ICFM) S = standard conditions. is = isentropic process psia L = standard conditions used for calculation or pPc = pseudo critical pressure. ft lb/lb V = specific volume. ft3/lb h = enthalpy.TECH BRIEF The following section covering Compressors and Expanders has been reproduced. usually at suction VE = volumetric efficiency. Oklahoma 74145.7 psia. ft3/min g = gas PL = pressure base used in the contract or regulation. Tulsa. 60°F Qg = standard gas flow rate. in Low speed reciprocating units — 0. lb/ft3 N = speed. www. ft lb k = Cp/Cv w = weight flow. published by the Gas Processors Suppliers Association.org. P/Pc m = mechanical pTc = pseudo critical temperature. t = temperature. usually 14. actual compression horsepower. psia avg = average Pc = critical pressure.gpaglobal. °R EP = extracted horsepower of expander Tc = critical temperature. °F excluding mechanical losses.85 T = absolute temperature.CTSSNET. Btu/lb v = velocity ft/s ICFM = inlet cubic feet per minute. SECTION 13 Compressors and Expanders Compressors And Expanders FIG. in SCFM = cubic feet per minute measured at E = overall efficiency 14. psia d = discharge PD = piston displacement. moles/min Subscripts n = polytropic exponent or number of moles P = pressure. sq in lb mole °R lb mole °R BHP = brake or shaft horsepower Btu C = cylinder clearance as a percent of piston = 1. BTU/(lb °F) s = entropy. BTU/(lb °F) r = compression ratio. expressed as a decimal MN = machine mach number = density. from the Engineering Data book. lb/min MCp = molar specific heat at constant pressure. lb/lb mole = efficiency.NET CTSS . Z = compressibility factor BTU/(lb mole °F) Zavg = average compressibility factor = (Zs + Zd)/2 MW = molecular weight. rpm Nm = molar flow. T/Tc GHP = gas horsepower. BHP U = impeller tip speed H = head.82 stroke = length of piston movement. BTU/(lb °R) D = cylinder inside diameter. by permission. X = temperature rise factor BTU/(lb mole °F) y = mole fraction MCv = molar specific heat at constant volume. Eq 13-4 TR = reduced temperature.sq in lb/ft3 ft lb = 1545 or Ar = cross sectional area of piston rod. 13-1 Nomenclature ACFM = psia ft3 conditions) R = universal gas constant = 10. steps. con- verting the velocity head into static pressure. 13-2). which of a Pitot tube follows a path such that. from the compressor inlet conditions to the compressor dis- dition to the stagnation condition. Compressors Depending on application. and is stat. dynamic. manner that no effect is produced by the velocity of the gas stream.7 psia (US and gauge pressure. rotor) accelerates the gas as it passes through the element. Lower installed first cost where pressure and volume or screws. It equals the algebraic sum of barometric pressure ‘standard’ conditions. scribed as an infinite number of isentropic compression ed as degrees Rankine. stream and is the pressure used as a property in defining the Isentropic work (head): the work required to compress a unit thermodynamic state of the fluid. the compression process is de- It is equal to the degrees Fahrenheit plus 459. ible diaphragm to displace the gas. were brought to rest and its kinetic energy converted to an enthalpy rise by an isentropic compression process from the flow condition to the stagnation condition. TECH BRIEF DEFINITIONS OF WORDS AND Capacity: (Actual Flow) of a compressor is the volume rate of flow of gas compressed and delivered referred to conditions PHRASES USED IN COMPRESSORS of pressure. measured at the stagnation point when a moving gas stream Isentropic power: defined as the power required to compress is brought to rest and its kinetic energy is converted to an isentropically and deliver the capacity of the compressor enthalpy rise by an isentropic compression from the flow con. It is the pres.NET CTSS . It is the pressure usually charge pressure. Isentropic compression: refers to the reversible adiabatic ing instrument moving at the same velocity as the moving compression process. 13-3 covers the normal range of operation for compres- The diaphragm compressor uses a hydraulically pulsed flex- sors of the commercially available types. for example 60°F and 14. or thermal type (Fig. mass of gas in an isentropic compression process from the Stagnation (total) pressure: the pressure which would be inlet pressure and temperature to the discharge pressure. constant. Ejectors are “thermal” compressors that use a high velocity The reciprocating compressor consists of one or more cylin- gas or steam jet to entrain the inflowing gas. Static pressure: the pressure in the gas measured in such a Mass flow: the rate of flow in mass units. reversible process that has the same suc- a measuring instrument moving at the same velocity as the tion pressure. It is the temperature used as a property in and discharge temperature as the actual process. measured by an impact tube. conditions are favorable. suction temperature fluid stream. and mixed flow machines.325 kPa (GPA-SI Standard). In a stationary body of gas. Isentropic efficiency: the ratio of the isentropic work to the work required for the compression process. discharge pressure. velocity of the mixture to pressure in a diffuser. cating machine are: and liquid ring type. the ratio of the reversible work input to the enthalpy rise is Absolute temperature: the temperature above absolute zero. the static and stagnation pressures are numerically equal. defining the thermodynamic state of the gas. Fig. The dynamic types include radial-flow (centrifugal). vane-type. each having a casing with one or more ro- tating elements that either mesh with each other such as lobes 1. between any two points on the path. then convert the ders each with a piston or plunger that moves back and forth. Polytropic compression: a reversible compression process be- sure generally measured by the differential pressure reading tween the compressor inlet and discharge conditions. The re- Static temperature: the temperature that would be shown by sult is an ideal. displacing a positive volume with each stroke.CTSSNET. flow. partially in the Positive displacement types fall in two basic categories: rotating element and partially in stationary diffusers or blades. In other words. reciprocating and rotary. Polytropic work (head): the reversible work required to Stagnation (total) temperature: that temperature which compress a unit mass of the gas in a polytropic compression would be measured at the stagnation point if a gas stream process. axial. Lower maintenance expense. The advantages of a centrifugal compressor over a recipro- Rotary compressors cover lobe-type.66. Absolute pressure: the pressure measured from an absolute Standard or normal flow: the rate of flow under certain vacuum. Standard) or 15°C and 101. 2. screw-type. compressors are manufactured compressors in which the rotating element (impeller or bladed as positive-displacement. Velocity pressure (dynamic pressure): the stagnation pres- sure minus the static pressure in a gas stream. each followed by an isobaric heat addition. They are rotary continuous-flow 13-2 2017 EDITION 72 WWW. or that displace a fixed volume with each rotation. It is the pressure that would be shown by a measur. temperature and gas composition prevailing at AND EXPANDERS the compressor inlet. intercoolers may be provided be- tween stages. Chemical. They are normally driven or multi-stage. for Petroleum. 1. Reciprocating compressors should be supplied with clean gas as they cannot satisfactorily handle liquids and solid particles 2. Capability of handling smaller volumes. In gas processing it would be ISO Standard 13631: 2002. Such cooling reduces the actual volume of gas going to 6.000 psi and higher at Low to moderate speed compressors. typically 300–700 rpm.NET CTSS .000 hp to be used. Greater continuity of service and dependability. although a non-lu. typically 600–1800 duty) are furnished with a compression ratio as high as 8. age to the compressor cylinder or frame components. rpm packaged separable compressors are used for field gas Gas cylinders are generally lubricated. discharge for special process compressors.” Reciprocating compressor ratings vary from fractional to more than 40. gas plant and mainline bricated design is available when warranted. mid-stream compression. These are heat exchangers which remove the 4. FIG. “Petroleum and Natural Gas In- unusual for units larger than 10. Less operating attention. The compression ratio per stage (and valve accordance with API Standard 618 “Reciprocating Compressors life) is generally limited by the discharge temperature and usu. example: nitro. Less sensitive to changes in gas composition and density. Reciprocating compressors are typically designed to one of the following industry standard specifications: RECIPROCATING COMPRESSORS API Standard 618 “Reciprocating Compressors for Petro- leum. Capability of delivering higher pressures. although small-sized units (intermittent Moderate to high speed compressors. and keeps the temperature within safe operat- trifugal machine are: ing limits. have historically been used in refineries. These compressors are typically applied in all compression ratio. Liquids 3. Adaptability to high-speed low-maintenance-cost drivers. compression. or electric motors. 13-2 Types of Compressors 13-3 2017 EDITION 73 WWW. by electric motors. oxygen. Liquids and solid particles tend to destroy cylinder lubrication and cause excessive wear. are non-compressible and their presence could cause major dam- 4. reduces the horsepower required The advantages of a reciprocating compressor over a cen. Greater flexibility in capacity and pressure range. TECH BRIEF 3. chemical plants and Reciprocating compressors are furnished either single-stage also can be used in gas plant service. Pressures dustries — Packaged Reciprocating Compressors.000 hp per unit. to approximately the temperature existing at the compressor intake.” ally does not exceed 4. Chemical and Gas Industry Services. 5. and instrument air. for compression. Greater volume capacity per unit of plot area. that may be entrained in the gas. These units are normally driven by gas engines gen. and Gas Industry Services. heat of compression from the gas and reduce its temperature 5. the high-pressure cylinders. Higher compressor efficiency and lower power cost. compression.CTSSNET.” range from low vacuum at suction to 30. The number of stages is determined by the over. On multistage machines. These compressors are typically applied in accordance with ISO Standard 13631. pression horsepower requirements. estimate the capacity of an existing compressor under practice.NET CTSS . This treatment reflects industry 2. Integral compressors were designed to API 11 which is no longer supported by API. Otherwise the basic thermody- The following text outlines procedures for making these cal. namic equations are the same for all compression. determine the approximate horsepower required to com- press a certain volume of gas from some intake condi. the work of There are two ways in which the thermodynamic calcula- compression would always be evaluated by the enthalpy change tions for compression can be carried out — by assuming: FIG. For specific information on a sented are based on charts. This still would be the best way to evaluate the The engineer in the field is frequently required to: compression horsepower. the efficiency of the machine. These compressors are ing the enthalpy change were developed. This is done using equations of state on a computer. The only difference in the horsepower evaluation is specified suction and discharge conditions. and machines as being different so far as estimation of horsepower requirements is concerned. Section 13 continues to treat reciprocating and centrifugal tions to a given discharge pressure. the enthalpy change is the best section. they may equally well given compressor. 13-4). culations from the standpoint of quick estimates and also pres- The reciprocating compressor horsepower calculations pre- ents more detailed calculations. 13-3 Compressor Coverage Chart 13-4 2017 EDITION 74 WWW. be calculated using the equations in the centrifugal compressor For a compression process. If a P-H diagram includes the mechanical losses in Equations 13-37 and 13-38.CTSSNET. is available (as for propane refrigeration systems). pression service at field gas plants. particularly Equations 13-25 through 13-43. The other methods are used only if access to a good equation of state is not available. 1. This also way of evaluating the work of compression. However. TECH BRIEF A low speed “integral” compressor refers to a compressor of the gas in going from suction to discharge conditions. the capability to generate that part of the P-H diagram required for Performance Calculations compression purposes. They were used as a no longer manufactured but there are a number of them still crutch and not because they were the best way to evaluate com- in operation in pipeline boosting service as well as inlet com. Today the engineer does have available. (See Fig. Years driven by a gas engine where the power cylinders of the engine ago the capability of easily generating P-H diagrams for natural that turn the crankshaft are in the same housing as the gas gases did not exist. The result was that many ways of estimat- compression cylinders. consult the manufacturer of that unit. in many cases. 8 to 1. for high-speed compressors (1000 rpm range. The path requiring the least amount of input work is n = 1. W= 1 V dp = p1 V dp Eq 13-1 If only the molecular weight of the gas is known and not The amount of work required is dependent upon the poly.0 for single-stage compression k= = = Eq 13-3 1. However. A sample calculation is shown in Fig. an approximate value for k can be determined tropic curve involved and increases with increasing values of from the curves in Fig. 1800 rpm) can be as much as 20% higher.5. Some compressor designs do not merit a since it only implies no heat transfer.986 1. which is equivalent to isothermal compression. TECH BRIEF 1. the horsepower requirement has been widely referred to in industry as “adiabatic”.CTSSNET.08 for two-stage compression Cv MCv MCp – 1. For isentropic compression.7 psia. 13-6 gives Equation 13-4 will also provide a rough estimate of horse- values of molecular weight and ideal-gas state heat capacity power for lower compression ratios and/or gases with a higher (i. although this is a The term adiabatic does not adequately describe this process. k is normally determined at the average of suction and dis- and the entropy remains constant. very arbitrary value. volume for each value The calculation of pPc and pTc in Fig. n. 13-8.NET CTSS . pvk = constant charge temperatures. CAUTION: Compressor manufacturers generally rate their Most compressor calculations are therefore based on an effi. Fig. 13-5 shows a plot of pressure vs.4 psia and in- By rearrangement and substitution we obtain: take temperature Cp MCp MCp F = 1. but it will tend to be on the high side. The work. It was developed for large slow-speed (300 to 450 rpm) compressors handling gases with It is usually impractical to build sufficient heat-transfer a specific gravity of 0. Brake ratio horsepower = (22) stage (# of stages) (MMcfd) (F) Equation 13-3 which applies to all ideal gases can be used to calculate k. of molar heat capacity must be determined at average cylinder pvn = constant temperature. as will be done subsequently in this chapter. The compressibility Z at T and P can 2 p2 then be determined using the charts in Section 23. 13-4 Integral Engine Compressor FIG. the more common gas industry value of 14. The ideal process also fol. 13-7. and some up to all compression processes of practical importance are adiabatic. Fig. machines based on a standard condition of 14. 13-7 permits calcula- of the above exponents.0 FIG. Most machines tend to op- erate along a polytropic path which approaches the isentropic. specific gravity. 13-5) is perature TR = T/pTc mix. 13-5 Compression Curves 13-5 2017 EDITION 75 WWW.10 for three-stage compression To calculate k for a gas we need only know the constant pressure molar heat capacity (MCp) for the gas.4 psia rather than ciency applied to account for true behavior. the mole weighted average value in gas characteristics during compression are considered. a process dur.986 Btu/(lbmol °F ) Eq 13-2 MMcfd = Compressor capacity referred to 14. 2. higher horsepower allowance and the manufacturers should be lows a path of constant entropy and should be called “isentropic. isentropic reversible path — a process during which increases as it passes from suction to discharge in the compres- there is no heat added to or removed from the system sor. the bulk of the heat of compression. its composition. Eq 13-4 Where: MCp – MCv = R = 1.e. W. the exponent used is k = ratio of specific heat at Equation 13-4 is useful for obtaining a quick and reasonable constant pressure to that at constant volume. Estimating Compressor Horsepower ing which there is no change in temperature. Since the temperature of the gas low for this the tendency is to use a multiplication factor of 20 instead of 22 for gases with a specific gravity in the 0.65 and having stage compression ratios equipment into the design of most compressors to carry away above 2. polytropic reversible path — a process in which changes For a multi-component gas. estimate for compressor horsepower.” consulted for specific applications. at 1 atm) for various gases. 13-5 Due to higher valve losses. performed in proceeding tion of the reduced pressure PR = P/pPc mix and reduced tem- from p1 to p2 along any polytropic curve (Fig. A compression process following the outer curve in Fig. The heat capacity varies con. To al- siderably with temperature. 043 8.98 Hydrogen sulfide H2S 34.95 25.66 0.78 6.15 11.50 21.361 616 11.99 7.11 n-Butane C4H10 58.76 9.95 6.070 11. pTc Individual Individual Mol Component Component Component Component Compo. Eng.17 7.73 27.36 n-Heptane C7H16 100. Chem.46 26.95 6.94 6.NET CTSS .78 0.54 18. p fraction critical pres.77 27.02 10.87 36.32 12.7 MCv = MCp – 1.1 734 2.081 13.94 45.29 9.38 22.18 22.18 8.9988 6.61 41.01 8. 1948.3 i-butane 0.64 27. Wiley.12 7.00 Hydrogen H2 2. MW updated to agree with Fig.23 Oxygen O2 31.01 7.CTSSNET.1 ethane 0.578 pPc = 667.55 Carbon monoxide CO 28.86 33.0055 58.177 30.85 18.61 28.95 13.51 23.04 14.28 9.01 25.00 9.56 9.59 29.80 22.54 21.07 1.9625 6.78 14.45 24.52 8. West. Petr.63 15.98 7.96 6. R.038 9.52 8.65 8.9216 16.84 20.98 8.467 13.41 Ethane C2H6 30.37 25.33 10.054 9. 23-2 Chemical Temperature Gas Mol wt formula 0°F 50°F 60°F 100°F 150°F 200°F 250°F 300°F Methane CH4 16.23 30.13 18.78 20.592 k = MCp/MCv = 9.10 0.95 6.108 17.95 9.56 1-Butene (Butlyene) C4H8 56.00 7.66 33.68 10.53 24.95 6.150 25.9 n-butane 0.77 0. Example gas mixture ture mol weight Molar heat capacity pPc.23 20.227 25.00 8.101 528 2.09 12.96 6.97 6.41 18.07 iso-Butane C4H10 58.0134 6.59 19.2 i-pentane 0.80 17.114 16.52 0. Determination of MCp.88 17.00 8.55 29.17 8.108 16.0000 MW = 17.4 Total 1.74 24.26 *For values of MCp other than @ 150°F.01 7.38 8.0185 44.94 6.00 46.735 MCp = 9. 287.150 24.96 6.320 25.73 27.01 44. Processing.010 8.782 8.0153 7.40 22. 44.89 22.22 Ethene (Ethylene) C2H4 28.64 10.71 11.39 31.95 8.96 6.15 0.34 28.00 38.12 8.65 16.16 cis-2-Butene C4H8 56. critical tem. refer to Fig.15 22.94 49.4 666 12.72 24.13 Benzene C6H6 78.76 13.90 15.90 iso-Pentane C5H12 72.578/7.108 18.6 550 26.0017 72.52 8.61 29.34 Propene (Propylene) C3H6 42.37 37.70 8.986 = 7.91 6.96 6.42 31.11 8.95 6.53 8.12 0.05 * Exceptions: Air — Keenan and Keyes.03 8.81 27.97 6.93 40.01 Ethyne (Acetylene) C2H2 26.99 7. Progress. and temperature. R.95 6.03 Carbon dioxide CO2 44.22 10.53 Air 28.26 25.78 33.0039 58.07 7.46 8.123 20.99 36.248 666 615.33 10.142 551 3.25 23.0305 8.04 18.96 38. 3rd Printing 1947.52 20.23 8.0488 30. Ammonia — Edw.03 7.08 8.204 34.88 19.81 10.16 10.61 23.00 24.123 20.89 Propane C3H8 44.672 707 34.42 8.07 8.94 27.17 27.97 6.6 343 316.0 765 4. Hydrogen Sulfide — J.054 490 0.23 Nitrogen N2 28.75 16.96 6.72 11. April 1953.816 19.0159 6.15 n-Hexane C6H14 86.53 8.010 6.97 6.30 35.36 8.61 Ammonia NH3 17.08 38.41 12.71 31.592 = 1.34 19.04 22. FIG.27 8.09 8.46 8.17 19.12 0. Thermodynamic Properties of Air.95 6.81 0. Determination of pseudo critical pressure.8 propane 0.63 14.86 6. Grabl.69 14.5 pTc = 363. 13-6 13-6 2017 EDITION 76 WWW.46 22. 13-7 Calculation of k Determination of mix.81 52.17 12. API Research Project 44.52 8.96 19.097 15.45 42.02 29.8 829 1.52 8.55 11. Btu/(lb mol • °R) *Data source: Selected Values of Properties of Hydrocarbons. TECH BRIEF FIG.87 6.99 7.17 32.90 12.123 31.47 trans-2-Butene C4H8 56.03 38.14 n-Pentane C5H12 72.49 16.08 25. c name Mol weight nent MCp @ @ 150°F y sure Pc psia perature Tc°R MW 150°F* methane 0. 13-6 Molar Heat Capacity MCp (Ideal-Gas State).03 Water H2O 18. Thermodynamic Properties of Am- monia at High Temperatures and Pressures.41 18.44 12.91 21.97 6. compressor capacity is expressed as the actual volumetric quantity of gas at the inlet to each stage of compression on a per minute basis (ICFM). using a k of 1. sion ratios between 1. compressibility factors can be de- termined from the P-H diagrams.5 14. lb/min) 10. particularly = 4.4 psia and in- take temperature through a compression ratio of 9 in a 2-stage The piston displacement is equal to the net piston area mul- compressor. 13-8 ing degrees. For pure components such as propane. TECH BRIEF FIG. mols/min) 379. we find the horsepower re.5 and 2. Some clearance volume is necessary and it includes the Most gases encountered in industrial compression do not space between the end of the piston and the cylinder head when exactly follow the ideal gas equation of state but differ to vary- 13-7 2017 EDITION 77 WWW. What will be the horsepower? tiplied by the length of piston sweep in a given period of time.55 (10–4) (stroke) (N) (D2– d2) considering the simplifying assumptions necessary in reducing compressor horsepower calculations to such a simple procedure. effective capacity may be typical of these curves. the piston does not travel completely to the end of the cylinder at the end of the discharge Capacity stroke.NET CTSS . therefore. must be con- Volumetric Efficiency sidered as close approximations to true compressor performance. (4) (1728) The two procedures give reasonable agreement. For a k of 1.15.55 (10–4) (stroke) (N) (2 D2– d2) this section are based upon the averaging of many criteria. inlet volume to any stage may be range. Fig.0. For the purpose of performance calculations. Z. calculated as the piston displacement (generally in cu ft/min) multiplied by the volumetric efficiency. quirement to be 136 BHP/MMcfd or 272 BHP. In a reciprocating compressor. (stroke) (N) (D2) Eq 13-10 From Equation 13-4 we find the brake horsepower to be: PD = (4) (1728) (22) (3) (2) (2) (1. (stroke) (N) (2 D2 – d2) Detailed Calculations PD = Eq 13-12 (4) (1728) There are many variables which enter into the precise calcu- lation of compressor performance. The degree in which any gas varies from the ideal is expressed by a compressibility factor. which modifies the Approximate Heat-Capacity Ratios of Hydrocarbon Gases ideal gas equation: PV = nRT Eq 13-5 to PV = nZRT Eq 13-6 Compressibility factors can be determined from charts in Section 23 using the pPR and pTR of the gas mixture. Curves are available which permit easy estimation of ap- proximate compression-horsepower requirements. The results obtained from these calculations. use a factor in the range of 16 to 18 for compres. For a double-acting piston (other than tail rod type). likewise.4. For a single-acting piston compressing on the crank end only. From SCFM 14. Moisture should be handled just as any other component in the gas. calculated by using the inlet pressure P1 and temperature T1. Generalized data as given in = 4.73 wT1 Z1 MW P1 ZL Q= Eq 13-8 From molar flow (Nm. although the user would be better advised to determine the compression horsepower using the P-H diagram (see Section 24). 13-9 is In a reciprocating compressor.CTSSNET.7 NmT1 Z1 Eq 13-9 P1 ZL Q= 520 From these equations. Example 13-1 — Compress 2 MMcfd of gas at 14. This displacement may be expressed: Solution Steps For a single-acting piston compressing on the outer end only.08) = 285 BHP = 4. 13-9. the power requirement would be 147 BHP/MMcfd or 294 total (stroke) (N) (D2 – d2) Eq 13-11 PD = horsepower.55 (10–4) (stroke) (N) (D2) From Fig.7 T1 Z1 520 P1 ZL Q = SCFM Eq 13-7 From weight flow (w. Volumetric efficiencies as determined by Equation 13-14 Clearance volume is usually expressed as a percent of piston are theoretical in that they do not account for suction and dis- displacement and referred to as percent clearance. as a cylinder can be represented by: 13-8 2017 EDITION 78 WWW. the volumetric entire piston displacement as gas capacity. ally spring-loaded check valves that permit flow in one direction clearance volume. the pressure within the cylinder at the piston displacement. 13-9 Approximate Horsepower Required to Compress Gases the piston is at the end of its stroke. end of the suction stroke is lower than the line suction pressure For double acting cylinders. It also includes the volume Zs Zd in the valve ports. crank end of a cylinder. The effect of the gas efficiency should be corrected by subtracting an additional 5% contained in the clearance volume on the pumping capacity of a for slippage of gas. amount. TECH BRIEF FIG. the percent clearance is based and.NET CTSS . the cylinder could deliver its When a non-lubricated compressor is used. VE = 96 – r – C (r1/k) – 1 Eq 13-15 Without a clearance volume for the gas to expand and delay the opening of the suction valve(s). the volume in the suction valve guards. The suction and discharge valves are actu- clearance. Zs Zd ing capacity of a cylinder compared to the piston displacement. lows: The term “volumetric efficiency” refers to the actual pump. This is a capacity correction only and. Sometimes additional clearance volume (exter. only. the pressure at the end of the discharge stroke is on the total clearance volume for both the head end and the higher than line discharge pressure. cu in. For this reason.CTSSNET. These two clearance volumes are not One method for accounting for suction and discharge valve the same due to the presence of the piston rod in the crank end losses is to reduce the volumetric efficiency by an arbitrary of the cylinder. typically 4%. and VE = 100 – r – C (r1/k) – 1 Eq 13-14 the volume around the discharge valve seats. C. The valve springs require a small differential pressure to C= (100) Eq 13-13 open. or cylinder charge valve losses. likewise. cu in. thus modifying Equation 13-14 as fol- nal) is intentionally added to reduce cylinder capacity. the degree of reversal. Rod loads are established charged from the cylinder. PD VE Ps 10–6 MMcfd = Eq 13-16b Zs For example. The energy of compression is used by tor of the supporting structure and crankshaft to withstand the the gas even though the gas slips by the rings and is not dis. torque (turning force) and the loads.. and is therefore too low.) Equation 13-32 gives better results. Gas rod loadings may be calculated by the use of Equa- etc. Inertial effects will tend to increase of 1.4 psia and suction temperature. In evaluating efficiency. crosshead. and because of this. which is commonly used the operator will know only line pressures. can be estimated from Equation 13-18. Larger valve area for a given swept volume will generally lead to higher compression efficiencies. Recent information suggests that this Many manufacturers also require a load reversal of the load modification is not necessary for all models of high speed com. Equation 13-17 would be used: 14.e. sors in the past have tended to be slightly lower than estimated from Equation 13-14. a volumetric efficiency of 80%.4 psia and suction temperature) to a PL and TL basis. bolting. as in Equations 13-19 and 13-20. cumulative. load-carrying capacity. but not recommended. The load-carrying of a compressor involves two primary considerations: rod loading and horsepower.9 would have a capacity based on gas pressure only.4 psia. visor in calculating cu ft/min.4 is as- sumed to equal 1. Using Equations 13-19 and 13-20. a compressor with 200 cu ft/min piston dis. would not be considered when calculating The horsepower rating of a compressor frame is an indica- compressor horsepower. to limit the static and dynamic loads on the frame. Load in compression = Pd Ap – Ps (Ap – Ar) = (Pd – Ps) Ap + Ps Ar Eq 13-19 Equivalent Capacity Load in tension = Pd (Ap – Ar) – Ps Ap The net capacity for a compressor. These deductions for non-lubricated and propane per. and pro- If the compressor is in propane. 13-9 2017 EDITION 79 WWW. If compressibility is not used as a di. useful data on this 18 is the theoretical value. an additional 4% should be subtracted from the volumetric ef- ficiency. volumetric efficiency.0. Rod Loading A tail-rod cylinder would require consideration of rod cross- section area on both sides of the piston instead of on only one Each compressor frame has definite limitations as to maximum side of the piston. point is seldom available in the field. Rod loads are calculated differently based upon the compres- formance are both approximate and.33 MMcfd at 14. TL = (MMcfd from Eq 13-16) Eq 13-17 Discharge Temperature The true rod loads would be those calculated using internal The temperature of the gas discharged from the cylinder cylinder pressures after allowance for valve losses. While the manufacturer may consider The discharge temperature determined from Equation 13. Normally. piston rod. °R or K. at 14. speeds and models. a plus value for the load placement. etc. It neglects heat from friction. Td = Ts (r(k –1)/k) Eq 13-18 A further refinement in the rod-loading calculation would be to include inertial forces. if both apply. se combined rod loads (gas load plus inertia load). Except in special cases. inertial forces are ignored. To convert volumes calculated using Equation 13-16 (i. irre. Some manufacturers use flange-to-flange pressures while others use internal pressures and others may Volumetric efficiencies for “high speed” separable compres. inertial forces when rating compressors.4 TL ZL PL Ts Zs MMscfd at PL. a suction pressure of in both compression and tension indicates a reversal of loads 75 psia. crankshaft. horsepower. at the crosshead pin. and suction compressibility of 0. jected bearing surfaces. sor manufacturer. In many instances the gas sales contract or regulation will specify some other measurement standard for gas volume.4 lb 14. versibility effects. pressure calculations. connecting rod.4 2 Zs Eq 13-16a in which can be simplified to Equation 13-16b when Z14..CTSSNET. TECH BRIEF first approximation. This load reversal is required so that lube pressors.NET CTSS . frame. in cubic feet per day @ = (Pd – Ps) Ap – Pd Ar Eq 13-20 14. may be calculated by Equa- tion 13-16a which is shown in dimensioned form: MMcfd = [ PD ft3 min ] 1440 min d [ ] VE% 100 lb Ps 2 10–6 in MMft3 ft3 Z14. then the statement “not corrected for compressibility” should be added. or similar heavy gas service. (Note: the temperatures are in absolute manufacturers generally rate their compressors based on line- units. oil can lubricate and cool the crosshead pin and bushings. the user should consider past experience with different tions 13-19 and 13-20. 21 – 1)/1. typically 5–10 psi. cooler.94 Equation 13-21. Calculate the compression ratio per stage. 7.975) [2 560/0.93 the discharge pressure of the preceding stage to obtain the suction pressure for the next stage. ond stages from Equation 13-21: lated. Zd = 0. The gas has a 14. Multiplying r by the absolute suction pressure of the Zavg = 0.21/(1.8 at PL 150°F would have an approximate k of 1.NET CTSS . r.82] ture is 100°F. tion: 3. Sum the stage horsepowers to obtain the total compres. es- stages. For by using Fig.8 1. From Fig.21) – 1] horsepower. where s is the number of compression 6. The number of stages. Repeat steps 4 and 5 until all stages have been calcu. Calculate overall compression ratio (rt = Pdfinal/Ps).05 and assuming interstage 1.975 stage being considered will give you discharge pressure of the stage.03 (0. the first ratios determined will be used. s. compression ratio of 3. is < ~ 4. 14.93) [2 580/0. Intake pressure is 100 psia.82] sor power required. 100 psia x 3 = 300 psia (1st stage discharge pressure). Calculate the horsepower required for the stage using 2nd stage: Zs = 0. assuming a high speed compressor? = 138. 900 psia = 3.80 (23 MW). discharge temperature for the Procedure second stage (with r = 3. For this sample problem.05 (compression ratio for 2nd stage) 295 psia Detailed Horsepower Calculation It may be desirable to recalculate the interstage pres- A more detailed calculation of reciprocating compressor sure to balance the ratios.21 – 1)/1. etc. For a multistage machines an allowance should be made for the in.6 + 138. This should be checked after determining the [(Pd/Ps)((k–1)/k)–1] Eq 13-21 average cylinder temperature. 5.03 Zavg [QgTs/E] (k/(k-1)) compression applications. This should gener. Discharge temperature for the 1st stage may be obtained horsepower required for each of the stages that are utilized. Suction pressure to second stage is given by 300 psia – 5 = 295 psia Where the 5 psi represents the pressure drop between first stage discharge and second stage suction.65 psia and 60°F. Compression ratio is 900 psia Note that in Example 13-1 the same conditions result in a =9 compression power of 285 BHP which is close agreement.65 520 [1. 13-32 or solving Equation 13-18. therefore. should be increased timate the compressibility factors at suction and dis- until the ratio per stage. charge pressure and temperature of each stage. 13-8 a gas with specific gravity of 0. r. cooling to 120°F) equals approximately 244°F.65 520 specific gravity of 0. mately 220°F.6 Example 13-2 — Compress 2 MMscfd of gas measured at 14. 7. 100 psia This would be a two-stage compressor.21/(1.. Discharge pressure is 900 psia. ally result in stage discharge temperatures of < 300°F depending on the interstage cooler outlet temperature 1st stage: Zs = 0. BHP for 1st stage = 3. For most TL BHP/stage = 3. 4.21 – 1)] [(300/100)((1. however. the 150°F curve will be ad- equate. Calculate the horsepower required for the first and sec- 6.21 – 1)] [(900/295)((1.82 Total BHP required = 137. In the same manner.98 assumed.97 3. 2. From the physical properties section (Section 23). discharge temperature = approxi- terstage pressure drop associated with piping. Subtr ac t the assumed interstage pressure loss from Zavg = 0. Zd = 0.21) – 1] = 137.03 (0. and intake tempera- BHP for 2nd stage = 3. Average cylinder temperature = 182°F.2 Assume E = 0. by taking the s root of rt. What is the required brake [1.2 = 275.CTSSNET.21. power requirements can be performed using the following equa. the ratio 13-10 2017 EDITION 80 WWW. Average cylinder temperature = 160°F. The total horsepower for the compressor is the sum of the 4. TECH BRIEF 2.92 5. scrubber. CTSSNET. the selection of valve materials is important to pre- vent excessive wear. API standard 618 recommends 1000 psig as the maximum pressure for both cast iron and nodular iron. Recognition of the box. A small amount of gas leaking through the packing can be pression per stage are used (plus an allowance for piping and objectionable.or double-acting pistons. If cylinders are re- cause of the oil vapors present. or simply vented. even though mechan. In practice. an extended cylinder ratio of compression will mean a low volumetric efficiency and connecting piece can be furnished. thermal shock. inlet and discharge gas pipe connections on the Cylinder Material Discharge Pressure (psig) cylinder are fitted with flanges of the same rating for the fol- Cast Iron up to 1. equal ratios of com. The non-lubricated compressor has found wide application Packing life may be significantly shortened by the dual re. etc. For this piston rod so that no lubricated portion of the rod enters the reason a high rod loading may result and require a heavier and more expensive frame. a tem- perature closer to 250°F or 275°F may be the practical limit. which may be either single-compart- design. Although oilwiper rings are used on the piston rod where above variables is. When handling gases containing oxygen. 5. Non-metallic packing seal In summary. still useful.200 to 3. or local government regulation). TECH BRIEF Limits to compression ratio per stage — The maximum to either form or line the pressure wall. especially gas or fluid and held under a slight pressure. 13-10 through 13-12. or corrosion resistance High-pressure compressors with discharge pressures from may also be a determining factor. and for most field applications. for safety. Forged Steel above 2. with other gases to prevent system contamination. which could sup- port combustion. it leaves the compressor frame. Cast Steel 1. Therefore. the cube root. 13-11 2017 EDITION 81 WWW. how- ever. Reciprocating Compressor Control Devices Cylinders are designed both as a solid body (no liner) and Output of compressors must be controlled (regulated) to with liners. temperatures of mechanical. decreasing the compression ratio in the Compressor valves for non-lubricated service operate in an higher stages to reduce excessive rod loading may prove to be environment that has no lubricant in the gas or in the cylinder. state. it is absolutely necessary that all traces of hydro- in the first stages and occasionally single-acting in the higher carbons in cylinders be removed.000 psi usually require special design and a com- charge pressure limits generally used in the gas industry for plete knowledge of the characteristics of the gas.000 Hydrostatic test. For two stages of compression the ratio per stage would ment or double-compartment. double-acting pistons are commonly used and helium. cylinder material selection. usually at 150% design pressure.200 lowing reasons: Nodular Iron about 2. advantageous.500 Suction pulsation bottles are usually designed for the same pressure as the discharge bottle (often federal. To reduce carbonization of the oil and the danger of fires. a safe operating limit may be considered to be approximately 300°F. Cylinder Design Piston rod packing universally used in non-lubricated com- Depending on the size of the machine and the number of pressors is of the full-floating mechanical type. there is a possibility of fire and explosion be. minute quantities of oil might conceivably enter the cylinder on the rod. at higher discharge pressures. Standard cylinder liners are cast iron. the use of rings of a type that requires no lubricant is used on the stuffing 300°F maximum would be a good average. mechanical shock. The dry type lines the cylinder wall and is not required to add strength.500 Practicality and uniformity of casting and machinery.000 to 30. For this reason.NET CTSS . of the water jacket. When handling oxygen and other gases such as nitrogen In the same units. other mate- rials or special alloys may be needed. consisting of a stages. These may be furnished gas tight approximately equal the square root of the total compression and vented back to the suction. cylinder. this is required stages of compression. each cylinder. Special distance pieces are furnished between cooler losses if necessary) unless otherwise required by process the cylinder and frame. There are two types. in Figs. The table below shows dis. where it is desirable or essential to compress air or gas without quirement to seal both high pressure and high temperature contaminating it with lubricating oil. This simply lengthens the require a larger cylinder to produce the same capacity. in high-pressure work. 13-13). see examples sign. for three stages. Cylinder materials are normally selected for strength. reciprocating compressors are furnished with cylinders case containing pairs of non-metallic rings of conventional de- fitted with either single. Where multi-stage operation is involved. With oxygen. ratio of compression permissible in one stage is usually limited The wet liner forms the pressure wall as well as the inside wall by the discharge temperature or by rod loading. ical or process requirements usually dictate a lower figure. Most compressors use oils to lubricate the cylinder with a Where no oxygen is present in the gas stream. As a rule. Cylinder liners are inserted into the cylinder body match system demand. quired to have special corrosion or wear resistance. or may be filled with a sealing ratio. however. force-feed lubricator having one or more feeds to 350°F may be considered as the maximum. Where even such Economic considerations are also involved because a high small amounts of oil are objectionable. For such cases a number of manufacturers furnish a “non- lubricated” cylinder (Fig. gases. 13-11 FIG.NET CTSS .000 psig Discharge 13-12 2017 EDITION 82 WWW. TECH BRIEF FIG.CTSSNET. 13-10 Low Pressure Cylinder with Double-Acting Piston FIG. 13-12 High Pressure Cylinder with Double-Acting Single-Acting Plunger Cylinder Designed for Piston and Tail-Rod 15. In these cases the combinations of pockets open. and no load capacity (used for start-up only) is compressors must be unloaded to some degree before start. 13-13 or starts the compressor by means of a pressure-actuated switch Piston Equipped with Teflon ® Piston and Wear Rings for as the gas demand varies. The cylinder capacity lines frequency drive (VFD) electric motor driven compressors and to represent the range of pressures calculated with all possible units driven by internal combustion engines. flow. The driver capacity line indicates the maximum allowable sor is to vary the speed. 13-13 2017 EDITION 83 WWW. A falling pressure indicates that gas is being used faster than it is being compressed and that more gas The purpose of this curve is to determine what steps of un- is required. one-quarter load. The nature of the control loading operation for a double acting cylinder at three capacity device will depend on the regulating variable — whether pres. three-quarter load. open. A common method of controlling the capacity of a compres. 13-14) operate to hold the compressor inlet valves open and thereby prevent compression. and holding open Fig. Often constant flow or a spe. This will produce a “saw methods of controlling the capacity are necessary. discharge to suction bypass. one-half. If suction valves were and constant-speed control. one-half load. Full Unloading for Starting — Practically all reciprocating load. pressor. Five-step control (full load. A rising pressure indicates that more gas is being loading are required to prevent the driver and piston rods from compressed than is being used downstream and that less gas serious overloading. a single set of curves for a given machine unless there are side cific power is required despite variations in operating condi. on the compressor driver to control the speed. Starting at the end (line 0-0) with full cylinder capacity. The letters adjacent to the low-pressure diagrams rep- sure. This is in reality a variation of constant-speed control in which unloading is ac- complished in a series of steps. and no load) is accomplished by means of clearance pockets. reducing the intake of additional gas. as necessary. Compressor capacity. and constant speed.NET CTSS . The driver can be a gas engine or electric motor. On recipro. temperature. Motor-driven reciprocating compressors above 100 hp in size are usually equipped with a step control. 13-15. or pressure may be varied Fig. The curve illustrates the relationship be- regulate capacity or maintain the compressor load within the tween compressor capacity and driver capacity for a varying driver rating. to cover the capac- regulator actuates the VFD controller or fuel-admission valve ity of the driver. These are automatic-start-and-stop control (opened or closed) required for unloading. ing on their design. not exceeded. points. 13-15) consist of pockets or small reservoirs which are opened when unloading is desired. the Electric motor-driven compressors usually operate at con. The number of cating compressors up to about 100 hp. stops FIG. loads or it is a multi-service machine. All lines are plotted for a single stage com- is required. or some other variable — and on type resent the unloading influence of the respective and cumula- of compressor driver. point it is dropped to the next largest cylinder capacity and fol- creasingly more common. This method is applicable to variable capacity for a given horsepower. two types of control are “teeth” depends upon the number of combinations of pockets usually available. as its name implies. Both manual and automatic compressor startup Zero-capacity operation includes holding all suction valves unloading is used. The gas is compressed into them on the compression stroke and expands back into the cylinder on the return stroke. Constant-speed control permits the compressor to operate at full speed continuously. sor unloading operation with a step-control using fixed volume Capacity Control — Capacity control is required to either clearance pockets.CTSSNET. also unloaded then there would be more “teeth” on the curve. Clearance unloaders (Fig. tive effect of the various pockets as identified in Fig. speed. TECH BRIEF Automatic-start-and-stop control. and clearance unloaders. line is traced until it crosses the driver capacity line at which stant speed. etc. It should be used only when the de- a Single-acting Non-Lubricated Cylinder mand for gas will be intermittent. Capacity control devices/unloading devices can be compressor suction pressure at a constant discharge pressure manually actuated or actuated by air or gas pressure depend. tions. Common methods of unloading include: dis. On some makes of machines inlet-valve and clearance control unloading are used in combination. Two methods of unloading the compressor with this type of control are in common use: inlet- valve unloaders. obtained by holding corresponding suction valves open or add- ing so that the driver torque available during acceleration is ing sufficient clearance to produce a zero volumetric efficiency. hence the name “saw tooth” curve. For constant speed motors other low until it crosses the driver line. charge venting. 13-17 shows an alternative representation of compres- the inlet valves using valve lifters. Inlet-valve unloaders (Fig. In many installations some means of controlling the output A common practice in the natural gas industry is to prepare of the compressor is necessary. but loaded part of the time and fully or partially unloaded at other times. varying from full load down to no load. 13-16 shows indicator cards which demonstrate the un- in accordance with the requirements. although variable speed drives are becoming in. tooth” effect. 13-16 Gas Pulsation Control Indicator Diagram for Three Load Points of Operation Pulsation is inherent in reciprocating compressors because suction and discharge valves are open during only part of the due to overshoot & undershoot stroke. FIG. Pulsation must be damped (minimized) in order to: a. for a two stage application. which is a pressure ves- i. a movable cylinder head is provided for variable clearance in the cylinder (Fig. prevent overloading or underloading of the compressors. Undershoot b. 13-15 Pneumatic Actuated Valves Controlling Four Fixed Pockets in Compressor for Five-Step Control Capacity at Standard Conditions Constant Discharge Pressure and Speed A A/B A/B/C A/B/C/D open open open open Note: No suction valves are unloaded 13-14 2017 EDITION 84 WWW. The simplest additional stage another “saw tooth” curve must be constructed. or a surge drum.NET CTSS . 13-14 Inlet Valve Unloader and all suction valves unloaded during start-up only FIG. and c. two curves are required to at. inlet or outlet.e. to open and close clearance pockets. 13-17 “Saw Tooth” Curve for Unloading Operation FIG..CTSSNET. TECH BRIEF The same method is followed for multi-stage units. one is a volume bottle. sel. or valves. 13-18). provide smooth flow of gas to and from the compressor. FIG. Where manual operation is provided. it often consists of a valve. reduce overall vibration. manual operation is satisfactory for many services. unbaffled internally and mounted on or very near a cylinder tain the final results. For each There are several types of pulsation chambers. In some cases. Although control devices are often automatically operated. /4) (15) = 424 cu in 2 Inside diameter of pipe must be used in figuring manifolds. 13-19: This is particularly important in high-pressure work and in small sizes where wall thickness may be a considerable per- centage of the cross sectional area. the common bottle.5. 13-19 Approximate Bottle Sizing Chart 13-15 2017 EDITION 85 WWW. Performance of volume bottles is not normally guaranteed NOTE: When more than one cylinder is connected to a bottle.180 cu in. proximately 7.CTSSNET. the suction bottle multiplier is ap- inders operating in parallel can also serve as a volume bottle. particularly where large Cylinder stroke = 15 in cylinders are involved. compressor manufacturers can be volume to absorb most of the pulsation. From Fig. Having determined the necessary volume of the bottle.NET CTSS . and appearance. Several industry meth. Suction-bottle volume = (7. ment for gas-pulsation control are also available. thumb for their sizing. Fig. the proportioning of diameter and length to provide this volume re- Example 13-3 quires some ingenuity and judgment. Organizations which provide designs and/or equip- ods were tried in an effort to produce a reasonable rule-of. space limitations. 13-18 Sectional View of a Cylinder Equipped with a Hand-Operated Valve Lifter and Variable-Volume Clearance FIG. Volume bottles are sized empirically to provide an adequate For more accurate sizing.5) (424) = 3. without an analysis of the piping system from the compressor the sum of the individual swept volumes is the size required for to the first process vessel. 13-19 may be used for approximate bottle sizing. Minimum manifold length is FIG. Indicated discharge pressure = 1400 psia A good general rule is to make the manifold diameter 1-1/2 Cylinder bore = 6 in times the inside diameter of the largest cylinder connected to it. TECH BRIEF A manifold joining the inlet and discharge connections of cyl. It is desirable that mani- folds be as short and of as large diameter as is consistent with Indicated suction pressure = 600 psia pressure conditions. At 600 psi inlet pressure. consulted. but this is not always practicable. and an electric motor) will have torsional natural design of the pulsation dampening equipment is based on an frequencies. tions. Length. nozzles what is the impact? Typically the torsional loads will happen should be located near the center of the chamber to reduce un. and pressure drop through the equipment of not more than for 1-2 months is often much larger. in. Length. large.0 9 18" 1432.2 2 1 20. cu in. 13-20 gives ap. The detailed discussion of recommended design approaches for pul. and in large volume units. or for a minimum of 2/3 of the normal operating loads. installation differences. in.0 67 8 14" 684. 13-20 Welding Caps Standard weight Extra strong Double Extra strong Pipe size Volume. For the mechanical natural frequency.3 411 16 120 5 10" 295.CTSSNET.0 13 7 16 3313.3 31 2 65. Volume.0 101 16 20" 2026. Manufacturing tolerances. and dampeners) are generally built to Section VIII of ASME Code and suitable for applicable cylinder relief valve set pres.0 137 16 13-16 2017 EDITION 86 WWW. The tions among these elements. Some additions must be made to the minimum thus determined to allow for saddle reinforcements and for welding All rotating equipment experiences a torsional load. curs in a horizontal or vertical direction. to mechanical natural frequencies of piping or the compressor ing speed range. frequency of the oscillation is the torsional natural frequency. the loads of other operating scenarios. in. but the downtime and cost of having the unit unavailable tem. the deflection oc- composition. and loading all play a critical part in Suction pulsation chambers are often designed for the same the system’s ability to operate without failure. A A torsional failure will typically occur without warning. 4" 24. compressor or engine. end. This applies at design condition and not necessarily for other operating pressures and flows.0 713 16 16" 967. As well as the pressure as the discharge units. Length. ples of torsional loads are: It is customary to close the ends of manifolds with welding inertia and gas loads from the pistons in a reciprocating caps which add both volume and length. Volume. the results can be catastrophic! Destroyed coupling. broken compressor shaft or broken motor shaft are potential mum residual peak-to-peak pulsation pressure of 2% of average consequences of torsional resonance. the torque fluctuations from a synchronous motor during startup. Consider fixing one end of a shaft and twisting the free piping and equipment system and considers dynamic interac.0 67 8 475. TECH BRIEF determined from cylinder center distances and connecting pipe Torsional Analysis diameters. when released the shaft will rotate back and forth. Those torsional natural frequencies are analogous acoustical study which takes into account the specified operat. at run speed and harmonics. The sor. FIG. Exam- of caps. Pulsation Dampeners (Snubbers) A complete drive train (for example reciprocating compres- A pulsation dampener is an internally-baffled device. the deflection is a twisting about the axis of the that simulates the entire compressor. it plays in the torsional system. Fig.NET CTSS . or proximate volume and length of standard caps. the torsional analysis should consider design discharge pressure. Pulsation dampeners are typically guaranteed for a maxi.5 4 11 16 122. and will not detect torsional problems. and variations in gas shaft.0 111 4 24" 3451.4 53 4 12" 517. such as compressor valve failures (upset) or the unit startup (transient). If a torsional natural frequency balanced forces. The best insur- ance against a torsional failure is a design study before a unit As pressure vessels.6 9 911. A design study will consider each component and the role sure. Pulsation dampeners also should be mounted as close as When the system is started and the compressor is loaded possible to the cylinder.6 53 4 264. shaft. are designed to detect lateral (horizontal or vertical) vibra- Reciprocating Compressors for General Refinery Services. occurs near a frequency where there is significant torsional energy. pulsation dampeners.0 21 2 15 3 6" 77. conditions of unloading. coupling.4 111 4 1938. 1% of the absolute pressure.6 10 1 16 1363. cu in.6 713 16 640.7 31 2 48 4 8" 148. The cost of repair can be absolute pressure at the point of connection to the piping sys. all pulsation chambers (volume bottles is built. For a torsional natu- Analog evaluation is accomplished with an active analog ral frequency. cu in. vibration sensors installed at bearings or on component frames sation suppression devices is presented in API Standard 618. dynamic tilting pad thrust bearing. and the resulting force is balanced by a hydro- present information for evaluating compressor performance. The extent of this overlap depends on a number of things. Considera. the problem is in the high pressure cylinder. Fig. vert velocity into static pressure. The secondary objective is to balance piston. Before rected by cleaning. The gas entering This will rise. when operating at a given load diffuser. or after the diffuser of the last impeller in a multi stage a thorough knowledge of the interrelated functions of the vari. The discharge ous parts and the effects of adverse conditions. or to operating sors on the low end of the flow range. compressors. or turboexpanders. staging. The best indica. or higher. parts and systems. or a simple cavity that collects tical. point. tion with unsuitable coolant or lubrication.000 rpm. Refer to (single stage) compressor would normally have application be. operational requirements. sometimes rapidly. Difficulties of this type can usually be cor. CENTRIFUGAL COMPRESSORS The rotating part of the compressor consists of all the impel- lers. changing shaft material or size are all easily done if the ity to select optimized impeller flow coefficients for the specified components have not been built. the inlet nozzle of the compressor is guided (often with the help tion or breaks. nozzle. Other seal types have been stage) centrifugal compressor is normally considered for inlet used in the past. pressor that accomplish the compression task are described in tion of discharge valve trouble is the discharge temperature. Modifications to a system that process conditions.000 rpm (the same pressures. An impeller consists of the discharge temperature from each cylinder.8 to 0. and maladjustment. tween 100 and 150.000 inlet acfm. This is one very good reason for keeping a record of guide vanes) to the inlet of the impeller. Discharge Figs. only.NET CTSS . Changing the coupling size or style. or the use of the machine on a ered by API Standard 617. compressor. elimination of an adverse a technical decision could be reached as to the type of compressor condition. If the the pressure drops. Major trouble can usually be traced to long periods of opera. If Diffusers can be vaneless or contain a number of vanes. cylinders. and economics would have to be considered. liquid. Components of Centrifugal Compressors A defective inlet valve can generally be found by feeling the valve cover. TECH BRIEF With early involvement by designers. brought in front of the next impeller through the return chan- nel and the return vanes.85 Mach number at the units where the operating conditions will be changed signifi. which can further con- of possible troubles with their causes and corrections is imprac. 13-22 gives an approximate idea of the flow range that To keep the gas from escaping at the shaft ends.000 inlet volume. of 40. the trouble is in the low pressure cylinder. steam or gas turbines (with or without speed-increasing Minor troubles can normally be expected at various times dur. configured compressor (the same compressor frame. These troubles are most There is an overlap of centrifugal and reciprocating compres- often traced to dirt. If the compressor has only one impel- Troubleshooting is largely a matter of elimination based on ler. while accurate to determine whether a centrifugal compressor should the axial thrust generated by the impellers is balanced by a be considered for a specific job. 13-21). The essential components of a centrifugal com- ally tell by feel if a particular valve is leaking. with more than 4–5 impellers. gears). As we will see later. If ler flow coefficients and high compression ratios or compressors this occurs. Recent advances in machine design have cantly from the existing conditions. and especially if the unit is resulted in production of some units running at speeds in excess being restaged. when a valve is in poor condi. dry gas seals a centrifugal compressor will handle. A complete list system can either make use of a volute. indicates trouble in one or the other of the two stages. delivery of the unit will be delayed. impeller tip and eye. 13-23 through 13-25 provide cross sectional drawings valve leakage is not as easy to detect since the discharge is al. coupling and driver) and similar operating conditions Most centrifugal compressors operate at speeds of 3. the service. A multi-wheel (multi. part of the velocity is converted into static pressure. This rotor runs on two radial bearings (on all modern com- This section is intended to supply information sufficiently pressors. that would be installed. 13-17 2017 EDITION 87 WWW. the gas will leave the impeller Recording of the interstage pressure on multistage units is with an increased velocity and increased static pressure. the gas enters the discharge system. see Fig. 13-22 efficiency values should be used as a reference modified. service for which it was not intended. Centrifugal compressors are usually driven by electric mo- Troubleshooting tors. a limiting factor being impeller stress considerations tion should be given to doing a torsional analysis on existing as well as velocity limitation of 0. and identification of major components for typical centrifugal ways hot. but virtually all modern centrifugal compres- volumes between 500 and 200. compressor has more than one impeller. these are hydrodynamic tilting pad bearings). Torsional design analyses should be done on all new units These efficiencies reflect compressor designs after say 1998. unless there is successful operating experience with a similarly in general earlier designs could be 4% lower in efficiency. temperatures and load steps). ing routine operation of the compressor. the gas will be again If it rises. but the following list of the more frequently encountered the gas before it exits the compressor through the discharge troubles and their causes is offered as a guide (Fig. the system can be Fig. adding a fly. proper adjustment. It will be much warmer than normal. or quick replacement of a relatively minor part. and will deteriorate for non-optimal impel- is already built can be expensive and may require re-design. A single-wheel sors used in the oil and gas industry use dry gas seals. Experienced operators of water-cooled units can usu. of a number of rotating vanes that impart mechanical energy to the gas. In the valuable because any variation. A multiwheel compressor can be thought of as a series of single wheel compressors con- tained in a single casing. are typically used on both shaft ends. the following text referring to Figure 13-24.CTSSNET. careless operation Design requirements for centrifugal compressors are cov- and inadequate maintenance. the Dry Gas Seals discussion for additional information. On the higher personnel being unfamiliar with functions of the various machine end of the flow range an overlap with the axial compressor exists. The efficiencies of centrifugal compressors rely on the abil- wheel. 13-3. Fig. 7. 2. next higher stage. TECH BRIEF The entire assembly is contained in a casing. For discharge The centrifugal compressor approximates the constant head- pressures below about 3400 kPa (500 psi). Broken or leaking valve(s). Motor Will Not 2. 4. and its performance is with end caps on either end. Compressor Will 2. Popping 6. Faulty seal installation. of cylinder. etc. 4. Dirty oil filter. (Fig 13-25). 4. 1. Improper ring side. 1. 1. 1. while the reciprocating is a constant tally split to allow the installation of the rotating components. 1. Improper fit of rings to rod/side clearance. consists of a center body A compressor is a part of the system. 6. high flow machine. Worn or broken piston rings or expanders. 6. Piston hitting outer head or frame end 6. Excessive Carbon 4. Temperature 3. Packing Over. Lubrication failure. Excessive temperature due to high 2. 10. Courtesy of Ingersoll-Rand Co 13-18 2017 EDITION 88 WWW. 3. Switchgear or starting panel. 5. Leaking discharge valves or piston rings. Cold oil. 13-21 Probable Causes of Reciprocating Compressor Trouble Trouble Probable Cause(s) Trouble Probable Cause(s) 1. such The operating characteristics must be determined before an as desired compression ratio. Incorrect power factor. 2. 1. Heating lube rate. 13-26 gives a rough comparison of the characteris- tics of the axial. Excessive rate of pressure increase. Packing rings assembled incorrectly. made. seals. 2. Excessive 1. 5. Excessive starting torque. 1. Improper lube oil and/or insufficient Crankshaft Oil 1. Dirt in packing. 2. Excessive lube oil. Excessive piston rod run-out. Scrapers incorrectly assembled. Cold oil. 3. Valve improperly seated/damaged seat Frame Knocks 3. Loose/worn main. Leaking suction valves or rings on next Relief Valve 5. Broken or leaking valves causing high On Valves temperature. High Discharge 2. Seal Leaks 2. Leakage Scraper Leaks 3. Plugged packing vent system. 3. Control panel. Worn packing rings. 8. Defective pressure gauge. 7. The axial compressor. Low Oil Pressure and/or bearings. and reciprocating compressor. 9. rags).CTSSNET. the compressors are usually of the barrel is a low head. Improper low oil-pressure switch setting. 1. Loose crosshead pin.or end-gap clearance. FIG. crankpin or crosshead 5. crosshead shoes. Incorrect oil. 5. Oil pump failure. striking oil surface. lube rate (blue rings). 4. number of wheels. siz- evaluation of compressor suitability for the application can be ing of compressor. 3. Loose piston. bearings. pin caps or 3. Scored piston rod. Worn scraper rings. type. Obstruction (foreign material. volume-variable head machine. Bearings. The desired system capabil- namic components (both rotating and stationary) can slide in ity or objective must be determined before a compressor can be and out of the center body once one of the endcaps is removed selected. 6. Worn/scored rod. 4. Low voltage. The curves are affected by many variables. variable volume machine. Improper lube oil and/or insufficient not Start 3. Defective oil relief valve. 5. Low gear oil pump by-pass/relief valve due to leaking inlet valves or rings on setting. Power supply failure. Fouled water jackets on cylinder. Excessive leakage at bearing shim tabs 3. falls somewhere in between. 1. Excitation voltage failure. The pressure containing casing. Fig. which For higher pressures. Clogged drain hole. Free air unloader plunger chattering. High inlet temperature. Packing Piston Rod Oil 2. Excessive compression ratio on cylinder 8. centrifugal. Oil carryover from inlet system or Synchronize 3. 13-27 is a typical performance map which shows the Performance Calculations basic shape of performance curves for a variable-speed centrifu- gal compressor. gasket. 2. Oil foaming from counterweights pressure ratio across cylinders. Noise In Cylinder 4. Interior frame oil leaks. Low oil pressure shutdown switch. 7. dictated by the system resistance. Plugged oil sump strainer. Insufficient cooling. Fouled intercooler/piping. 9. higher stage. Improper lube oil and/or lube rate. 4. shaft and aerody. the casing is horizon. Faulty relief valve.NET CTSS . 4. previous stage. 11. Loose crosshead lock nut. type of gas. blind or valve closed in discharge line. Knock is actually from cylinder end. Low oil pressure. 500 0.000 0.500 a compressor at different speeds can be compared (Kurz and 500.000 0. the less deviation is 145.81 3. 7.000.000 0.000 0.84 0.76 10.55.81 2. the centrifugal compressor can deliver constant capacity at variable pressure.84 0.78 0.81 4.000 0.500. variable capacity at con- Approximate Centrifugal Compressor Flow Range stant pressure.000-145.84 0.000. 2003).84 0.800 sors).81 6.65 20.33.81 2.NET CTSS . which is strictly only true for identical Mach numbers in all stages. operating points of 100. This fact is captured in the fan law.20.300 k1Z1RT1 80.84 0.500 Ohanian. 13-22 With variable speed.000 0. but 7.84 0.68 0. The more stages the compressor has.500 Mach number: 33.000-115.000-200.CTSSNET. 500 0. TECH BRIEF FIG.900 u MN = Eq 13-22 55.200 which is still a good approximation for cases where the machine 20.80.000 Similarity Law (Fan Law) (inlet acfm) efficiency efficiency ft head/wheel Under certain simplifying conditions.000 0.600 changes by less than 10% (for single and two stage compres- 115. or a combination variable capacity and variable pressure.81 8.81 4.000.84 0. Nominal flow Average Average Speed to range polytropic isentropic develop 10. 2002).500 acceptable (Kurz and Fozi. then the compressor will show the follow- FIG. 13-23 Example Centrifugal Compressor Showing Nomenclature of Key Parts 13-19 2017 EDITION 89 WWW. The fan law is based on the fact that if for two operating points A and B all velocities change by the same factor (which in particular means that none of the flow angles change). pression ratio (i. These terms are of- posed on the chart: Line A represents typical system resistance ten used interchangeably. These curves are only suitable for estimat- GHPA GHPB Eq 13-24 = ing only and are not intended to take the place of a “wheel-by- NA3 NB3 wheel” selection by the compressor manufacturer.CTSSNET.NET CTSS . the curves be used to calculate performance using field data in pressor operates will force the compressor to operate along the an attempt to determine a variance from predicted performance fan line. such as a refrigeration unit where there is determine mass flow. 13-27 depicts typical performance curves with a small the weight flow in lb/min is known. Fig. All centrifugal compressors are based on flows that are law. ating condition of the system. and the new operating condition of because the centrifugal wheel is sensitive to inlet volume. This curve can be used in reverse to of a closed system.. and specific speed. 13-24 Typical Centrifugal Compressor Cutaway 13-20 2017 EDITION 90 WWW. 13-30 is a useful curve to find inlet (actual) cfm when Fig. 13-29 through 13-36 may be used for estimating com- pressor performance. This is indicated by the surge line in Fig. 13-29 is used to convert scfm relationship that is not (at least not exactly) following the fan to icfm. In general. TECH BRIEF ing relations between two different operating points : system. The range of NA NB stable operation is reduced because of the larger compression HisA HisB Eq 13-23b ratio. a relatively constant discharge pressure. The system resistance has been superim. both denote the gas at suction conditions. 13-27. com- the compressor (as described by the fan law) sets the new oper. This is done described by the fan law). head). such as pipeline application where pressure increases with capacity. NA2 NB2 A = B Estimating Performance and therefore Figs. Actual cfm and inlet cfm compression ratio. Line B is an open-end FIG. QA QB Eq 13-23a = Fig. the system will enforce a head and flow based on manufacturer’s data. 13-28 shows a higher compression ratio.e. nor should This does not imply that the system within which the com. Fig. The intersection of the new resulting system pressure (not converted to inlet or actual cubic feet per minute. 13-28 being fur- = ther to the right than in Fig. Fig. t1 = 0°F the range of 60 to 70%. 60 to 75%.CTSSNET. 13-31. since mechanical problems as well as safety problems may ex. Note: for a natural gas with k = 1. TECH BRIEF Fig.NET CTSS .15.0.000 icfm the compression.30 t2 = 480°F (excessively ist. This curve includes compressor efficiencies in the range of high). Q1 = 10. It includes overall compressor efficiencies in k = 1. Dis- charge temperatures above the 400°F range should be checked Answer: t2 = 230°F (approximately) from Fig. 13-33 gives the approximate horsepower required for Example 13-4 — Given: r = 10. FIG. 13-25 Centrifugal Compressor Cross Section 13-21 2017 EDITION 91 WWW. 13-31 is used to determine the approximate discharge Find: Discharge temperature temperature that is produced by the compression ratio. see Figs. Unless otherwise specified. = 1.000 lb/min FIG. Higher Compression Ratio 13-22 2017 EDITION 92 WWW. w. If the number of wheels is not a whole number. the equa- tions in this section should be used. This method applies to a gas mixture for which a P-H diagram chart is not available. Fig. Low Compression Ratio Compressor Performance. 13-27 FIG. TECH BRIEF Example 13-5 — Given: Weight flow. 13-28 Compressor Performance.000 from Fig. 13-6 and 13-7. FIG.CTSSNET. use the next highest number. 13-33. 13-26 head = 70 000 ft-lb/lb Compressor Head Find: Horsepower Answer: GHP = 3. All values for pressure and temperature in these calculation procedures are the absolute values.NET CTSS . volumes of flow in this section are actual volumes. and discharge temperature. 13-36 predicts the approximate number of compressor wheels required to produce the head. To calculate the properties of the gas. Calculating Performance When more accurate information is required for compressor head. gas horsepower. 13-29 ICFM to SCFM Z=1 13-23 2017 EDITION 93 WWW.NET CTSS .CTSSNET. TECH BRIEF FIG. NET CTSS . TECH BRIEF FIG. 13-30 Mass Flow to Inlet Volume Flow Z=1 13-24 2017 EDITION 94 WWW.CTSSNET. TECH BRIEF FIG. 13-31 Approximate Discharge Temperature Z=1 13-25 2017 EDITION 95 WWW.NET CTSS .CTSSNET. CTSSNET.NET CTSS . 13-32 Head Z=1 13-26 2017 EDITION 96 WWW. TECH BRIEF FIG. TECH BRIEF FIG.CTSSNET.NET CTSS . 13-33 Approximate Horsepower Determination FIG. 13-34 Efficiency Conversion 13-27 2017 EDITION 97 WWW. 545) (T1) (Z1) 1545 ZavgT1 P2 (n – 1)/n Eq 13-34b MW (n – 1)/n P1 Q= Eq 13-25 Hp = –1 (MW) (P1) (144) If we assume the compression to be isentropic (reversible (w) (Hp) Eq 13-35 adiabatic.000) ZRT P2 (k – 1)/k Eq 13-26 Polytropic and isentropic head are related by MW (k – 1)/k P1 His = –1 Since these calculations will not be wheel-by-wheel.CTSSNET. hp 30 si Ca #4 The approximate theoretical discharge temperature can be #1 #3 d calculated from: an 20 #2 P2 (k – 1)/k P1 ideal = T1 –1 Eq 13-29 T2 = T1 ideal Eq 13-30 10 The actual discharge temperature can be approximated: 7 P2 (k – 1)/k – 1 1 2 3 4 5 6 8 10 20 P1 Eq 13-31 Shaft speed.NET CTSS .) The equations for head and gas horsepower based upon polytropic compression are: 10 ZavgRT1 P2 (n – 1)/n Eq 13-34a 7 MW (n – 1)/n P1 Hp = –1 1 2 3 4 5 6 8 10 20 Shaft speed.# ze GHP = si #5 ( is) (33.500 13-8).600 ZavgRT1 P2 (k – 1)/k Eq 13-27a MW (k – 1)/k P1 His = –1 6 150.500 10. use FIG. constant entropy).000 4.800 which can also be written in the form: a.000 8. Oil-seal horsepower losses T2 = T1 + Tactual Eq 13-32 70 60 Polytropic Calculation 50 Sometimes compressor manufacturers use a polytropic path 40 6 . Bearing horsepower losses 1545 ZavgT1 P2 (k – 1)/k Eq 13-27b 80 MW (k – 1)/k P1 His = –1 70 60 The gas horsepower can now be calculated from: 50 6 (w) (His) Eq 13-28 40 .000) ng Bearing loss. N. 13-7 and 1 7. thousand rpm Courtesy Chemical Engineering Magazine 13-28 2017 EDITION 98 WWW.200 Isentropic Calculation 3 33. hp 30 #4 gs 1 d# n k #3 sin (k – 1) = Eq 13-33 an p (n – 1) Ca #2 20 (See Fig. then: GHP = ( p) (33. TECH BRIEF To calculate the inlet volume: which also can be written in the form: (w) (1.# instead of isentropic. N. For this. Polytropic efficiency is defined by: ize #5 Oil-seal loss. is normally determined at the average suction and discharge temperature (see Figs.900 To calculate the head: 5 115. 2 20.000 2. 13-35 the average compressibility factor: Mechanical Losses Z1 + Z2 Zavg = 2 Max Flow (inlet Nominal Speed Casing Size acfm) (rpm) The heat capacity ratio. the head will be calculated across the entire machine.000 6.400 4 55.000 3. k. thousand rpm actual = T1 is b. 13-34 for conversion of isentropic efficiency to poly- tropic efficiency. especially for gear. This equation will give a head of 10. With these two points located the differ- ing can cause damage to the thrust bearing due to the rotor ential isentropic enthalpy can be calculated from the following shifting back and forth from the active to the inactive side. seals. surg- charge state point (2is).5 to windage.000 – 1. 13-37 rep- Without discharge flow. For the given inlet conditions. Scheel’s equation: When a P-H diagram is available. density) can be used. This is the surge point. Nominal speeds to develop 10. For a single compression stage. and number of wheels can be estimated. 13-22. TECH BRIEF His p To find the discharge enthalpy: Hp = Eq 13-36 is his h2 = + h1 Eq 13-43 The approximate actual discharge temperature can be calcu. from product being cooled by refrigerant at higher pressures than the lowest evaporator level. locating the isentropic dis- mum allowable temperature of the unit is exceeded.000 ft for a gas when MW = 30 and 11. To calculate the total compressor horsepower: BHP = GHP + mechanical losses Eq 13-38 Centrifugal Refrigeration Compressors The mechanical losses of centrifugal compressors (including Compression ratio per wheel will vary on the order of 1. Surg- starting from Point 1 follow the line of constant entropy to the ing can cause the compressor to overheat to the point the maxi- required discharge pressure (P2). with the machines. To convert to polytropic head it will be necessary to assume Fig. See Fig. denser en route to the evaporators and/or to accept side loads boxes with an idler gear. Compressor Speed Since side-loading is the practice rather than the exception. horsepower losses due to friction in bearings. power. The polytropic head may now be deter- Bearings and seal losses can also be roughly computed from mined from Equation 13-36. equation: “Stonewall” or choked flow occurs when sonic velocity is is = h2is – h1 Eq 13-41 reached at any point in the compressor. pressed. refrigeration loads re- (No. be avoided since it can be detrimental to the compressor. the following procedure should be used. However. of wheels) (H max/wheel) N = (Nnominal) Eq 13-39 quired in MMBtu/hr.35 Eq 13-40 Two conditions associated with centrifugal compressors are surge (pumping) and stone-wall (choked flow). Fig. When this point is To convert to isentropic head. When the compressor reaches this point. for parallel shaft gearboxes. the enthalpy can be shown The repeated pressure oscillations at the surge point should as point 1 on the P-H diagram. bearings) are typically between 1 and 2% of the total 2.000 feet of head/wheel can be determined from Fig. the flow through the compressor can- not be increased further. The gas horsepower can be calculated using Mechanical Losses Eq 13-28 and Eq 13-35. sponding to the inlet flow. is lated in an analagous manner to Equations 13-29 through 13-32 The actual discharge temperature can now be obtained from but replacing (k–1)/k and is with (n–1)/n and poly respectively. the equation is: reached for a given gas. 13-34 will give a corresponding adiabatic efficiency. His = his (778 ft lb/Btu) Eq 13-42 13-29 2017 EDITION 99 WWW. the P-H diagram. GENERAL mum head per wheel. and type of driver. to calculate the maxi. 13-22 for an efficiency corre- size for conventional multistage units.NET CTSS . Flow Limits H max/wheel = 15. the speed method. it is quite common to flash refrigerant from the con- higher number for higher gearbox ratios. Fig. only to repeat the cycle.500 (MW)0.75 per wheel depending on the refrigerant and speed. heat rejection medium (air or water).CTSSNET. discharge pressure drops until it is with- resents a section of a typical P-H diagram. in the compressor’s capability. When a P-H diagram is available for the gas to be com- the gas in the discharge piping back-flows into the compressor. it is the fastest and most Mechanical losses = (GHP)0. 13-35 shows losses related to the shaft speed and casing a polytropic efficiency.000 ft when MW = 16.4 Eq 13-37 accurate method of determining compressor horsepower and discharge temperature. 13-36. After the gas horsepower has been determined by either From Fig. where the number of wheels is determined from Fig. 13-36 and Equations 13-39 and 13-40. Gearbox Due to the ease of applying external side loads to centrifugal losses are usually 2 to 3%. with the lower number for larger machines. and speed increasing gears must be added. The basic equation for estimating the speed of a centrifugal it is common to let the centrifugal compressor manufacturer compressor is: obtain the desired performance characteristics from the follow- H total ing data: evaporator temperature levels. the following equation based on molecu- lar weight (or more accurately. Also. At some point on the compressor’s operating curve there ex- ists a condition of minimum flow/maximum head where the de- P-H Diagram veloped head is insufficient to overcome the system resistance. mum differential pressure including surge thrust loads. as they eliminate oil whip or half-speed oil whirl which can lations indicate that the head and the horsepower are directly cause severe vibrations. 13-37 Wheels Required P-H Diagram Construction discharged from the compressor casing after one or more stages Interstage Cooling of compression and. a tapered land ling discharge temperatures. Substantial power economy can be gained by precooling the Tilting pad bearings have an advantage over the sleeve type gas before it enters the interstage impellers. vidual machines may or may not be cooled or have intercoolers. 13-36 FIG. each sized for good damping characteristics and high the thermal stress complication. to precool gas ahead of the first wheel. it may be advantageous to use an external cooler There are certain processes that require a controlled dis. charge end of the shaft to minimize axial loads on the thrust bearing. more commonly. is free from pad type. In some cases. It involves injecting and atomizing thrust bearing may be used but must be selected for proper a jet of water or a compatible liquid into the return channels. Intercoolers usually are mounted separately. stability. The forces transmitted from the flexible coupling and electric motor diaphragm coolers are usually connected in series. however. liquid refrigerant is frequently used for this tapered land is recommended. TECH BRIEF FIG.CTSSNET. Compressor designs with impellers arranged in one direc- rosion. Radial journal bearings are designed to handle high speeds The thermal stress within the horizontal bolted joint is the and heavy loads and incorporate force-feed lubrication. External intercoolers are commonly used as the most effec- tive means of controlling discharge temperatures. indi- about 300°F. The gas is 13-30 2017 EDITION 100 WWW. or tilting case. after being cooled. Performance calcu. Liquid injection cooling is the least costly means of control. injection into the gas. charge temperature. axial culation through cast jackets in the diffuser diaphragms. multi-lobe sleeve. The vertically split barrel-type case. double faced. purpose. and flooding present certain problems resulting tion usually have a balance drum (piston) mounted on the dis- in possible replacement of the compressor rotor. the compression of gases such as oxygen. On units where the thrust forces are low. the hazards of cor. Nevertheless. Axial thrust bearings are bidirectional. piv- Two methods of cooling within the casing are used — water oted-shoe type designed for equal thrust capacity in both direc- cooled diaphragms between successive stages and direct liquid tions and arranged for force-feed lubrication on each side. In rotation direction. straight sleeve. For example. Thrust bearings are sized for continuous operation at maxi- Diaphragm cooling systems include high-velocity water cir. At times a combination of pivoted-shoe and refrigeration units. backed babbitted shells or liners. When there tio are such that the discharge temperature of the gas exceeds are two or more compressor casings installed in series. and acetylene requires that the tem. thrust. chlorine. Journal and Thrust Bearings perature be maintained below 200°F. Injected liquid also functions as a solvent in washing the impellers free of deposits. Multistage compressors rely on intercooling whenever the inlet temperature of the gas and the required compression ra. in external heat exchangers. proportional to the absolute gas temperature at each impeller. is returned to the next stage or series of stages for further compression. Bearing sleeves or pads are fitted with replaceable steel- The gas may be cooled within the casing or. They governing design limitation in a horizontally split compressor are self-aligning.NET CTSS . erosion. and mechanical (contact) (oil or gas). 13-44 and 13-45. The sleeves are lined with babbitt or a similar non-galling material which is compatible with the prop- erties of the compressed gas and the sealing liquid. refrigerant gases. tal control system. An iron core in the stator Higher complexity is wound with coils through which is fed an electric current. 13-38 illustrates typical journal and thrust bearings Advantages generally used in horizontally and vertically split casings. there can be no one universal seal. 13-38 Journal and Thrust Bearing Assembly Basically. where it passes through the casing. etc. arrangement. Reduced bearing-related losses (near zero friction) sible for inspection and maintenance. cording to a set algorithm that corrects the deviation. The currents are adjusted ac. With the wide range of temperature. Deviations from the desired position of the Shaft Seals shaft will trigger the software in the control system to adjust Shaft seals are provided on all centrifugal compressors the current flowing through the electromagnets that determine to limit. Reduced space/weight requirements due to elimination Bearing supports are cast integral with. has the basic ele- ments similar to the liquid film seal. Increased reliability and availability ture monitoring. Bearing housings are horizontally split and readily acces. or bolted to. This fluid also per- forms the very important functions of lubricating the sleeves and removing heat from the seal area. the of the need for a bearing lube oil system case with isolated bearing chambers to prevent lubricating oil leakage into the gas system or contamination of the oil or the Reduced long term costs for maintenance and repairs gas. 13-41 through 13-46. The liquid film seal. The seal consists of two sleeves which run at close clearance to the shaft with a liquid injected between the sleeves to flow to the seal extremities. gas leakage along the shaft the strength of the magnetic field. Improved machine monitoring/diagnostic capabilities Magnetic Bearings Higher speeds possible. is introduced between the two rings at a controlled differential pressure of about 5 psi above the internal gas pressure. An active magnetic bearing compris. The sealing liquid. was also devel- oped for the severe conditions of service but requires higher oil circulation rate than the mechanical (contact) type. or seal system. Provisions are made to accommodate pick-ups and sensors for vibration and tempera.NET CTSS . Fig. It includes sensors that measure the exact position of the shaft.CTSSNET. thereby inducing a magnetic field. FIG. presenting a bar- rier to direct passage of gas along the shaft. See Fig. 13-39 for a schematic of a typical magnetic bearing The electronic part of the active magnetic bearing is the digi. This magnetic field produces Requires electrical power the forces that support the compressor shaft. Limitations es two main components — a mechanical part and an electronic part. TECH BRIEF Fig. The mechanical (contact) seal can be applied to most gases. 13-31 2017 EDITION 101 WWW. the designs of seals available are: labyrinth (gas). A mechanical gas seal uses the process gas as working fluid to eliminate the seal oil system. to handle all applica- tions. liquid film (oil). and operating conditions encountered by compressors. The mechanical parts of the bearing are similar to an elec. or completely eliminate. but finds its widest use on clean. The seal oper- ates with oil pressure 35 to 50 psi above internal gas pressure as opposed to 5 psi in the liquid film seal. heavier hydrocarbon gases. 13-40. See Figs. speed. Magnetic bearings are a relatively new development that are gaining in popularity. Magnetic bearings are available in radial and axial/thrust designs. pressure. A mechanical (contact) seal. usually a lubricating oil. The significant difference is that clearances in this seal are reduced to zero. restrictive ring (oil or gas). Figs. Generally physically larger than “conventional” bearings tric motor with a rotor and stator. CTSSNET. TECH BRIEF FIG. 13-39 FIG. 13-41 Single Gas Seal 13-32 2017 EDITION 102 WWW. 13-40 Active Magnetic Bearing System Mechanical (Contact) Shaft Seal FIG.NET CTSS . NET CTSS . TECH BRIEF FIG.CTSSNET. 13-42 Double Gas Seal FIG. 13-43 Tandem Gas Seal 13-33 2017 EDITION 103 WWW. 13-44 pressor frame size. This is the typ- Dry gas seals are used to prevent process gas from leaking ical occurrence with pressurized equipment prior to start-up. very low leakage can be other. 13-45 Liquid Film Shaft Seal with Cylindrical Bushing 13-34 2017 EDITION 104 WWW. This leakage is lost to vent or flare. this seal vent. the forces from the springs. Rotation. the primary seal gas is not lost. are machined into one of the rings. the other a seat. This portion of are held in contact by spring load. gas is injected between the process gas and the primary seal at a pressure nominally higher than the suction pressure. along the rotating shaft of the compressor into the environment.. Normally.CTSSNET. At this protective barrier for the dry seal. TECH BRIEF Dry Gas Seals lift-off pressure is 689 kPad (100 psid). the seal faces separate as the pressure the primary seal gas leaks across the face seal to the primary overcomes the spring force between the faces. tungsten ber.2 The start-up. this seal provides the main sealing function. 4 (four) modes of operation: the seal gas leaks into the compressor through the labyrinths No Rotation. i. During operation of the com- natural gas compression. main in contact up to lift-off speed. as long as the drop.1%) when com- No Rotation. The quantity of this recycled gas is quite small (less than 0. Silicon carbide. Case is Unpressurized: The seal faces re- face. we have two seals combined: pressor. This is the typical condition in an unpressurized seal at carbide or carbon are typical materials for the seal rings. Parting of the sure conditions. which normally occurs at 150 rpm. Each seal consists of two rings. An even smaller portion of pressure and above. Both leakage rates. Separation is caused by hydrodynamic effect due to One ring is stationary with the compressor casing. silicon nitride. Liquid Film Shaft Seal with Pumping Bushing FIG. it provides an important main in contact up to a certain pressure differential. Most of The seals see. but is recycled. yet.e. two faces is affected by the pressure differential across the seal For tandem dry gas seals. or less than. and maintain a very narrow gap between the gas on one side and approximately atmospheric pressure on the stationary and rotating face. Filtered seal seal gas is free of solids and liquids. decrease as a fraction of compressor flow with increasing com- FIG. one of them a spring loaded seal Rotation. flat faces of the seal rings form the seal. Case Is Pressurized: The seal faces re. pared to the compressor inlet flow. that during rotating conditions. Therefore. and the rotation of the shaft. Case Is Pressurized: The seal faces will When the machine is at stand-still the axially moveable seal maintain an equilibrium gap depending on the speed and pres- ring is pressed on the other ring by the springs. are The primary face seal is exposed to the high-pressure seal in equilibrium. which are most commonly used in faces. Case is Unpressurized: The seal faces at the shaft into the compressor suction flow. Grooves. while the fact that there is no mechanical contact the compressor suction pressure. and the aerodynamic force created by the grooves due to gas flowing through the seal. in general. Seal leakage is the same as. By taking the full pressure between the rings avoids any seal deterioration. while the seal gas pressure is held slightly higher than maintained. flow through the labyrinth and through the face seal.NET CTSS . measuring a few microns in depth. the other the groove configuration in the face of the rotating seal mem- rotates with the shaft. For transmission service. filters.) piped and mounted on a Compared with oil seal systems. A typical dry gas seal system is designed to: seal compressors. dry gas to avoid Provide clean air or nitrogen to the separation seals. provide clean nitrogen to the intermediate Lubrication and Seal-oil Systems labyrinth when needed . usually an oil. On all centrifugal compressors that have force-feed lubricat- Dry gas seals need to be protected from lube oil migrating ed bearings. control valves. Pressurized holds of longer time are possible. may be injected between the secondary seal seal units have a 127 mm (5 in. In order to protect the tem eliminates the addition of oil to the gas in the pipeline. And disadvantages: Monitor the leakage past the primary dry seal and alarm The cost of dry seals is higher in comparison to oil seals. In service Combined Seal-Oil and Lube-Oil System involving heavily contaminated gases. having approximate viscosities of 150 Saybolt Universal Seconds (SUS) at 100°F and 43 SUS at 210°F. into lube oil tanks. it eliminates sour gas carryover should never be allowed to exceed the primary vent pressure. This or mechanical (contact) seals are used. This gas also requires the same dry seal vent connections have a 34. lubrication and seal-oil sys- tems may be furnished as combined into one system. Degassing flues/tank connections on wet gas like nitrogen. makes it much easier to capture and run leakage gas into a flare system. The compressor manufacturer normally supplies both sys- tems in order to have overall unit responsibility. The flow past the outer sleeve passes through an atmospheric drain system and is returned to the reservoir. The seal gas is usually process gas that has been filtered.) of water column limit. Provide clean and dry seal gas to the face of the dry seal to prevent contamination and early failure of the seal. or as one lubrication system having booster pumps to increase the pres- FIG. This cleanliness as the primary seal gas. It operates at near zero pressure-differ. a dry seal sys- ential during normal running conditions. and conditioned in the dry gas seal system. contaminating the seals. It is similar to the primary seal and becomes active when est in compressors with dry seals is that there is no process the primary seal fails. As environmental limits become stricter. the elements (oil reservoir. The lubrication system may supply oil to both compressor and driver bearings (including gear). filtered process gas to the ties is easier to limit and is less than buffer gas flows on wet seals. the secondary vent pressure wellhead or field gas service.5 kPag (5 psig) limit. The dry gas seal system does not require external power source . Pressurized Hold. it will be in- Some tandem dry seals also have an intermediate labyrinth creasingly advantageous to leave the compressor pressurized seal located between the primary and secondary seals . TECH BRIEF The secondary face seal acts as a backup to the primary face Gas/Oil Interface. a lubrication oil system is required. a pressurized seal-oil is accomplished by a separation seal (often referred to as buf. usually an inert Degassing. pressure gauges. and hydraulic control system. etc. a degassing tank may be installed in the seal oil trap return line to remove the oil-entrained gas prior to return of the seal oil to the common oil reservoir. couplings (if continuously lubricated). In addition to all the elements of a common pressurized lu- brication system. function of this intermediate labyrinth is to facilitate the use of a secondary seal gas. The relatively low flow through the inner sleeve is collected in a drain trap or continuous drainer and may be returned to the reservoir or 13-35 2017 EDITION 105 WWW. The seal gas flow to the dry seal cavi- system is set up to provide clean. A single lubricant shall be used in all system equipment. separate lube-oil and with External Sweet Buffer Gas seal-oil systems should be used. The dry gas seal Seal Gas Quantity. pumps with drivers. 13-46 sure of only the seal oil to the required sealing level. When oil-film from the bearings of the compressor to the dry gas seals. fer seal). trip and throttle valve. Optionally. usually air or nitrogen to avoid lube oil migration into the dry Each system is designed for continuous operation with all gas seal. Secondary seal gas. while and the intermediate labyrinth. coolers. Depending on the application. This separation seal uses separation (or buffer) gas. gas/lube oil interface. One of the main reasons for the inter- seal. The parasitic power requirement to compress seal gas is less with a dry gas seal system. and lube oil tank explosive It is not necessary to inject seal gas ahead of the secondary seal mixture levels. as well as turbine governor. or shutdown if abnormal conditions exist. the seal oil system requires a collection system for the oil. The dry seal cavities must have clean.NET CTSS . as primary seal gas that leaks through the primary seal has already been filtered. Depending on the gas composition. oil degradation. The instead of blowing to vent at every shutdown. system must be provided. For secondary face seal from failure. dry gas seal systems have flat steel fabricated base plate located adjacent to the compres- the following advantages : sor.CTSSNET. see Equations 13-23 and 13-24): FIG. In the case of a single-shaft gas turbine. 13-51 Effect of Adjustable Inlet Guide Vanes on Compressor Performance FIG. The surge tank provides seal-oil capacity for coastdown and low speed. 13-46 shows clean sweet buffer gas being injected into the center of a labyrinth seal preceding the oil film seal with seal oil supplied between the two sleeves. on the other hand. mixes with the bearing lube oil drain Centrifugal compressor controls can vary from the very ba- flow. and gas-expander turbines. seal-oil design may call for buffer gas injection to form a barrier and its high speed permits the compressor to be directly con- between the compressed gas and the seal oil. A motor drive pres- with a seal-oil system which incorporates an overhead surge ents limitations in operation of the compressor due to constant tank. rected by introduction of a speed increasing gear.and seal-oil reservoir. depending upon the degree and type of contamination Drivers — Centrifugal compressors can be driven by a wide which occurred while it was in contact with the internal gas. 13-48 Volume Control at Variable Speed FIG. the more control of the compressor capacity or discharge pressure. gas combustion turbines. The constant speed restriction is minimized by of the machine and blowdown of the gas present in case of a suction or discharge throttling. Fig. and returns to the common lube. Pressure Control at Variable Speed The most efficient way to match the compressor characteris- tic to the required output is to change speed in accordance with the fan laws (affinity laws. The driver characteristics. process response. Part of the seal oil flows across the inner sleeve and mixes with buffer gas and then CONTROL SYSTEMS drains into the seal oil trap.NET CTSS . 13-50 Volume Control at Constant Speed FIG. 13-47 be selected. TECH BRIEF discarded. Compressors using only liquid film seals should be provided Each driver has its own design parameters. has variable speed capability that allows amounts of contaminants are present in the process gas. A steam tur- In combined seal-oil and lube-oil systems when large bine. The low speed restriction is cor- compressor shutdown. the power output is limited at a reduced speed. variety of prime movers including electric motors. sic manual recycle control to elaborate ratio controllers. steam tur- bines.CTSSNET. nected to the driver. 13-49 Pressure Control at Constant Speed 13-36 2017 EDITION 106 WWW. The other part of the seal oil flows across the outer sleeve. and compressor oper- ating range must be determined before the right controls can FIG. machine. The vanes are built into the inlet of increase in process pressure above the set-point value will the 1st stage. and thus requires a White. 13-51 illustrates the effect of such control at vari- ous vane positions. surement. the flow transmitter (FT) senses the process flow. and suc- of the gas is reduced. This can be matched to the compressor head-capacity curve. ies the turbine-governor speed setting within a predetermined range. Adjustable Inlet Guide Vanes — The use of adjustable inlet guide vanes is the most efficient method of controlling a As the load decreases. the density flow from pressure differentials over a flow element. 13-50. the economics of inlet guide vanes sends it to the flow controller (FC). One of the complications is. TECH BRIEF The final element is a suction throttle valve (STV) that re- N1 Q1 H1 Eq 13-44 = = duces the flow of gas into the compressor.NET CTSS . Volume Control at Constant Speed nor on the turbine or. This cylinder is operated by a servo-valve (SRV) that re- sends a modified signal to the final control element. the linkage mechanism either automatically or manually. If the pro- 13-49). tional to the process pressure and sends it to the pressure control- ler (PC). the speed adjustment can be made automatically by a pneumatic or electric controller that The control scheme for this arrangement is shown in Fig.2006) a surge limit line can be defined that is invariant to changes in gas composition. must be considered because of their higher initial cost. However.CTSSNET. cess discharge pressure. maintaining the desired system discharge pressure. 13-47). or succeeding stages. 13-49 has the pressure sig- nal sensed and amplified in a similar manner as described in A key issue in surge control is the accuracy of the flow mea- the scheme for variable speed control (Fig.e. and Prior to control selection. 13-47 senses the pro- mitter signal and sends a modified signal to the final element. higher total head if the discharge pressure remains constant. the control system sensors measure the gas An increase in flow over set point would cause a signal to reach flow through the compressor and the head it generates. Throttling the suction results in a slightly lower suction ing point of the compressor to move away from surge ( Kurz and pressure than the machine is designed for. the discharge pressure will rise. In points on the head/capacity curve. requires the knowledge of the gas composition. alternatively. pressure and temperatures at suc- tem flow. by normalizing the flow and the head appropriately (White and Pressure Control at Constant Speed Kurz. Fig. The guide vanes are adjusted by means of a positioning cylin- The pressure controller amplifies the transmitter signal and der. Pressure Control at Variable Speed The flow transmitter (FT) senses the process flow using an orifice or venturi as the primary flow element (FE). con- verts the signal to a signal proportional to the process flow. In throttling the inlet. i. It is therefore recommended to use properly installed 13-37 2017 EDITION 107 WWW. tems. that the calculation of head and higher head at reduced flow. In general. many applications. If the nature of the process requires constant volume de. An constant speed compressor. the speed can be controlled manually by an operator adjusting the speed gover. then the arrangement shown in Fig. Here. To de- the governor and reduce the speed to maintain the desired sys. With such drivers. a recycle suction throttling device such as butterfly valve or inlet guide valve in a recycle line is opened.. This var- gree of closing of the guide vanes to decrease flow. 13-52). N2 Q2 H1 A process pressure increase over a set value would cause a One of the principal advantages of using steam or gas tur- signal to reach the suction throttle valve (STV) and would par- bines as drivers for compressors is that they are well suited to tially close the valve in order to reduce the inlet pressure. Integral (reset) and rate correction factors may be needed. The vanes adjust the capacity with a minimum of efficiency Volume Control at Variable Speed loss and increase the stable operating range at design pressure. resulting in a matching of the required tion and discharge pressures and temperatures (as described weight flow to the compressor inlet-volume capabilities at other earlier). variable-speed operation. on system requirements the controller may require additional correction factors called integral (reset) and rate. and requirement for frequent adjust- The flow controller amplifies the transmitter signal and ment. Depending ceives a signal from the flow controller. an increase in flow above the set point causes a signal to reach the final element. sends a modified signal to the final element. compressor with the predicted surge line (Fig. 2004). complex mechanism. 13-48 would be impeller which reduces the head-capacity characteristics of the used. tion and discharge are measured. which is accomplished Surge Control systems are by nature surge avoidance sys- by a mechanism that varies the turbine-governor speed setting. converts The control system operates as follows: this to a signal that is proportional. and can be controlled through cause the signal to reach the governor and reduce the speed. which will result in the required de- The final element in this case is speed control. termine compressor head. The control system shown in Fig. This allows the actual operat- vanes. maintenance. It converts this signal to a signal propor- Reset and derivative controller actions may be required. The flow controller amplifies the trans- The pressure transmitter (PT) in Fig. Anti-surge Control The final element is speed control. The knowledge of head and flow allows the comparison of the present operating point of the When using electric motors as constant speed drivers (Fig. the centrifugal compressor is normally controlled by a cess forces the compressor to approach the surge line. and sends this signal to the flow controller (FC). This is accomplished by pre-rotation of the gas entering the livered. the gas composition can change. The final element is the compressor guide-vane mechanism. changes the speed in response to a pressure or flow signal. Here. cycle valve smooth and without upset to the process. electricity supply. To that end. ations. and ultimately reach the discharge pressure nec- margin flow. When the cally kept at a fixed position to allow the compressor to operating point reflects more flow than the required protection start. 13-38 2017 EDITION 108 WWW. very different. low reduction of the process flow to zero while keeping the compressor on line. Using the pressure differential 4. or “error. It must be understood that the anti-surge control system ence. The piping system is the dominant factor in the overall erating point using the pressure. changes in ca- been used successfully.NET CTSS . This will also make the transition 2. The single valve surge avoidance system. TECH BRIEF FIG. sce- When opened. A control algorithm (P+I+D) acts upon this differ. temperature and flow data system response. the compression units have to be shut down in- stantly. difference between the operating point and the surge limit is the control error. range. Unit Startup: In this condition the recycle valve is typi- the compressor is prevented from increasing further. An appropriate control algorithm: It must ensure surge from fully closed recycle valve to an increasingly open re- avoidance without unnecessarily upsetting the process. 13-52 Typical Compressor Map (Variable Speed) Courtesy of Solar Turbines Incorporated orifices or venture flow meters. Recycle valve correctly selected for the system volumes: to-noise ratio. a portion of the gas from the discharge side of the narios: compressor is routed back to the suction side and head across 1. It must be analyzed and understood. 5. A surge avoidance system determines the compressor op. 3. It is not recommended to use pitot type pacity. They must be capable of tive method. the surge control valve moves toward the closed essary to open the check valve. process. and accuracy. A precise surge limit model: It must predict the surge centrifugal compressor can stay on-line even at a no-flow limit over the applicable range of gas conditions and condition. provided by the instrumentation. must be designed to operate under three. Process Control: with a properly sized recycle valve. The system compares the Large volumes will preclude the implementation of a compressor operating point to the compressor’s surge limit. with a low signal. Properly installed ultrasonic flow meters have also large and rapid. The right instrumentation instruments must be selected 3. the fuel supply. There are 5 essentials for successful surge avoidance: 2.CTSSNET. a 1. or elbow flow meters for flow measurements in surge control systems because the signals tend to be weak.” to develop a control signal to the recycle valve. valves must fit the compressor. as well a small and slow. Emergency shutdown: During certain emergency situ- to meet the requirements for speed. The valve must be fast enough and large enough to en- sure the surge limit is not reached during a shutdown. Recycle valve correctly selected for the compressor: the between compressor flange and impeller eye is also a very effec. and feed gas in to the position and the compressor resumes normal operation. Well-designed surge control systems can al- characteristics. pressure on the discharge side of the compressor. such as a steam or gas turbine. erence the discussion of torsional analysis in the Reciprocating ing or reducing gear unit is furnished between the compressor Compressor section for additional information. TECH BRIEF or steam supply to the driver are cut instantly. the recycle valve has to open quickly to relieve the tor and/or analyzer. The usual method for surge avoidance (“anti-surge control”) consists of a recycle loop that can be activated by a fast acting Fig. Output signal from each transducer is small A typical anti-surge control system is shown in Fig. to bearing housing. Vibration transducers fall into three categories: displace- In some instances it is necessary to use multiple loops or ment probe. 13-53 and. FIG. its inertia. and vibration moni- sor. and API Standard 678. also consider monitoring vibration at the gear shaft situation. Accelerometer- This control system may be provided to monitor the driver Based Vibration Monitoring System. Because the speed reduction The main system components are: variation transducer(s). When a speed increas. the compressor approaches its surge limit. velocity pick-up. The analysis is not as complex as for that required for ble machinery failure through alarm and/or shutdown devices.NET CTSS . that usually runs at are not as great as those within reciprocating compressors. Typical a compressor may lose 30% of its speed in the first second. The displacement probe is most commonly used for equip- lows the necessary accuracy in flow control for process control. therefore. and accelerometer. signal amplifier(s) with d-c power supply. as it can measure shaft vibration relative as well as the fast reaction for an emergency shutdown. behavior at the shaft bearings for detection of excessive lateral Torsional analysis is also recommended for centrifugal com- vibration and axial movement and for protection against possi. pressors. and the fact that the energy sources the driver. ment with high value. 13-54 shows a vibration severity chart for use as a guide valve (“anti-surge valve”) when the control system detects that in judging vibration levels as a warning of impending trouble. also reduces the head-making capability of the compres. the compressor will decelerate rapidly under bearings. multiple valves in parallel to accomplish a system that both al. it must be amplified before being transmitted to a vibration monitor or analyzer.CTSSNET. Ref- the same high speed as the compressor. For more information on vibration monitoring systems. 13-53 Example Anti-Surge Control System courtesy of Solar Turbines Incorporated ENGINE COMPRESSOR W SV AFTERCOOLER DV TT FT PT PT TT LV SCRUBBER ANTI-SURGE SV = SUCTION VALVE CONTROLLER LV = LOADING VALVE LIMIT VV = VENT VALVE SWITCH DV = DISCHARGE VALVE 4-20mA TT = TEMPERATURE TRANSMITTER POSITION FT = FLOW TRANSMITTER TRANSMITTER PT = PRESSURE TRANSMITTER SOLENOID 4-20mA ENABLE 24VDC FAIL OPEN ANTI-SURGE CONTROL VALVE 13-39 2017 EDITION 109 WWW. reciprocating compressors due to the limited operating envelop The system may protect not only the compressor but also of centrifugal compressor. see API Standard 670. In this and driver. Noncontacting Vibration and Axial Position Vibration Control System Monitoring System. It may not accurately depict peak response frequencies. The critical speed map is used extensively because it en- ables determination of bearing or support stiffness by correlat- ing test-stand data.NET CTSS . Equally important is to analyze the dynamic behavior of the compressor for sudden changes in load due to start-up.CTSSNET. The intersec- tions of the bearing stiffness curve and the critical speed lines represent the undamped critical speeds. bearing support stiffness and damping are considered together with synchronous vibration behavior for a selected imbalance distri- bution. critical speed. The result is a map Vibration Severity Chart1 like that shown in Fig.mils Rotational Speed . 13-55 the rotor behavior at a particular station or axial location such Undamped Critical Speed Map FIG. A computer is normally required to solve the resulting differential equations. 13-56. the critical speeds for a given rotor geometry are calculated for a range of FIG. First. the use of this map is very limited because it is based on a simplified undamped. Critical Speed Map down. A critical speed map is one of various methods used to pre- dict the operational behavior of the rotor. TECH BRIEF OPERATIONAL CONSIDERATIONS Successful rotor design is the result of accurate calculation of critical speeds. 13-56 Unbalanced Response Plot Vibration Levels . circular synchronous analysis with no cross-coupled or unbalance effects. The plot of results of a typical unbalance response study is shown in Fig. The intersection points generally indicate margins between the criticals and the oper- ating speed range. flexibility. and cross-plotted on the critical speed map. or loss of power supply. The map depicts the values of the undamped critical speeds and how they are influenced by bearing stiffness. 13-54 assumed bearing-support stiffness values. The bearing stiffness character- istics are determined from the geometry of the bearing support system. Satisfactory results depend on the accu- rate input of bearing stiffness and damping parameters. Each curve represents FIG. A critical speed occurs at a condition when the Rotor Dynamics and Critical Speeds rotor speed corresponds to a resonant frequency of the rotor- bearing support system. 13-55. Under no circumstances should the The demand for smooth-running turbomachinery requires compressor be allowed to run at a critical speed for a prolonged careful analysis of rotor dynamics taking into account bearing length of time as the rotor vibrations amplified by this condition performance. can cause machinery failure. shut. However.RPM Courtesy of Solar Turbines International 13-40 2017 EDITION 110 WWW. and rotor response. Unbalance Response Analysis This method predicts rotor-bearing system resonances to greater accuracy than the critical speed map. Here. It is a good trending tool showing a machine’s basic dynamic characteristics. Several runs are usually made with various amounts and locations of unbalance. c. If the trouble cannot be traced to adverse gas flow conditions or liquid “slugs” present in the system. Driver Power 2. °F The unbalance-response results predict the actual ampli. at intermediate inlet flange if side stream is added or This is expressed in mils of vibration amplitude per ounce-inch liquid drop-out occurs in the interstage cooler. 2. TECH BRIEF as those corresponding to the midspan. to measure its performance. lube oil console. Lack of proper care of any machine is bound to result in a suc- cession of minor troubles eventually leading to a major break- down. 13-57 Operational troubles occurring in service may be due to a Rotor Response Plot variety of causes. Compressor speed. Inlet conditions (at the compressor inlet flange): piping and all tubing and wiring. Guide vane setting speed for rigid shaft rotor systems. Control setting (depending on the type of compressor ranges. Twenty (20) percent over the maximum continuous b. b. See Figures 13-59 and 13-60. Integrally geared compressors offer the following potential advantages: low power consumption due to different impeller speeds. mass flow. Pressure. °F Axial compressors are basically high-flow. INTEGRALLY GEARED COMPRESSORS An integrally geared compressor utilizes a central driven bull gear with typically 2–4 high speed pinion-driven shafts. Intermediate conditions (if applicable) hangs. std flow) and gas composition tudes that permit calculations of the unbalance sensitivity. bearings. 5. Temperature. low-pressure ma- chines. it is often desirable multiservice capability. Flow (scfm. One or two impellers can be mounted on each pinion shaft. Fig. 13-57 shows limits of placement of critical speeds a. determine driver power output indepen- speed for flexible shaft rotor system. Discharge Conditions (at the compressor discharge The peaks of the response curves represent the critical speed flange): locations. Once the compressor has been installed. Careless operation and maintenance needs little comment. b. Temperature. Pressure.NET CTSS . or lb/min) Design requirements of integrally geared compressors are covered by API Standard 617. or gram-inch of unbalance. Flow (actual. Centrifugal Compressors for General Refinery Services. b. 3. psia AXIAL COMPRESSORS d. process coolers. tailored aerodynamics and optimized auxiliaries. in contrast to the lower flow. psia No rotor can be perfectly balanced and. process 1. Temperature at intermediate inlet flange. high-pressure centrifugal compressors (the axial compressors used in gas turbines are of- 13-41 2017 EDITION 111 WWW. and the separation margin of encroachment (SM) from controls) all lateral modes is required to be at least: a. dently of compressor power measurement Troubleshooting FIG. Fifteen (15) percent below any operating speed and twenty (20) percent above the maximum continuous a. Pressure at intermediate nozzles. a. A package includes the compressor. Fig. it must be relatively insensitive to reasonable amounts of unbalance. This forms a compact unit for the mul- tistage compression of a wide range of gases. The following parameters needs to be determined: packaged designs available. oF Critical speeds should not encroach upon operating speed 4.CTSSNET. therefore. If available. acfm. a. and over. Gas composition c. rpm 1. 13-58 can be used as a guide for troubleshooting frequently encountered problems. wide operating range and improved part-load efficien- cies due to adjustable inlet guide vanes at the first or at Field Performance all compression stages. psia as specified in the API Standard 617. To localize Low Lube Oil vibration. indicate whether driver or 11. 3. Lube oil temperature leav. Poor conditions of lube oil or dirt Low Discharge High Bearing Oil Tem- 3. Although the axial compressor requires A cross-sectional view of a typical axial flow compressor is more stages. 13-42 2017 EDITION 112 WWW. 11. Deposit buildup on rotor or dif. compressor. As can be seen in Fig. machinery (sympathetic vibra- 1. 6. tion. tube-sheet. Warped shaft caused by uneven 5. Note: heating or cooling. 4. Axial rotor to the gas in order to generate an increase in gas pressure. Wiped bearing. Piping strain. Loose or broken bolting. Compressor Surge piping or improper valve posi. shaft due to severe rubbing. 8. 5. 6. Worn or damaged coupling. Loose wheel(s) (rare case). 2. 1. 8. the diametral size of an axial is typically much shown in Fig. typical upper end of the flow range at 400. is the gle casing. Defective grouting. 1. Compressor not up to speed. Water in lube oil.CTSSNET. Operating at or near critical 9. be permitted to exceed 6. 13. iary oil pumps. 1. or a combination of both. Bearing lube oil orifices missing 16. tion). 9. Loose or broken foundation bolts. 10. Failure of both main and auxil. In general. Low inlet pressure. or gummy deposits in bearings. Leaks in the oil system. to obstruction in the discharge 8. lubricated type is used). Leak in lube oil cooler tubes or Shaft Misalignment 3. 4. Uneven build-up of deposits on Pressure running (if main oil pump is alone. Inadequate or restricted flow of 2. as many stages to achieve a given pressure ratio as would be re- quired by a centrifugal. Shaft misalignment. 3. 180°F. Fouled lube oil cooler. Low level in oil reservoir. mitted from the coupled 9. These stationary vanes. 12.000 cfm. 2. Leak in oil pump suction piping. 15. temperature. 2. Rough journal surface. Unbalanced rotor or warped 7. as its name implies. Water In Lube Oil 2. Damaged rotor or bent shaft. 13-58 Probable Causes of Centrifugal Compressor Trouble Trouble Probable Cause(s) Trouble Probable Cause(s) 1. can be fixed or vari- pressure rise per stage. Oil pump suction plugged. Excessive bearing clearance. compressors are generally smaller and significantly more effi. Change in system resistance due 7. without the auxiliary oil pump pling and operate driver 10. 1. Condensation in oil reservior. rotating blades operating in series on a single rotor in a sin- istic feature of an axial compressor.000 cfm with a based on efficiency and size. Excessive vibration. shaft-driven). causing unbalance. Relief valve improperly set or driven machine is causing vibration. The axial compressor’s capital cost Performance Capabilities — The volume range of the is usually higher than that of a centrifugal but may be justified axial compressor starts at approximately 30. Incorrect pressure control valve 14. An axial flow com. Liquid “slugs” striking wheels. Clogged oil strainers or filters. fusers restricting gas flow. Leak in discharge piping. Warped bedplate. 13-61. speed. lower than for a centrifugal. or stators. Inadequate flow through the ing bearings should never 5. Excessive vibration of adjacent or plugged. Vibration may be trans. TECH BRIEF ten designed for higher pressures and compression ratios). The character. Dry coupling (if continuously 3. This should help to rotor wheels. the and stationary blades to transfer the input energy from the flow range for the axial overlaps the higher end of the range for FIG. 2. Excessive Vibration 7. setting or operation. 4. 13-3. compressor. Excessive system demand from Note: lube oil cooler. it takes approximately twice able angle. driver. Improperly assembled parts. disconnect cou. Excessive compressor inlet lube oil to bearings. Inadequate cooling water flow to 5. 5. Operating in surge region.NET CTSS . stuck open. Pressure perature 4. 2. A multistage axial flow compressor has two or more rows of cient than comparable centrifugal compressors. The casing contains the stationary vanes (stators) axial direction of flow through the machine. for directing the air or gas to each succeeding row of rotating pressor requires more stages than a centrifugal due to the lower blades. compressor or 1. Warped foundation. Much larger The axial compressor utilizes alternating rows of rotating axial machines have been built. Piping strain. High oil viscosity. 3. Faulty lube oil pressure gauge 4. Operation at a low speed machine. or switch. The operational characteristic of the turbo gear unit shall remain unaffected. Voith Turbo BHS Getriebe GmbH creases the efficiency of your Voith or retrofit. See for oil requirement in combination with yourself if your application or project is high reliability: BHS AeroMaXX. It’s worth talking to us: The BHS AeroMaXX technology in. Up to 30 % more Efficiency Higher gear unit efficiency and lower non-Voith gear unit up to 30 %.com/bhsaeromaxx.NET CTSS . The purely passive-mechanical soluti- on can be installed in a new gear unit or provided as a simple retrofit. suitable with our suitability indicator at
[email protected] Upgrade for Turbo Gears.voith.com 2017 EDITION 113 WWW.CTSSNET. even on-site within a short period of time. at the higher end flows. the physical size of the axial is far smaller than the ered by API Standard 617. cesses that cannot tolerate contamination of the compressed besides aircraft jet engine use. comparable centrifugal machine that would be required. Typical dis- Rotary screw compressors are available in oil-free (dry) or charge pressures are usually less than approximately 100 psig. and can reach 90% (adiabatic). Fig. a thorough evaluation of axial vs centrifugal for larger machines. ing the two screw profiles as one screw drives the other. The injected lubricant provides a layer separat- Horsepower requirements for axial flow compressors in pro. Efficiencies for axial compressors are high.000 HP for single injected machines generally have higher efficiencies and utilize casing units. especially axial’s flow range. is in gas turbines. applications. the axial air compressor is often designed to oper- Oil-injected screw compressors are generally supplied without ate at final discharge pressures of up to around 500 psig. the axial compressor often becomes the obvious choice. Oil-free compressors typically use shaft- They are very commonly utilized in refineries and other indus- mounted gears to keep the two rotors in proper mesh without trial processes for high volume. The most common application of axial compressors. 13-62 shows a cutaway cross-section of a typical ro- sors are always manufactured as multistage machines. At the lower end of the ments. In gas turbine gas or where lubricating oil would be contaminated by the gas. TECH BRIEF typical centrifugal compressor coverage. must normally be made.NET CTSS . depending on flow and pressure ratio require- FIG. fall into the category of rotary positive displacement compres- Because of the low pressure rise per stage. sors. also known as helical lobe compressors.CTSSNET.000 to 65. compressors are in general low pressure machines. As stated Design requirements for centrifugal compressors are cov- previously. 13-59 Typical Integrally Geared Compressor Showing Nomenclature of Key Parts 13-43 2017 EDITION 114 WWW. timing gears. and the efficiency of the axial is usually better. low pressure air supply appli- contact. the axial is often a better match for the drivers Screw compressors. However. In many high flow SCREW COMPRESSORS applications. oil-injected designs. axial compres. that would typically be selected. Axial tary screw compressor. Applications for oil-free compressors include all pro- cations. Oil- cess service typically range from 3. n Result: Elliott refrigeration compressors and unmatched experience have been central to successful LNG projects for decades. n Challenge: Select a compression partner to ensure years of efficient. From the first commercial LNG baseload plants to today’s mega-plants in Russia. the Middle East and Asia. Elliott’s proven experience with different processes and drivers is supported by manufacturing centers in the US and Japan. and a global network of service centers. www.elliott-turbo. LNG producers have chosen Elliott for efficient.n Customer: LNG producers throughout the world. reliable production.com . reliable compressors and matchless expertise. Who will you turn to? C O M P R E S S O R S n T U R B I N E S n G L O B A L S E R V I C E The world turns to Elliott. They turned to Elliott for leadership in LNG compression. 13-60 Typical Integrally Geared Compressor Arrangement Showing Nomenclature of Key Elements FIG.CTSSNET. TECH BRIEF FIG.NET CTSS . 13-61 Typical Axial Compressor Showing Nomenclature of Key Parts 13-44 2017 EDITION 116 WWW. com 2017 EDITION 117 WWW.NET CTSS . constantly evolving expertise and in-depth knowledge of gases.siadmi. because they are the result of almost a century of experience and are a perfect combination of innovation. SIAD Macchine Impianti. Compressors. Air Separation Units. It is our know-how that goes beyond the latest technology! For further information: siadmi_compr@siad. beyond technology All our compressors have a distinctive characteristic.CTSSNET.eu SIAD Macchine Impianti. www. Made in Italy Welding and Services. the volume diminishes and pres. closes. The compression process is intake aperture and flows into the heli. 13-45 2017 EDITION 118 WWW. cal grooves of the rotors which are open. rotors proceeds. the final pressure attained. the air intake aperture completed. the discharge commences. 13-63 Working Phases of Rotary Screw Compressor (a) (b) (c) Suction intake. sure rises. TECH BRIEF FIG.CTSSNET. Gas enters through the Compression process .NET CTSS . As rotation of the Discharge . 13-62 Rotary Screw Compressor FIG. .. storage Power plants Compressor Services Compressor Parts Installation & Commissioning Maintenance Overhauling Engineering Compressor valves & reconditioning Spare Parts Management Training Engineering & consultancy Capacity control systems Individual products & special applications BORSIG ZM Compression GmbH www.Integrally Geared Compressors Centrifugal Compressors for Process Gases for Process Gases Horizontal and vertical design with up to a maximum of 6 axes. Discharge pressure: ...000 m³/h Discharge pressure: . 16.de .borsig.API 618 ..borsig. 150 bar Capacity/flow: .. Oil and gas industries machine protection and condition monitoring for Refinery technology reciprocating and centrifugal compressor units Natural gas ... 1.000 kW Typical fields of application: BORSIG BlueLine Chemical and petrochemical industries Crude oil recovery Combines control system.Reciprocating API 617 . 300.000 bara Power: . Fax: +49 (0) 3764 / 5390-5092 E-mail:
[email protected] m³/h Power: . emergency shutdown..000 kW Capacity/flow: .de/zm Seiferitzer Allee 26. 08393 Meerane / Germany Phone: +49 (0) 3764 / 5390-0.. 25. transport. 115. Gaskets (7).000 acfm. Cylinder and Housing (5). jet pumps have been successfully used in the following can be shortened. the effective length of the rotors duction. tolerance to Rotor and Shaft (1). 13-63 provides a sequence of drawings showing the compression Jet Pump Technology1. In particular. de-bottlenecking compressors. screw Rotary-sliding vane compressors (Fig. the process service. 13-6 Operating Principle of Sliding Vane Compressor 13-46 2017 EDITION 120 WWW. 13-6 fluid movers as compared to a compressor or multi-phase com- Sliding Vane Compressor and Principal Components: pressor but their attractiveness is their low cost.NET CTSS . A standard design should have primary separation and Design requirements for screw compressors are covered un- secondary separation using coalescing filters. preventing flar- percent down to 10 percent of full compressor capacity.2 process. Fig. normally under of the compressor into the space created by the unmeshing of 150 HP. preventing HP wells from imposing back pressure on LP wells. ing of LP gas (vapor recovery). Most applications of rotary-sliding vane compressors trapped gas out while a new charge is drawn into the suction in oil and gas service involve fairly small units. The ro- tor is fitted with blades that are free to move radially in and Gas compression is achieved by the intermeshing of the ro. Continued rotation then moves the remaining 1800 cfm. are simple devices that use a high pressure (HP) fluid to regulating device known as a slide valve. eductors or ejec- motors. Sliding vane compressors are available in single. Bearings (2). presence of some liquids in gas and their simplicity compared Mechanical Seals (4). and is and gas continues to flow into the compressor until the entire in. rotary COMPRESSORS screw compressors are now compressing a large number of gases in the hydrocarbon processing industries. Each unit has a rotor and gas gathering applications. with capacity control normally achieved via an internal tors. Power is applied to the male rotor cylinder wall by centrifugal force. a new pair of lobes as the compression cycle begins again.CTSSNET. jet pumps are less efficient FIG. Typical single-stage capacities are ranging reduced as it increases in pressure. Oil As the rotor continues to turn. ROTARY-SLIDING VANE Although originally intended for air compression. Further rotation uncovers through 3200 cfm and 50 psig. and de-liquefication of liquid-loaded wells. In general. TECH BRIEF the oil for cooling as well. Depending upon der API Standard 619.and multi- rection of the discharge port. separation is critical and often the cause for operating prob- lems. By moving the slide in increase the pressure of a lower pressure fluid (LP). Coupling (9) FIG. Screw compressors are usually driven by constant speed Jet pumps. eccentrically mounted inside a water jacketed cylinder. The volume of gas is progressively stage configurations. These blades are forced against the tating male and female rotors. out of longitudinal slots. Typical adiabatic efficiency will be in the range If an oil-injected compressor is used. In gas pro- a direction parallel to the rotors. Heads and Covers (6). terlobe space is filled. recovered via a downstream scrubber and recycled to the inlet. This provides smooth control of flow from 100 applications: boosting production of gas wells. includ- gaining in popularity in the gas production business in booster ing vapor recovery and vacuum service. Blades (3). which allows for higher compression Rotary screw compressors in use today cover a range of suc- ratios in a single screw compressor stage. eliminating intermediate compressors. 13-64) are positive compressors are widely used in refrigeration service and are displacement machines. and how the female rotor a void is created and gas is taken in at the inlet port. Continued rotation brings a male lobe into the interlobe spacing compressing and moving the gas in the di. the oil content of the compressed vapor may need to be removed down to 100 ppb levels. gas inside these pockets is compressed as the rotor turns. tion volumes from 180 to 35. Fig. two-stage compressors deliver the discharge port and the compressed gas starts to flow out of pressures from 60 to 150 psig and flows up to approximately the compressor. They have several applications. with discharge pressures up to 750 psig. Lube Supply Line (8). 13-65 illustrates how in- and as a lobe of the male rotor starts to move out of mesh with the dividual pockets are thus formed by the blades. the intermesh space is increased is injected into the flow stream to lubricate the vanes. the downstream oil of 70 to 80%. also known as jet compressors. In vapor recovery applications. The combined stream flows through flow through the nozzle. In “typical” applications the discharge pres- sure is 1.CTSSNET. Figure 13-67 provides typical performance of a jet pump un- der a range of gas pressures and flow ratios. The resulting discharge pressure is primarily a function of the downstream production and pro- cess system. and the LP/HP mass flow ra- tio. the LP pressure can be increased from a few percent up to five fold with a single jet pump. The reduction in perfor- nozzle on the HP fluid side. increasing liquids in the LP In most gas production applications. pressure of the liquid phase. as shown in Fig 13-66. recycle mode. 13-67 HP to LP Pressure Ratios Courtesy of CALTEC. but often it is 1:1 or less. as the liquids restrict sure fluid is introduced. The high pressure gas flows through the nozzle crease of the sonic velocity of the combined stream. the produced water can be pumped up to high pressure and used to boost the LP gas pressure to gas pipeline pressures. which has significantly more mass than the gas phase. a low pressure zone is liquid at operating pressure and temperature. Other operating conditions.5 to 3 time greater than the low pressure source. Presence of liq- produced in front of the nozzle. or other facility the mixing tube to transfer momentum and energy between the separators such as a test separator or a compact separator. but to a lesser extent. a jet pump can provide a cost effective solution to increase or maintain production or boost the pressure of low The performance of gas-gas jet pumps deteriorates if there pressure (LP) processed gas. the high pressure stream can choke the flow of the jet pump due to the rapid de- source is gas. a mixing mance is a result of the additional energy required to boost the tube and a diffuser. For example in well field applications. the vapor flows into the outlet gas pipeline. such as temperature and fluid physical properties will factor into the performance of the jet pump. the high pressure source is sometimes a liquid. The primary factors governing jet pump performance are the HP/LP pressure ratio (PR). The fluid is then expanded in a diffuser where be used to separate the phases to achieve acceptable jet pump the velocity of the fluid is reduced and pressure of the system performance. may two streams. is increased. In addition. or a compressor with excess capacity or in a tion and the HP source availability. TECH BRIEF to other systems such as compressors. Gas-liquid separators. In general. uids in the HP source is also problematic. The high FIG. Limited 13-47 2017 EDITION 121 WWW. a LP fluid inlet nozzle. 13-66 pressure vapor and water stream are then separated.NET CTSS . If there is a local high available LP/HP flow ratio is dependent upon the field installa- pressure source. The FIG. at which point the low pres. As a result. and the water is recycled for General Configuration of a Jet Pump jet pump use. The primary components are a are liquids present in the LP fluid. The impact where some of the pressure (potential) energy is converted into of liquids on performance is typically minimal up to 2 volume % kinetic energy (velocity). tedious. the gas is on its dew point line. High ethane recovery requirements (i. Any specific information must come Point 3 represents the outlet of the expander. At 2. A above that affect a final process selection. the gas is 100 percent vapor. its pressure-temper. without the expander fective cooling for a given pressure drop. or constant enthalpy ranges of inlet flow and pressure conditions. The higher temperature at Point 4 results in a reduction of Selection of a turboexpander process cycle is indicated when product recovery. expansion process. easily adapted to wide varia. less than the theoretical work in the real case. 1. Additional calculations are iterative. Mechanical design of the turboexpander is the business of ature path is shown by the dashed line from point 2 to point 3. because the path to Point 4 is adiabatic without the drocarbon Dewpoint. over 30% eth- ane recovery). vapor now has its own pressure-temperature diagram..e. LNG. An example calculation of an expander operating on pure methane is provided to demonstrate the thermodynamic prin- Fig. That is. the expander lowers the bulk stream tempera- There are multiple factors in addition to the ones listed ture which can result in partial liquefaction of the bulk stream. Hydrocarbon Recovery. and Nitro. “Free” pressure drop in the gas stream. These units operate over wide point 4. of using the expander as a driver for a compressor can be seen Of the various general turbine types available. P1) to the expander are generally set by upstream conditions. the gas enters the expander inlet separator in the order of 2% are usually deducted to calculate net power where the condensed liquid is separated from the vapor. the inlet gas is tors. Air Separation Units. The use of the expander brake compressor one or more of the following conditions exist: to boost the residue gas pressure will allow a lower expansion pressure without the use of more residue compression. 13-69. As the gas is cooled by the gas/gas exchangers and demethanizer side ex. the gas does not cool to as low a temperature as Rejection. The expander 4. If the ponent stream must be determined by trial-and-error calcula- gas is cooled.e. The trend in the gas running (therefore the brake compressor also not running). The solid line on the right is the dew point line. most new gas processing plants er than that accomplished in the expander (nearly isentropic) for ethane or propane recovery were being designed to incor. above conditions are coexistent. This is due to Note that the pressure at Point 4 is not as low as that at- the expander following an isentropic path as compared to an tained by flow through the expander (Point 3). generally a turboexpander pro- cess selection will be the best choice. inlet gas. mations for expander performance. THERMODYNAMICS 3. process for recovering ethane and heavier hydrocarbons from a natural gas stream. 13-70. more liquid is condensed until the bubble point line is reached — the solid For multicomponent streams. The solid curve represents the plant power considerations. pansion producing work and thereby cooling the gas more than provides descriptions of a number of common turboexpander the simple isenthalpic (J-T) expansion path. If the gas had been expanded without doing reaction turbine design is dominant in cryogenic turboexpander any driver work. TECH BRIEF Turboexpanders The use of turboexpanders in gas processing plants began expansion. 13-68 shows a typical low temperature turboexpander ciples of expanders. As cooling continues. Nitrogen gas doing work. represented by point 1 on both Fig. At this point. the expansion path would be from point 2 to natural gas plant applications. This is because it isenthalpic path of a JT valve. Also. In the process of producing work. reaches the dew point line. Expander and compressor performance is typically modeled using current process simula- Downstream of the gas treating facilities. and are only close approxi- cooling results in colder liquid. porate the particular advantages characteristic of an expander producing usable work and lower temperatures. MECHANICAL As the gas flows through the expander. Helium Recovery. The outlet pressure P2 from the expand- Fig. By 1970. several manufacturers. 13-68 and 13-69. process cannot restore the demethanizer overhead vapor to the boexpander. Section 16. Current turboexpander process applications include: Hy. This is called a Joule-Thomson. 13-71 gives an example calculation. At the expander inlet. Fig. Flexibility of operation (i. A turboexpander (often just referred to as ‘expander’) recovers useful work from the expansion of a gas stream. and thereby provide more ef. operates isentropically in the ideal case and produces something tion in pressure and products). the path (2) to (3) is isentropic ex- gen Refrigeration Cycles. residue gas pressure using the separate recompressor alone. by utilizing vari- 13-48 2017 EDITION 122 WWW. 13-69). NGL and LPG Recovery. In many applications the loading device for the turboex- changer. such as natural gas. the hand line on the left. 13-69 represents the pressure-temperature diagram er is often set by the desired NGL recovery and recompressor for this expander process. the path to Point 3. Compact plant layout requirement. The outlet temperature and pressure would be high- in the early sixties. 2. its temperature moves along the dotted line to point 2 pander is a centrifugal compressor. At a fixed pressure and. all of the gas is liquid. process applications for hydrocarbon recovery. This input to the driven end from the expander. the processing industry continues toward increased use of the tur. has been assumed for this example that. If two or more of the simple schematic of an expander is given in Fig. as rep- resented by the dashed curve. Shaft and bearing losses (Fig. Gas inlet conditions (t1. The importance from such supplier. the radial in Fig. liquid starts to condense when the temperature tions if one were to do them by hand. if the temperature of the gas is to the Outlet conditions for the expander processing a multi-com- right of this dew point line.CTSSNET.NET CTSS .. . These normally require gearing to reduce the expander 5. must take into account start-up. In this case. etc. best efforts at the manufacturing stage to avoid this problem. The list is by no means compre- hensive. is acceptable if it can be determined that the gas flow through rator vessel. special anti-surge instrumentation for the compressor unit. Both lubricated and non-lubricated turboexpander designs 2. An inlet screen of fine mesh is usually required the compressor is balanced with flow through the expander and for solids removal. 6. turboexpanders. They operate at very high rotating speeds 3. and shutdown con- ditions. heavy oils) will often occur here first and can be Auxiliary Systems detected by an increase in pressure drop across the screen. This uid entrainment. The expander inlet gas stream must be free of solid or liq. rotating speeds are set to op. dry. The stream must be clean. etc. cooled and filtered lube oils to the turboexpander bearings as shown on Fig. It is common practice to install a turboexpander-compressor with no 1. TECH BRIEF able inlet guide vanes. but these items require more than the normal amount The installation of a turboexpander-compressor unit also of concern in designing the installation of a turboexpander unit requires the proper design of a lube system.NET CTSS . amines. be within prescribed limits to avoid distortion of the case. 13-68 Example Expander Process 13-49 2017 EDITION 124 WWW. Other applications of option and influenced by operating economics. bearing modifications.. turboexpanders are listed below. instrumentation. Its application is normally an owner and vendor the same shaft as the expander wheel. Source of the seal gas. This to 83% for the expander and 68 to 70% for the compressor.CTSSNET. Liquids are removed in a high pressure sepa. Even though the manufacturer will exert his promise in the compressor end design and lower compressor ef. Loading of the flanges by the process piping system must speed to that required for the driven unit. operating. the power recovery are expander-pump or expander-generator drives. carbon diox- ide. sweet. Monitoring of the pressure drop across this the two will vary simultaneously. is an are available. Failures due to mechanical resonance have occurred in timize the expander efficiency. particularly during start-up. Vibration detection instrumentation is useful but not the process. Since power recovery and refrigeration effect are primary benefits of expander applications. screen is recommended. Selection of this valve and actuator type mon to similar sophisticated rotating equipment. 13-72. the expander inlet. Lubrication System — The lubrication system circulates and of sufficient pressure to meet the system requirements. This will usually result in a com. Formation of solids (ice. Normally a quick closure shutoff valve is required on and thus are subject to the design and operating cautions com. Usual efficiencies quoted for radial type units are 80 in-plant operation may uncover an undesirable resonance. The most common configuration is a turboexpander-com- pressor where the expander power is used to compress gas in 4. ficiencies. in common with other industrial rotating equipment. must be solved in conjunction with the manufacturer and may involve a redesign of the wheels. re- sulting in bearing or wheel rubbing problems. vane or Some areas requiring extra attention in the installation of diffuser redesign. the compressor wheel operates on mandatory. The principle components of the system FIG. for cryogenic operation. important consideration. but save you money on power and maintenance costs. LPG vapor. two-stage to 1800 SCFM • Working pressures to 300 PSIG • Made in the USA since 1929 Find out more at www. • Suitable for natural gas. it has only three moving parts.Simple. flare gas. bio gases. Combined with low operating speeds which minimizes wear and vibration. it is designed to not only outlast other compressors.flsmidth. and ammonia refrigeration • Carbon fiber vanes last longer than traditional blades • Variable flows with VFD and/or bypass • Single stage to 3000 SCFM.com/compressors . reliable efficient Vapor Recovery? LPG Transfer? Natural Gas Boosting? The answer is the FLSmidth® Ful-Vane™ rotary vane compressor! Built robustly for long service life. Pressure-Temperature Diagram for Expander Process Seal gas filtration is essential because of close clearances provided between the shaft and seals. A minimum seal gas temperature FIG. s1 = 1. It can be of a fan air fuel gas system. 24.0 lb lb°F At P2 = 300 psia and assuming 100% efficiency (ideal) BTU s2 = 1. twin filters. 13-69 (about 70°F) is required to prevent oil thickening. an oil cooler. a dual filter pump suction as well as to serve as a degassing drum permit- valve. Most manufactur. warmed and used as seal gas. or put back into the compressor suction end. The leaking seal gas is collected in the The lube oil cooler is an integral part of the system to reject oil reservoir.NET CTSS . electric heater (if required).80) 35 ( BTU lb = 28 ) BTU lb T2 actual –157°F Work produced = ( 28 BTU lb ) ( 105408 lb hr ) BTU = 2951424 hr BTU Horsepower = 2951424 = 1160 HP hr BTU 2545 HP 13-50 2017 EDITION 126 WWW. Absence of oil. then returned through a mist eliminator to the heat that is generated across the bearings.for Enthalpy & Entropy values. sales gas is ideal for use as seal gas. water cooled. If necessary. Seal Gas System — The seal gas system prevents loss of proper filtration. 13-71 Expander Example Calculation Flow: 60 MMscfd T1 = –60°F P1 = 900 psia P2 = 300 psia Composition: 100% C1 MMscfd//1d/1 lbmol lbmol/16 lb lb 60 = 6588 = 105408 24 hr/379.CTSSNET. FIG. cooled type or shell and tube design. If no recompression is pro- vided. 13-70 lb lb Simple Expander Assume 80% expander efficiency: actual = (0. ting process seal gas to be released from the oil. can cause bearing damage. The lube oil pumps (one stand-by) must maintain a constant flow to the radial and thrust bearings. injected into each labyrinth shaft seal at a pressure higher than that of the process gas. At Inlet conditions BTU BTU h1 = 295 .0 T2 ideal –160°F lb°F BTU h2 ideal 260 lb BTU BTU ideal = (295 – 260) = 35 FIG. Lube oil filtration is extremely important due to close toler- ances between bearing surfaces. If recompression is necessary for the gas processing plant. process gas and assures protection against entry of lube oil into ers recommend a light turbine oil (315 SSU at 100°F) for best process gas areas. duplicate coolers (one stand-by) are The system for seal gas injection consists of a liquid collec- recommended. tor. or im. To accomplish this. the reservoir should be equipped with a heater to bring the oil up to temperature for a “cold” start.5 scf hr/lbmol hr Using Fig. a bladder type with switching coastdown accumulator. a stream of “seal gas” is machine performance. TECH BRIEF are monitored on the lube console and normally consist of two The lube-oil reservoir serves as a surge tank to enhance electric motor-driven lube oil pumps. a stream can be taken from the expander inlet separator. If the cool- ing water is scale forming. and a pressurized reservoir with mist eliminator. and differential pressure regulators. CTSSNET. From Spec to Ship to Support. customized equipment built to exact specifications. from start to finish. www.com/en 2017 EDITION 127 WWW. That’s the promise of high performance.mhicompressor. Count on next-generation designed compressors. Expect flexible solutions and greater certainty in project execution. count on Mitsubishi’s advanced compressor promise – highly engineered.NET CTSS . THEN WE OVER DELIVER. OUR ADVANCED COMPRESSOR WE PROMISE HIGH PERFORMANCE. Most of all. With Mitsubishi Heavy Industries. you can expect more than reliable performance. delivered. Reliable Compressor Performance. Also. This valve is called the J-T (Joule-Thomson) valve. Fig. The expander manu. given the process conditions. 13-73 shows the change in efficiency as a func. improper gas dehydra- tion. and improper seal gas filtration. the second pump serving as a standby. put enough oil into the process to cause a problem. heat buildup which occurs through the bearings. form a protective barrier against carbon dioxide or water freez- ing. wheel. Gas entering the expander is directed by adjustable nozzles into the impeller. This is done by providing a force-measuring load-meter on each thrust bearing. and a thrust control valve which controls the thrust by control of pressure behind the thrust balancing drums or behind one of the seals. Fig. 13-72 higher pressure differentials. Pressure reductions are normally limited to 3-4 ratios.CTSSNET. High Thrust Thrust bearing force imbalance is caused by difference in High Lube Oil Temperature pressures between the expander discharge and compressor suc- tion. a 9 to 15 psi signal from a pressure con. 13-51 2017 EDITION 128 WWW. thrust bearings. If the seal gas is delivered from a cold supply point (expander inlet separator) then a means of heating the gas is necessary. Some of these conditions are: Greater ratios reduce expander efficiency to the extent that 2- stage expansion may be advisable. Control Systems For temperature control. lack of oil flow. High Vibration The adjustable inlet nozzles function as pressure control Low Lube Oil Flow valves. Seal Gas — Use a suitable gas stream with filtering and pressure control to maintain proper gas pressure at the shaft As a further protection against water freezing. Most expanders are supplied with monitoring and shutdown devices for shaft vibration. These devices are set to shut down the expander before damage occurs. The seal gas should be introduced before the lube oil system facturer determines the wheel diameter and specific speed for is started because there might be a pressure upset which would maximum efficiency. These two load-meters indicate thrust bearing oil film pressure (propor- tional to bearing load) and the third shows the pressure behind the balancing drum as controlled by the valve in its vent as a means of adjusting the thrust load. it is essential that steps be taken Lube Oil Schematic to control the thrust loads against each other. the thrust loads are usually within the capabilities of the thrust bearings. jection connections are incorporated into the system upstream of the expander. Controls are provided to ensure oil flow to bearings at proper pressure and tempera- ture.NET CTSS . High Inlet Screen Pressure Drops troller opens a bypass control valve. About one-half of the pressure drop across the Shutdown — A number of conditions during the operation expander takes place in the nozzles. the expander speed Each of the main rotating components (radial bearings. improper oil filtration. On increasing flow beyond the full open nozzle position. seals. Machine — The expander speed is established by the man- ufacturer. 13-74. a tem- er dehydration and filtering. Two (2) lube oil pumps are furnished. Lube Oil — The lube oil must be filtered. the oil must be cooled to prohibit Process — Control of the process streams begins with prop. may change. Most systems use a primary and secondary filtering system. methanol in. The standby oil pump is controlled au- tomatically to cut in to provide oil pressure upon failure of the main pump or reduction in pressure for other reasons. A pneumatic operator takes a split range signal (3 to High Inlet Separator Level 9 psi) to stroke the nozzles. imparting kinetic energy to of expanders justify prompt shutdown to avoid serious dam- the gas which is converted to shaft horsepower by the expander age. TECH BRIEF Seal gas flow requirements are determined by the expander Generally an oil flow bypass valve is included to permit ex- manufacturers as a part of their performance rating. At FIG. or it could come from an outside source such as pipe vibration or gas pulsation. With a differential of the order of 20 psi. As plant operating conditions change. thereby the net thrust load will not exceed the thrust bearing capacity. and shaft seals) can be damaged or eroded by tion of change in design flow rate. cess flow to bypass the expander bearings and return to the reservoir. Vibration comes from an unbalanced force on one of the ro- tating components. Generally a final protective screen perature control bypass is included in the circuit for an extra upstream of the expander is designed into the piping system to measure of control to keep the oil from getting too cool. low operating costs. or helical screws.Simple. natural. crankshafts.CTSSNET. pistons. the cylinder and rotor can each be re-machined several times .com 2017 EDITION 129 WWW. two-stage to 1800 SCFM • Working pressures to 300 PSIG • Made in the USA since 1929 Call us at +1 610 264 6800 and mention this ad to receive a special package offer.NET CTSS . In addition. With only two bearings and no valves. and minimal downtime. and bio gases • Durable carbon fiber blades extend the cylinder life • Total capacity control with VFD and/or gas bypass • Single-stage to 3000 SCFM. reliable efficient FLSmidth’s Ful-Vane™ rotary vane compressors are designed for long life. www. • Suitable for casing head.flsmidth. field maintenance is easier than with other compressor technologies. Our B3000™ carbon fiber blades outlast the competition.resulting in a number of Ful-Vane compressors still in operation since the 1940s. flare. 545 FIG. Simultaneously. The expander bypass valve (J-T) opens automati- cally and is positioned by the split-range pressure controller to keep the plant on-line in the J-T mode. This is accomplished by actuating quick acting shutdown valves at the expander in- let and outlet and the compressor inlet. mass flow (lbs/hr). inlet and outlet conditions (pressure. 13-73 Low Lube Oil Pressure Example Change in Efficiency with Flow Rate High Speed Two primary actions of a shutdown signal are to block gas flow to the expander and the compressor. The pro- cess of calculations is just the reverse of selecting a machine performance. temperature) for the expander. Field Performance — Field measurements can be made to check efficiencies and horsepower of the expander. a pres- surized bladder supplies oil to the bearings during the expander coast down. 13-74 Typical Expander/Compressor Cross-Section with Thrust Balancing Schematic 13-52 2017 EDITION 130 WWW.> actual = ht2P2 – ht1P1 h actual = h ideal lbs/hr EPactual = 2. TECH BRIEF FIG.NET CTSS . Knowing the gas composition. the actual difference in enthalpy can be determined for each unit.CTSSNET. ” Solar Tur- Turbomachinery Symposium.” Perry.. New York.” Neerken. “Gas and Air Compression Machinery. McGraw-Hill Book Co. New York. 2006. Section 6. Gastech.. American Petroleum Institute Standards — API 678 — “Accelerometer ..... W. Because ..com 13-53 has nothing to do with secrets.” Hy- ing and Analysis. J. Beg.” Poling. “The Physics of Centrifugal Compressor Performance... Poe. New York . 1979... Inc. CTSS bines International. TECH BRIEF REFERENCES Gas Machinery Research Council.. New York. Compressors for General Refinery Services. Shaft-Sealing and Control Oil Systems for Special-Purpose Applica- Kurz./Mafi... Dr. Houston. 1964. S. Aug.” 35th Criqui. International Organization of Standardization Standard ISO 13631: March 2011. “Compressor Selection for the Process Industries. Based Vibration Monitoring Systems. 2004./Chilton. R. O’Connell. San Jose. 2009 Texas. 1 Sarshar.. Transmission and Processing. Los Angeles. “Selection Guide for Expansion Turbines. and Fozi. L. S. R.” Mc- Book Co. C.co/dictionary 1..95 Plus Shipping . 2006.A. P. A.. Heinz P. “Chemical Engineers Handbook. J. New York. 2001. Kurz. H. nology to Boost Production from Oil and Gas Fields”.. “Acceptance Criteria for Gas Compres- tions. “Application of Transducers to Rotating Machinery Monitor- Bergmann. “Guideline for Field Testing of Gas Turbine and Centrifugal Compressor Performance. “A Practical Guide to Compressor Technology. “Applications of jet pump technology to enhance production from gas fields”.. White.“Centrifugal Compressor Applications: Up- stream and Midstream. “Compressed Air and Gas Data. “Handbook of Natural Gas Centrifugal Compressors and Expander Compressors for Petroleum. Houston. “Turboexpanders and Expansion Processes for In- Brown. Kurz. Gibbs.. P. Jan.” Fifth Edi- American Petroleum Institute Standards — API 619 — “Rotary Type tion. W. Inc. C.” Reid. 1975. M. Chemical and Gas Industry Services. R. R. Paperback. Speight. Feb. Gas Machinery Research Council.” ASME Paper GT2002–20282. New York. Chemical Engineering..” McGraw-Hill Bloch. F.4322
[email protected].. line Simulation Interest Group. 204 pages US$24. American Petroleum Institute Standards — API 670 — “Non-Contact- ing Vibration and Axial Position Monitoring System .558.A. rocating Compressor Performance. R. B.” Gulf Publishing. 2 Sarshar. E.” 38th Turbomachinery Symposium. “Application Guideline for Centrifu- gal Compressor Surge Control Systems.” American Petroleum Institute Standards — API 618 — “Reciprocating Chemical Engineering. Swearingen.. M.” 2006.” 2009 . A. C. Chemical and Gas Industry Services. A. The Illustrated Dictionary Of Essential Process Machinery Terms Why struggle through useless Internet search results for technical terms? Order your copy today: “LIP SEAL” http://dieselpub. G. Offshore Gas Processing.” Rasmussen. Jan. “Rotor Dynamics of Centrifugal Compressors.” 5th ed.. California. J. drocarbon Processing..” Rotoflow Corp. “The applications of Jet Pump Tech. F. P. M. J.” Ingersoll Rand Co.800.” dustrial Gas. 2002 — Petroleum and Natural Gas Industries — Packaged Recipro- cating Compressors. C. Prausnitz. Positive Displacement Compressors for Petroleum. S. Scheel. A. 2002. BIBLIOGRAPHY Kurz.M. “Control Systems for Centrifugal Gas Compressors. California. R.. N.” sion Systems. “The properties of Gases and Liquids. American Petroleum Institute Standards — API 617 — “Axial and Mokhatab.”Guideline for Field Testing of Recip- Feb.. Graw-Hill Book Co. R. Gas Machinery Research Council.. Texas.” Noise Control and Vibration Reduction. F. 1975. R.. D.... Inc. Beg.” 2008 . “Surge Avoidance for Compressor Systems. H..” Pipe- American Petroleum Institute Standards — API 614 — “Lubrication. N. Dr. N. McGraw-Hill. 2009. 341 hp = 1..472 41 55.138 kgf m 1 kgf m = 9.341 21 28.825 84 112. 17 23.791 69..392 71 95.417 83 112.461 80 107.724 67 90.259 97 130.184 44 59.233 60 81.051 70 93.693 36 48. In its Section 2.. ampere A SPECIFIC CONSUMPTION second squared.. The Newton is that force which..619 92 124. Description and Definition of Terms.143 82 109.CTSSNET.305 fuel and Btu/ft3 or kJ/m3 for gas fuel) multiplied times 4 5..669 is the Newton meter (Nm).. kilogram kg when applied to a body having a mass of one Time..963 48 65.128 85 115...737562 pound-force (lbf ft).159 per square meter (kN/m2)..705 81 109..360 metric hp HEAT RATE kW hp kW hp kW hp kW hp kW hp 1 hp = 0. one bar being 100.623 1 metric hp = 0. candela cd ambiguous term...808 73 98...030 50 51 67. A 14 18..251 46 62...397 16 21.300 63 85.. being equivalent to just 1 g/kWh = 0. One Watt (1 W) is cific energy consumption is expressed: g/kWh..... the gram (g)..907 71 96.. PK. grade) scale.687 95 128.. The Kelvin unit is identical in interval 19 25.810 56 75... energy and type.5 lbf/in2 = 1.000145 lbf/in2 or 0.. this unit being one thousandth of a bar..00134102 horsepower... with a wide range of multiples and sub- quantity of heat – the Joule (J).368 66 89.312 1. PS.........135 26 35.033 (lb/hph) equivalent to 0.012 65 88.502 42 56. for which the SI unit urements are given. which is a kilogram meter per Length...797 37 49. The SI system.774 34 45. Known System of Units (Systeme International d’ Unites).736 g/metric hph To give an idea of how currently used units convert kilowatt (kW) is used..22 Imp gal/h 5 6...728 28 37.049 37 50. this heat value of the fuel whether liquid or gaseous The base SI unit for linear dimensions will be the being based on the SI unit of work.. will no longer apply for force.600 98 131..410 30 40.802 81 108..526 34. this being the same as a kilopascal.712 22 29. Thermodynamic temperature . On the other TEMPERATURES 10 13.. mass..507 85 86 113....646 (sfc) specific fuel consumption (measured in lb/hph TORQUE or g/kWh).319 49 66..595 54 72.. absolute zero K Distribution Press Ltd. so one Newton meter (1 N m) is X sfc (ft3/hph) 15 20... and equal to 0.503 72 97.705 8.414 = kJ/kWh 18 24.....245 6 8.069 bar is still permitted.956 kPa).231 50 67.896 45 61.871 90 120. is founded on seven base units. 118 Ewell Road...423 24 32..848 87 116..877 59 79...894 93 124.001 sure. gives it an acceleration of one meter per Electric current ..735 kW = 0. 0.. there is a school that favors the kiloNewton 15 20.101972 To convert these units to SI units: 17 22..641 60 80... Thus the SI unit of measurement for net spe.028 67 89...607 47 63. so the kilogram in effect should Amount of substance.010 SI unit of force — the Newton (N) – and the SI unit 9 12......761 20 26.020 kgf/cm2..014 metric 1 g/metric hph = 1.656 64 86. so direct conversions can be 20 27. One Watt is a kilometer is a meter x 103.626 33 44... The 1 g/hph = 1.890 49 65..102 1 Nm = 0. it will continue to be common parlance to internal combustion engine referred to net power use the word “weight” when referring to the mass of an object.. or 0.754 98 132..7457 kW.351 Heat Rate (Btu/hph) = LVH (Btu/lb) X sfc 10 13.202 29 39.055 = kJ/kWh 1 lbf ft = 1.405 38 51..061 82 111.079 kilogram-force meter (kgf m).. multiples ranging from exa (1018) to atto (10-18): A equal to one Joule per second (1 J/s). while a very small unit of power. One Newton (1 N) is 11 14.184 43 58.975 93 126.263 90 91 122..023 23 30.807 Nm = 7..415 74 99.165 57 77. Use of Celsius 1 lbf/in2 = 0.067 23 31..282 100 134....208 47 63. so for engine ratings the 0. and 1 hp being the equivalent of 0.110 99 134..889 European engine designers favor the bar as the unit 1 liter/h = 0. which is ment of lube-oil consumption will be quoted in liters 3 4..738 lbf ft = 0.981 34 46.668 currently accepted metric equivalent..138 38 50. but it is important to note that the kilogram these being: both the FPS and corresponding SI units of meas..380 hand..300 59 79.828 42 56...349 80 108.941 99 132..282 77 104. so measure. Undoubtedly. since this is an Luminous intensity.005 64 85.98 bar “Vehicle Metrics” published by Transport and 0 K = 273°C....2248 pound-force (lbf) or 0. 5 6 6.166 66 88.356 Nm = 0. and the 12 16.986 hp (LHV) of Fuel (measured in Btu/lb or kJ/g for liquid 2 2.558 11 14....Kelvin K Fuel consumption measurements will be based on the currently accepted unit.341 hp 1 lb/hph = 608.715 seems to be favored to indicate barometric pres.779 25 33. this being based on the For Liquid Fuel 8 10.116 40 54.742 53 71....398 97 131..323 62 83.867 45 46 60..944 62 84....346 61. character is used without the degree symbol (°) nor.. this is a very small unit..682 22 29. 4 5..820 40 53...102 kgf m Btu/kWh X 1.. for engine performance purposes.277 56 75.. which is the equivalent of 14....28084 feet (ft).479 39 52...582 1 bar = 14.484 83 111.987 115. in 1973 published its Performance Test Codes for 2017 EDITION 132 WWW.438 77 103.847 28 37...577 95 127. These tables are reproduced from the booklet 1 kgf/cm2 = 0..533 only 0.....761 39 52.914 30 31 40. so being virtually the same as the 9 12.NET CTSS ...447 again...079 68 92..433 33 44..618 57 76....710 69 92.mole mol Kilowatt Hour (kWh). which is becoming uni...042 96 130.374 kilogram-force (kgf)... and one meter is equal to kilo.34102 hp) 1 kW = 1..959 58 77..177 one Newton per square meter (1 N/m2)..484 86 116..147 70 94.....772 84 113..364 24 32..097 76 101.212 91 122. and the “Weight” in itself will no longer apply..756 75 100.254 53 71.161 41 54.098 54 73..10197 12 16..589 61 82.024 123.. meter m second squared.356 21 28.120 79 105.926 76 103.638 78 105.... this code is intended for tests of all WEIGHTS AND LINEAR for which the abbreviation SI is being used in all types of reciprocating internal combustion engines DIMENSIONS languages. Then mally employed with other scales of temperature.843 43 57..913 52 69.. gram (kg) will continue to be used as the unit of versally used..435 69 93.803 temperature of zero degree Kelvin is equivalent to 16 21... The American Society of Mechanical Engineers 1°C = 273 K Surry.341 k/kWh British unit of horsepower is equal to 1.115 35 46.214 74 100. For indications of “weight” the original metric kilo- for determining power output and fuel consumption.....982 61 81.456 36 48..733 72 96.553 92 123.601 of pressure.001644 lb/hph = millimeter is a meter x 10-3..964 3 4.454 55 74...540 44 59...466 100 135.420 Or 19 25..504 lbf/in2 or 8 10. For Gaseous Fuel 13 17....092 32 42...0197 kgf/cm2 made by adding or subtracting 273.546 liters/h 7 9..3 g/kWh to SI units.675 42..746 g/hph = 0..570 75 101.692 of length – the meter (m)....36 g/kWh horsepower (CV...0000102 kgf/cm2.328 The derived SI unit for torque (or moment of force) 7 9..014 metric hp Heat Rate is a product of Lower Heating Value 1 1.270 32 43.. Surbiton..840 87 117..337 35 47.......521 58 78.687 65 87.235 94 126...715 gram force (kgf) and one member is equal to Heat Rate (Btu/hph) = LVH (Btu/ft3) 14 18.386 52 70..530 89 119.870 kgf/cm2...196 88 119..046 25 26 33..056 3. POWER output.074 73 97.936 55 73.. is the Newton (N). mechanical.491 27 36. the millibar The SI unit of temperature is Kelvin (K).35582 Nm) Although it has been decided that the SI derived Although the metric liter is not officially an SI unit..)..746 kW = 1. 1 kW being equal to 1.993 79 107.387 27 36.515 18 24.000 Pascal (100 1 Imp gal/h = 4. meter.331 94 127..751 31 41. etc. second s kilogram.664 63 84.738 equal to 0.226 to the Celsius unit.. 1 1.369 68 91.... KILLOWATTS (kW) TO HORSEPOWER (hp) (1 Kw = 1.. units/power units so that energy consumption of an though. for example..145 lbf/in2 or 0.. is based on low unsaturated The derived SI unit for power is the Watt (W).. 13 17..15°C on the Celsius (centi. as PTC 17.233 lbf ft LUBRICATING-OIL POUNDS FORCE FEET (lbf ft) TO NEWTON METERS (Nm) PRESSURE AND STRESS CONSUMPTION (1 lbf ft = 1...918 96 128..821 2 2.0102 a temperature of -273...572 51 68. Mass .. SI UNITS… THE INTERNATIONAL STANDARDS SYSTEM The system outlined here is the International Reciprocating Internal Combustion engines.552 89 120. being the same as its use will continue to be permitted.779 78 104..549 48 64. the tables below give examples.069 29 38. So many per hour (liters/h). Btu/hph X 1. lbf ft Nm lbf ft Nm lbf ft Nm lbf ft Nm lbf ft Nm unit for pressure and stress should be the Pascal (Pa). KT6 6HA England..189 88 118.. Also adopted is heat only be used as the unit of mass. If converting from Fahrenheit degrees to Centigrade degrees.843 29 63.22 19 66.3048 m/sec 0.205 76 2.1 79 174.370 100 220.51 m/s 1 lb/hp = .811 66 2.4 31.911 44 97.575 60 2.0176 100 to 1000 571 1060 1940 849 1560 2840 C F C F 577 1070 1958 854 1570 2858 38 100 212 77 170 338 582 1080 1976 860 1580 2876 MILLIMETERS (mm) TO INCHES (in) 43 110 230 82 180 356 588 1090 1994 866 1590 2894 49 120 248 88 190 374 593 1100 2012 871 1600 2912 (1 millimeter = 0.33 26 78.8 27.640 72 158.16 cm2 6.8 55 131.4 28.753 53 116.139 50 110.096 84 185.56 33 91.2 188 370 698 427 800 1472 lb kg 0.594 62 136.4516 sq.0 221 430 806 460 860 1580 kcal kilocalorie -6.416 11 24.4482 -14.4 321 610 1130 Nm3/hr normal* cubic meter/hour Old Metric 3.02 cu.0 86 186./min.315 28 1.644 17 37.6 78 172.003 64 141.1 97 206. 8.425 8 0.8 171 340 644 410 770 1418 ft/sec foot/second in mm 25.4 67 152.710 87 191.0665 7.929 69 2.6 13 55.9 7 44.0 26.756 90 3.347 95 209./hp 15 0.323 79 3.409 22 48.277 80 176.188 5 11. 7.046 30 66.258 20 44.0283 m3/min 0.717 89 3.254 75 165. 7 0.432 27 59.0716 -7.439 16 35.047 72 2.22 45 113.827 41 1.9 ft.732 64 2.9 66 150.2 243 470 878 482 900 1652 kPa kilopascal °F (Interval) °C (Interval) 5/9 °C (Interval) 5/9 -3.693 63 2.33 38 100.268 Note: The numbers in bold face type refer to the temperature either in degrees Centigrade or Fahrenheit 4 0.945 44 1.325 8.914 m 0.2 15.78 27 80.2 1 33.6 96 204.378 55 2.093 40 88.3 65 149.0 18.165 75 2.848 18 39.2 28. in.934 49 108.00 23 73.0 37.898 20 0.44 40 104.8 82 179.677 88 3.660 33 72. H2O kPa 0.0 59 138.00 41 105.559 85 3.346 the equivalent temperatures will be found in the left column.4536 -9.320 46 101.0 50 122.9 84 183.039 21 0.866 42 1.126 74 2.7 89 192. m/s ft.980 59 130.740 10 cu.465 9 0.235 lb.063 47 1.0 12.1868 5.22 28 82.2 81 177.0 68 154.6 25.540 -5.8064 566 1050 1922 843 1550 2822 nm3/hr nm3/min 0.2 34.0 304 580 1076 N Newton 2.189 66 150 302 100 212 413 610 1130 2066 888 1630 2966 2 0.0 21. m3 0.0 193 380 716 432 810 1490 hp horsepower -8.0 5 41.825 13 28. Multiply 2.7 11 51.11 21 69.0 23. ft.6 149 300 572 388 730 1346 cm3 cubic centimeter Btu kJ 1.2 90 194.7 71 159.748 39 1.4 58 136.069 35 77.030 14 30.1 12 53.8 18. 5 0.070 -6.142 94 207.67 29 84.6 87 188.244 77 3.4 94 201.0 14 57.197 25 0.276 27 1.733 92 202.260 52 2.6 51 123.0185 kg/m3 16.6 27.22 36 96.891 83 182.274 36 79.343 51 112.402 81 3.8 0 32 10.2 216 420 788 454 850 1562 psig kPa gage 6. kg/metric hp lb/hp 19 0.687 82 180.961 98 216.44 49 120.709 38 1.6 343 650 1202 6.2 299 570 1058 538 1000 1832 mph mile per hour 1.6 19.4 36.845 73 160.231 70 154.701 1 L = 61.992 96 3.540 -11.5939 N/m 14.4 266 510 950 504 940 1724 cu.053 19 41.8 21.3558 -3.11 30 86.9 13.6 543 1010 1850 821 1510 2750 atm kPa 101.9 75 167.008 71 2.2590 kcal/nm3 0.2 160 320 608 399 750 1382 °F Fahrenheit -12.1 61 141.7 98 208.3 74 165.858 L cu.413 66 145.032 97 3.324 90 198.937 93 205.6 260 500 932 499 930 1706 m meter ft/sec m/sec 0. the answer will be found in the column on the right.211 10 22.8 73 163. mm2 645.0 29.551 96 211.299 53 2.73 psia cm H2O kPa 9.574 2 4.4 11.3558 N•m 1.NET CTSS .6 316 600 1112 N/m2 Pascal From Metric By 3. Hg inch mercury psi kPa 6.3769 cm Hg 2.3 8 46.33 47 116.0 277 530 986 516 960 1760 m2 square meter gas (US) L 3./min.4 17.8 64 147.7854 L 3.0 138 280 536 377 710 1310 cm centimeter lbf N 4.482 81 178.0 77 170.307 which is desired to convert into the other scale.888 39 85.6093 -2.779 3 6.1565 -11.339 54 2. in.67 35 95.024 46 1.4 20.071 98 3.073 79 174.283 78 3.1 52 125.8948 ata 0.118 23 0.I.795 91 3.799 63 138.0 332 630 1166 psia pound/square inch absolute cm2 mm2 100. Hg kPa 3.8 227 440 824 466 870 1598 in.4 76 168.89 39 102.6 288 550 1022 527 980 1796 m3/min cubic meter/minute scfm nm3/min 0.598 7 15.8 199 390 734 438 820 1508 in inch hp kW 0.906 43 1.617 67 147.0 110 230 446 349 660 1220 -17.6 232 450 842 471 880 1616 kJ kilojoule -5.1 70 158.7457 -8.165 99 218.756 97 213. kg/m3 16.6093 km/hr 1.4 549 1020 1868 827 1520 2768 *“Normal” = 0°C and 1.026 69 152.433 31 1.89 48 118.0929 -16.663 77 169.252 -13. = 0.479 37 81.2 327 620 1148 psi pound/square inch 4.8948 bars abs 0.9 57 134.7 80 176.11 34 93.2 54 129.235 15 33. CONVERSION FACTORS SI — METRIC/DECIMAL SYSTEM TEMPERATURE CONVERSION TABLES* ABBREVIATIONS CONVERSION FACTORS By Albert Sauveur abs absolute To Convert To S.44 15 59.5939 -13.8 538 1000 1832 816 1500 2732 bars kPa 100.2 132 270 518 371 700 1292 lb/cu.0 35.957 54 119.6 33. in. in.2488 cm H2O 2.457 57 2.208 65 143.228 26 57.6 30.56 22 71.4 6 42.7854 -0.8 338 640 1184 psig pound/square inch gage kcal kJ 4. ft.8 91 195. 5.913 94 3.4 22.6 69 156.0 15./min.220 51 2.142 49 1.0 95 203.4 182 360 680 421 790 1454 gal gallon yd m 0.4 25.8 100 212.779 17 0.087 73 2.540 kg kilogram in.598 86 3.56 31 87.0551 kcal 0.914 88 194.571 57 125.937 KILOGRAMS (kg) TO POUNDS (lb) (1 kilogram = 2.8 30. cubic foot Btu/hr W 0.390 61 134.2 12.548 52 114.6 4 39.7 62 143.2 1000 to 1630 scfm standard* cubic foot/minute cm mm 10.417 56 2.819 18 0.512 33 1.61 0.2 31.2 99 210.8 32.78 37 98.4 210 410 770 449 840 1544 in.4482 N 4.4536 kg 0.03937 inch) 54 130 266 93 200 392 599 1110 2030 877 1610 2930 mm in mm in mm in mm in mm in 60 140 284 99 210 410 604 1120 2048 882 1620 2948 1 0.630 36 1.ft.9 93 199. 1 m/s = 196. while if converting from degrees Centigrade to 6 0. Multiply To Old Multiply 0 to 100 100 to 1000 – cont.520 84 3.6 204 400 752 443 830 1526 in.8 24.787 40 1.I.CTSSNET.0283 -1.8948 kg/cm2 0.772 65 2.583 VOLUME PISTON SPEED WEIGHT/HORSEPOWER 12 0.070 -7.3332 37.251 31 66.8 35.366 56 123.228 71 160 320 104 220 428 3 0.3 83 181.157 24 0.236 26 1.6 16.079 22 0.7457 kW 0.354 29 1.6 11.802 8 17.7 2 35.0268 nm3/hr 1.496 58 2. m2 0.116 45 99.706 43 94.528 91 200.386 degrees Fahrenheit.591 35 1.393 6 13.874 93 3.01325x105 9.822 68 149.89 25 77.78 18 64.2 17.56 42 107.2 271 520 968 510 950 1742 mm millimeter -1.162 55 121.835 92 3.4 14.78 46 114.8 143 290 554 382 720 1328 cm2 square centimeter lbf/ft N/m 14.669 37 1.729 48 105. = 0.2931 kcal/hr 0.505 86 189.0929 m2 0.6 121 250 482 360 680 1256 °C Celsius sq.6 177 350 662 416 780 1436 ft-lb foot-pound ft m 0.110 99 3.185 60 132.7 53 127.3048 -10. H2O inch water psia kPa abs 6.621 12 26.33 17 62.502 42 92.480 83 3.102 48 1.776 58 127.362 80 3.441 82 3.984 45 1.181 50 1.0283 0 32 89.543 11 0.0 32.44 24 75.683 38 83.4 154 310 590 393 740 1364 cu.436 71 156.968 70 2.8 116 240 464 354 670 1238 Btu/hr British thermal unit/hour -16.661 14 0.614 23 50.455 32 70.2 72 161. 1 kg/metric hp = 2.868 78 171.953 95 3.3 56 132.462 2017 EDITION 133 WWW.164 L 100 ft.3 92 197.400 cm 2.525 47 103.11 43 109.4 293 560 1040 532 990 1814 1.1 88 190.023 25 55.300 85 187.050 74 163. ata atmosphere absolute From Metric By Metric By C F C F C F C F Btu British thermal unit English -17.4 33.2 554 1030 1886 832 1530 2786 Pascals cm Hg kPa 1.6 36.67 20 68.2 23.6 22.984 4 8.459 76 167.8 9 48.150 100 3.204 21 46.8 10.614 61 2.504 10 0.0 249 480 896 488 910 1670 kW kilowatt ft-lb N•m 1.2 63 145.297 41 90.4 127 260 500 366 690 1274 cfm cubic foot/minute -15.6 60 140.914 -10.850 67 2.119 89 196.8 16.622 CONVERSION FACTORS CONVERSION FACTORS CONVERSION FACTORS 13 0.2 20.4 238 460 860 477 890 1634 °F °C = (°F -32) 5/9 °C = (°F -32) 5/9 -4.67 44 111.1 10 50.890 68 2.3048 m 0.1 3 37.8 310 590 1094 To Convert To S.637 28 61.551 34 1.0283 m3 0.20462 pounds) kg lb kg lb kg lb kg lb kg lb 1 2.4 85 185.0 166 330 626 404 760 1400 Btu/scf kJ/mm3 37.865 34 74.16279 6.8 282 540 1004 521 970 1778 m3 cubic meter cfm m3/min 0.654 62 2.638 87 3.0 C F C F sq square kg/cm2 kPa 98.472 32 1.819 24 52.252 -12.535 59 2.394 30 1.89 16 60.0185 -15.8 13.2 26.3048 -2.8 254 490 914 493 920 1688 L liter mph km/hr 1.007 9 19.ft.4474 kg/metric hp 16 0.0 560 1040 1904 838 1540 2804 *“Standard” = 59°F and 14.4 scf standard* cubic foot kcal/hr W 1. NET CTSS .Get the most out of Engine Upgrades Combustion stability Engine management Lower hydrocarbon emissions Precise fuel delivery Control of air-fuel mixture Extended service intervals High efficiency for all load ranges Ignition systems Reliable combustion of leaner mixtures Tailored to manufacturer specifications Reduced downtime 2017 EDITION 134 WWW.CTSSNET. CTSSNET.your equipment Energy savings Stepless flow control Innovative valve design Compressor re-conditioning Resource savings Reduced purge gas consumption Elimination of process gas leakage Increased reliability Environmental compliance New valve plate material Leakage-free compressor operation Compressor monitoring Reduced oil consumption Compressor re-conditioning 2017 EDITION 135 WWW.NET CTSS . 2017 EDITION XX WWW.CTSSNET.NET CTSS . 2017 EDITION XX WWW.NET CTSS .CTSSNET. Find out more at www.CTSSNET.man.Green Technology Efficient power engineering Marine Engines & Systems Power Plants Turbomachinery After Sales The new gas turbines from MAN Diesel & Turbo offer outstanding reliability. Short synchronization times guarantee heat and electricity whenever they are needed.turbomachinery. We have the answer to your energy requirements thanks to customer-tailored solutions with 6-13 MW gas turbines.eu 2017 EDITION 138 WWW. Efficiency rates of over 90% can be achieved with the aid of state-of-the-art combined heat and power technology. compactness and flexibility in modern gas power plants.NET CTSS . Because of their low levels of noise and waste gas emissions they are particularly suitable for installation in residential areas. CTSSNET.NET CTSS .2017 EDITION 139 WWW. Because we always keep the big picture in mind. art standardized and customizable machines. we believe that our satisfied customers all over the world are our biggest achievement.NET CTSS . we bring more Residue Gas Compressors Standardized Fuel Gas Boosters innovation. various LNG cycles.CTSSNET. This means not only state-of-the. but also a leading Research & Development team and our unswerving commitment to customer service. lives. 2017 EDITION 140 WWW.Solutions with an impact Refrigeration Gas Compressors Gas Processing Expanders You lead an industry Refrigeration gas compressors Our expander compressors are key deliver high flow levels and to cryogenic NGL/LPG recovery. that powers peoples’ maximum efficiency for optimal natural gas dew point control and NGL recovery and LNG production. compressors ensure reliable and packaged to deliver precise natural uninterrupted sales gas supply gas throughput for optimal without pulsation or stress gas-fired turbine performance. We bring the solutions that fuel your success. At Atlas Copco Gas and Process. more efficiency. to pipeline. and more reliability that enable you Atlas Copco residue gas A standardized full gas booster is to succeed in your sector. atlascopco-gap. onboard LNG reliquefaction.CTSSNET. rates for industrial gas main ammonia. Petrochemical Expander Single-Shaft Compressor An expander runs at the heart of The single-shaft centrifugal downstream processes. and hydrogen.CO2 Compressor LNG Compander An efficient. CTL. including compressor delivers high flow ethylene. propylene.NET CTSS . leveraging the best of integral-gear applications and other supercritical power cycles. www. integrated Energy-efficient compander design Take a closer look at our featured solution for urea production. syngas air supply as well as GTL. the industry’s most efficient and compact compressor design.atlascopco-gap/igc 2017 EDITION 141 WWW. IGCC and methanol. butylene. Discover more about integrally-geared compressors at: www.com Integral Gear Technology running at the core Atlas Copco turbocompressors and expanders are designed around Integral Gear Technology. methanol. CCS technology to reliably power your turbomachinery solutions at: and advanced oil recovery. gas-tight. CTSSNET. A new fit for innovative compression. NEA GROUP also proves its OEM in-depth know-how when it comes to revamp & modernization of dia- phragm compressors from HOFER as well as from other brands. The multi-stage. the service provider of the GROUP.com sales@neuman-esser. NEAC Compressor Service. Additionally.and oil-free compression.de Phone: +49 (0) 208 / 4 69 96-28 www. one crank drive system offers a leakage-free solution for low suction and high discharge pressure ratios at high mass flows.com 2017 EDITION 142 WWW.A NEW FIT FOR INNOVATIVE COMPRES SOLUTION NEEDED TO COMPLY WITH ZERO EMISSION? COMBINE A GAS-TIGHT RECIP CRANKCASE WITH LEAKAGE-FREE DIAPHRAGM HEADS. The NEA hybrid is the answer to the high technical demands of emission.andreas-hofer.hybrid-compressors. cares for the fully sustainable lifetime of all compression systems. This innovative concept combines NEA’s gas-tight crank- case with HOFER’s diaphragm head. www. Once installed.de Phone: +49 (0) 2451 / 481-147 www.NET CTSS .neuman-esser.de sales@andreas-hofer. CTSSNET.SION BLUESTROKE COMPRESSOR TECHNOLOGY PENN Process TM Compressors Recips built in Berlin up to the end of 1995 Authorized OEM supplier for reciprocating compressor lines: Demag 2017 EDITION 143 WWW.NET CTSS . LEADING COMPRESSOR TECHNOLOGY – LOWEST LIFE CYCLE COSTS www.com .burckhardtcompression. POWERING THE FUTURE Thoroughly Proven Power Solutions Maybe you need a turbine compressor set for natural gas transmission, gas gathering or some other process. Or perhaps you need power and heat for continuous duty industrial processes. No matter what the job or where the location, Solar Turbines can provide the power. 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[email protected] for more information. ©2017 Solar Turbines Incorporated NATURAL GAS ENGINES 2017 Basic Specifications 2017 EDITION Manufacturer Output Range Output Per Cylinder Range (kW) Rated Speed Range (rpm) hp kW Displacement Per Cylinder (L/cyl) Stroke (mm) Bore (mm) Rating System & Standard No. ISO - SAE - DIN - Other Number Of Cylinders & Configuration L: In-Line V: Vee-Type H: Horizontal O: Opposed Catalog Page Reference Engine Model Maximum Brake Mean Effective Pressure (bar) min max min max min max min max ARROW ENGINE CO. * K-6 102 116 0.9 1L 4.5 400 800 7.1 6 5 C-46 127 159 2 1L 8.7 450 800 5.6 9 7 C-66 146 190.5 3.2 1L 12.8 350 700 5.5 13 10 C-96 178 216 5.4 1L 18.1 300 600 5.6 19 14 C-106 190.5 216 6.2 1L 28.9 400 800 5.8 32 23 C-255 190.5 190.5 10.8 2L 49 400 750 6 65.7 49 L-795 190.5 228 6.5 2L 24.3 300 600 3.7 65 49 A32 105 120 1.000 3L 6 1000 1200 5.8 22 16 145 A42 105 120 1 3L 10 900 2000 5.8 47 35 A54 98 118 0.9 6L 9.9 900 2200 6.8 68 51 A62 105 120 1 6L 10 900 2000 5.8 80 60 A62TA 105 120 1.000 6L 14.2 1000 1800 9.2 115 86 A90 118 135 1.470 6L 16 1200 1800 6.5 109 81 A90TA 118 135 1.47 6L 18.7 1200 1800 9 150 112 A160 150 150 2.65 12L 35.8 1200 1800 6.7 215 160 BUCK'S GM * 3.0L 102 91 0.75 4L 5.25 7.5 1400 2200 5.31 28 40 21 30 Continuous hp @ 3200 ft. NG fuel 4.3L 102 88 0.72 6V 4.66 7.5 1400 2200 5.51 38 61 28 45 Continuous hp @ 3200 ft. NG fuel 5.7L 102 88 0.71 8V 5.25 8 1400 2200 6.34 56 86 42 64 Continuous hp @ 3200 ft. NG fuel * This company is not represented in the 2017 Supplement with a section describing its products. 8.1L 108 110 1.01 8V 8.87 14.5 1400 2200 7.51 95 155 71 116 Continuous hp @ 3200 ft. NG fuel CATERPILLAR INC. * GCM34 340 420 38.13 16, 12V 381.25 381 750 750 232.07 6135 8180 4575 6100 G3600 300 300 21.2 6, 8L; 12, 16V 220.7 235.1 1000 1000 193.05 1775 5045 1324 3762 G3500 170 190 4.32 8, 12L; 16, 20V 48.9 64.3 1200 1400 184.54 524 1725 391 1286 G3400 137 152 2.3 6L; 8, 12V 26.7 39.5 1500 1800 169.97 215 637 160 475 G3300 121 152 1.75 4, 6L 17.8 26.2 1800 1800 145.52 95 211 71 157 WWW.CTSSNET.NET CTSS NATURAL GAS ENGINES 2017 Basic Specifications 2017 EDITION Manufacturer Output Range Output Per Cylinder Range (kW) Rated Speed Range (rpm) hp kW Displacement Per Cylinder (L/cyl) Stroke (mm) Bore (mm) Rating System & Standard No. ISO - SAE - DIN - Other Number Of Cylinders & Configuration L: In-Line V: Vee-Type H: Horizontal O: Opposed Catalog Page Reference Engine Model Maximum Brake Mean Effective Pressure (bar) min max min max min max min max CUMMINS INC. KTA19GC 159 159 3.16 6L 33 52.3 1200 1800 265 420 198 313 SAE J1995 G/GTA855 140 152 2.33 6L 19.5 35.5 1500 1800 157 286 117 213 SAE J1995 Second Cover QSL9G 114 145 1.48 6L 21.8 21.8 1800 2200 175 175 130 130 SAE J1995 G/GTA8.3 114 135 1.38 6L 12.3 23.7 1500 1800 99 190 74 142 SAE J1995 G/GTA5.9 102 120 0.98 6L 6.2 14.5 1500 2200 49 116 37 87 SAE J1995 DRESSER-RAND BUSINESS * Guascor SFGLD-L (Part of Siemens Power & Gas Series 152 165 2.99 6, 8L; 12, 16V 52.5 52.5 1400 1800 11.7 420 1120 315 840 ISO 3046 Division) (180, 240, 360, 480) Guascor SFGLD-L 146 160 175 3.5 16V 51.3 51.3 1200 1500 11.7 1093 1093 820 820 ISO 3046 Series (560) Guascor SFGRD-L Series 152 165 2.99 6, 8L; 12, 16V 46.8 46.8 1400 1800 10.4 375 1000 281 750 ISO 3046 (180, 240, 360, 480) Guascor SFGRD-L 160 175 3.5 16V 54.4 54.4 1400 1800 10.4 1160 1160 870 870 ISO 3046 Series (560) GE OIL & GAS * Ajax DPC 2804 STD 381 406 46.33 4L 110 158 265 440 4.80 592 846 441 630 ANSI PTC 17-1974 Ajax DPC 2804 LE 381 406 46.33 4L 104 149 265 440 4.30 560 800 418 597 ANSI PTC 17-1974 Ajax DPC 2803 STD 381 406 46.33 3L 110 158 265 440 4.80 443 633 330 472 ANSI PTC 17-1974 Ajax DPC 2803 LE 381 406 46.33 3L 104 149 265 440 4.30 420 600 313 447 ANSI PTC 17-1974 Ajax DPC 2802 STD 381 406 46.33 2L 110 158 265 440 4.80 295 422 220 315 ANSI PTC 17-1974 * This company is not represented in the 2017 Supplement with a section describing its products. Ajax DPC 2802 LE 381 406 46.33 2L 104 149 265 440 4.30 269 384 201 298 ANSI PTC 17-1974 Ajax DPC 2801 STD 381 406 46.33 1L 100 143 265 440 4.30 134 192 100 143 ANSI PTC 17-1974 Ajax DPC 2801 LE 381 406 46.33 1L 100 143 265 440 4.30 134 192 100 143 ANSI PTC 17-1974 Ajax DPC 2202 STD 330 406 36.15 2L 78 110 265 440 4.30 207 296 164 220 ANSI PTC 17-1974 Ajax DPC 2202 LE 330 406 36.15 2L 78 110 265 440 4.30 207 296 164 220 ANSI PTC 17-1974 (Continues) Ajax DPC 2201 STD 330 406 36.15 1L 78 110 265 440 4.30 104 148 82 110 ANSI PTC 17-1974 WWW.CTSSNET.NET CTSS NATURAL GAS ENGINES 2017 Basic Specifications 2017 EDITION Manufacturer Output Range Output Per Cylinder Range (kW) Rated Speed Range (rpm) hp kW Displacement Per Cylinder (L/cyl) Stroke (mm) Bore (mm) Rating System & Standard No. ISO - SAE - DIN - Other Number Of Cylinders & Configuration L: In-Line V: Vee-Type H: Horizontal O: Opposed Catalog Page Reference Engine Model Maximum Brake Mean Effective Pressure (bar) min max min max min max min max GE OIL & GAS * Ajax DPC 2201 LE 330 406 36.15 1L 78 110 265 440 4.30 104 148 82 110 ANSI PTC 17-1974 Ajax E-565 216 254 9.29 1L 21 30 315 525 3.67 28 40 21 30 ANSI PTC 17-1974 6G-825 254 267 13.52 6L 54 81 600 1000 7.38 390 650 291 485 ANSI PTC 17-1974, DEMA 8G-825 254 267 13.52 8L 50 75 600 900 7.38 533 800 398 597 ANSI PTC 17-1974, DEMA 12G-825 254 267 13.52 8L 50 75 600 900 7.38 800 1200 597 895 ANSI PTC 17-1974, DEMA 16G-825 254 267 13.52 16V 50 75 600 900 7.38 1067 1600 796 1194 ANSI PTC 17-1974, DEMA 6GTL 254 267 13.52 6L 68 103 600 900 10.10 550 825 410 615 ANSI PTC 17-1974, DEMA 8GTL 254 267 13.52 8L 68 103 600 900 10.10 733 1100 547 821 ANSI PTC 17-1974, DEMA 147 12GTL 254 267 13.52 12V 68 103 600 900 10.10 1100 1650 821 1231 ANSI PTC 17-1974, DEMA 16GTL 254 267 13.52 16V 68 103 600 900 10.10 1500 2250 1119 1679 ANSI PTC 17-1974, DEMA 8SGT 254 267 13.52 8L 84 140 600 1000 12.42 900 1500 671 1119 ANSI PTC 17-1974, DEMA 12SGT 254 267 13.52 12V 83 124 600 900 12.28 1333 2000 994 1492 ANSI PTC 17-1974, DEMA 16SGT 254 267 13.52 16V 82 124 600 900 12.20 1766 2650 1317 1977 ANSI PTC 17-1974, DEMA 6GTLB 254 267 13.52 6L 68 103 600 900 10.10 550 825 410 615 ANSI PTC 17-1974, DEMA 8GTLB 254 267 13.52 8L 68 103 600 900 10.10 733 1100 547 821 ANSI PTC 17-1974, DEMA 12GTLB 254 267 13.52 12V 68 103 600 900 10.10 1100 1650 821 1231 ANSI PTC 17-1974, DEMA 16GTLB 254 267 13.52 16V 68 103 600 900 10.10 1500 2250 1119 1679 ANSI PTC 17-1974, DEMA 8SGTB 254 267 13.52 8L 84 140 600 1000 12.42 900 1500 671 1119 ANSI PTC 17-1974, DEMA * This company is not represented in the 2017 Supplement with a section describing its products. 12SGTB 254 267 13.52 12V 83 124 600 900 12.28 1333 2000 994 1492 ANSI PTC 17-1974, DEMA 16SGTB 254 267 13.52 16V 82 124 600 900 12.20 1766 2650 1317 1977 ANSI PTC 17-1974, DEMA 8SGTD 254 267 13.52 8L 84 140 600 1000 12.42 900 1500 671 1119 ANSI PTC 17-1974, DEMA 12SGTD 254 267 13.52 12V 83 124 600 900 12.28 1333 2000 994 1492 ANSI PTC 17-1974, DEMA 16SGTD 254 267 13.52 16V 82 124 600 900 12.20 1766 2650 1317 1977 ANSI PTC 17-1974, DEMA (Continues) 2406G 240 260 11.76 6L 112 149 900 1200 12.62 900 1200 671 895 ANSI PTC 17-1974, DEMA WWW.CTSSNET.NET CTSS 12.4 6L 167.8 12.550 ISO3046.4 18V 167.NET CTSS .32 9L.0 233. Constant speed.3 18V 315 332 720 750 19.24 10V 134 168 270 330 8. 18V28AG 295 400 27.62 1800 2400 1343 1790 ANSI PTC 17-1974. DEMA 2412G 240 260 11.100 17. Dual fuel.828 18.9 12V 38.76 12V 112 149 900 1200 12. 12. W46GD 460 580 96.3 900 1000 19.62 2698 2998 2012 2237 Methane # >80 & ISO 3046/1 16V22AG 220 300 11. 20V 450 460 720 750 23 5431 12.55 12V 299 374 270 330 8.62 1200 1600 895 1194 ANSI PTC 17-1974.000 ISO 3046.4 900 1000 19.8 104.17 9L.76 8L 112 149 900 1200 12.13 4800 6000 3581 4476 ANSI PTC 17-1974. W34DF 340 400 36. 20V 480 500 720 750 22 5793 13. DEMA 148 12W330 GE'S WAUKESHA * 275GL 275 300 17.410 4320 10. 16.0 750 1000 15.810 19. Gas Engine.410 4320 10.0 1200 1800 12.4 12V 167. Dual fuel. Dual fuel.0 6.700 17. W50DF 500 580 113. Constant speed.9 750 1200 10. Constant speed. 12.9 345 2250 257 1678 ISO 3046/1 VGF 152 165 3. ISO .8 55.550 ISO3046. W50SG 500 580 113. 16.4 7709 8129 5670 5979 Methane # >80 & ISO 3046/1 WÄRTSILÄ * W34SG 340 400 36.7 2720 5000 2028 3728 ISO 3046/1 GAS ENGINES VHP 216 216 7. DEMA GMV10 Cooper Bessemer 356 356 11. NATURAL GAS ENGINES 2017 Basic Specifications 2017 EDITION Manufacturer Output Range Output Per Cylinder Range (kW) Rated Speed Range (rpm) hp kW Displacement Per Cylinder (L/cyl) Stroke (mm) Bore (mm) Rating System & Standard No.9 614 1450 458 1081 ISO 3046/1 VHP 238 216 9.61 4047 4498 3019 3355 Methane # >80 & ISO 3046/1 * This company is not represented in the 2017 Supplement with a section describing its products.690 23. Constant speed.4 900 1000 19. DEMA 2416G 240 260 11.SAE - DIN .224 25.4 900 1000 19. DEMA 8W330 Cooper Bessemer 457 508 26.7 186.260 ISO3046.4 16V 167.2 90. Dual fuel.535 11.4 900 1000 19.2 160 1175 119 880 ISO 3046/1 NIIGATA POWER * 6L22AG 220 300 11. 16.7 186.7 186.4 8L 167.32 9L. 16V 42.64 1800 2250 1343 1679 ANSI PTC 17-1974.88 18V 1045 1070 500 514 22 25. 8L.55 8V 299 374 270 330 8.CTSSNET.76 16V 112 149 900 1200 12.64 2160 2700 1611 2014 ANSI PTC 17-1974.24 12V 134 168 270 330 8.62 1349 1500 1007 1118 Methane # >80 & ISO 3046/1 SYSTEMS 8L22AG 220 300 11.931 23.8 186. W32GD 320 400 32. Gas Engine.7 6L.61 3597 3997 2683 2982 Methane # >80 & ISO 3046/1 18V22AG 220 300 11. 16V 169. 16V 19. Constant speed.8 186.000 ISO3046.64 3200 4000 2387 2984 ANSI PTC 17-1974. WWW. 20V 480 500 720 750 22 5793 13.535 17.Other Number Of Cylinders & Configuration L: In-Line V: Vee-Type H: Horizontal O: Opposed Catalog Page Reference Engine Model Maximum Brake Mean Effective Pressure (bar) min max min max min max min max GE OIL & GAS * 2408G 240 260 11. 18V 975 500 514 24 15.1 750 1200 10.88 18V 950 975 500 514 20 22.39 12. DEMA Cooper Bessemer 356 356 11.337 4050 9200 ISO3046.62 2400 3200 1790 2387 ANSI PTC 17-1974. Constant speed. DEMA GMV12 Cooper Bessemer 457 508 26.62 1849 1999 1342 1491 Methane # >80 & ISO 3046/1 12V22AG 220 300 11. 1 4850 * This company is not represented in the 2017 Supplement with a section describing its products.000 13.316 33.3 3429 Industrial RB211-GT30 45. Industrial Trent 60 DLE 72.CTSSNET.5 12.820 6071 8590 36.7 6825 SGT-750 54.8 3429 (Continues) VECTRA 30G HS 31.150 6743 9540 21.7 4800 Industrial RB211 GT62 41.525 Energy Division legacy) SGT-300 (8 MW) 11.075 SGT-300 (9 MW) 12.299 7443 7853 13 3780 149 SGT-600 33.3 3570 Industrial Trent 60 WLE 82.9 13.151 33.8 9975 SGT-400 (15 MW) 20.1 3570 Industrial RB211-GT30 DLE 44.210 5837 8260 34.6 4850 Industrial RB211 GT 61 45.006 14.230 32.950 6599 9340 22. includes Siemens legacy and Rolls-Royce SGT-200 10.6 4800 Industrial RB211 G62 39.9 9975 SGT-500 25.009 6122 6459 24.466 6816 9644 18 6200 WWW.NET CTSS .376 33.994 41.0 4800 Industrial RB211 GT 61 DLE 44.990 6306 8920 21.075 29.918 6908 7288 18.948 14.469 23.847 25.240 7344 7738 14 8085 SGT-700 45.881 19.075 SGT-400 (13 MW) 18.8 12.216 8364 7256 7655 13.679 54.650 (Part of Siemens Power & Gas Division.3 6405 Industrial RB211 G62 DLE 37.091 6541 6901 22.877 61.650 6602 9340 21.3 4800 Industrial RB211 GT62 DLE 41.428 7028 9943 16.3 11.465 27.242 33. MECHANICAL DRIVE GAS TURBINES 2017 Basic Specifications 2017 EDITION Manufacturer Heat Rate Continuous Output At ISO Conditions Catalog Page Reference Maximum Output Shaft Speed (rpm) Model Number Pressure Ratio bhp kW Btu/hph kJ/kWh DRESSER-RAND BUSINESS * SGT-100 7640 5700 7738 10.300 7684 7616 8035 12.950 6819 9650 20.669 6661 7027 18.495 30.388 9238 7142 7535 14.737 6516 6875 22.800 6299 8910 22.084 30. 500 6877 0 19 7800 PGT20 23.871 6776 9589 18 3600 VECTRA 40G 42.660 23.520 29.395 6347 8980 22 6200 DR-61GP 42.535 7647 0 12 5111 WWW.369 6440 9114 23 3600 VECTRA 40G4 45. LM6000PD 58.892 7400 0 16 6500 PGT25 31.102 31.553 33.436 44.288 33.NET CTSS .395 33.902 34.229 6316 8936 24 6200 DR-61G4 45.962 32.969 8413 0 11 4670 MS5002(E) 45.380 43.609 6992 0 18 6500 PGT25+ 42.470 8714 0 9 4670 MS5002(D) 45.127 16. MECHANICAL DRIVE GAS TURBINES 2017 Basic Specifications 2017 EDITION Manufacturer Heat Rate Continuous Output At ISO Conditions Catalog Page Reference Maximum Output Shaft Speed (rpm) Model Number Pressure Ratio bhp kW Btu/hph kJ/kWh DRESSER-RAND BUSINESS * DR-61G 32.500 GE10-2 16.CTSSNET.809 43.852 6433 9104 23 3600 DR-63G PC 59.065 31.068 11.822 49.835 0 15 12.590 6992 0 23 6100 * This company is not represented in the 2017 Supplement with a section describing its products.982 7649 0 16 7900 NovaLT16 22.830 6054 8566 30 3743 150 KG2-3G 2682 2000 9978 14.118 7 1800 GE OIL & GAS * NovaLT5-2 7510 5600 10.037 6348 0 22 6100 PGT25+G4 46.855 6075 0 29 MS5002(C) 39.772 6884 0 17 5714 (Continues) MS6001(B) 58.322 6042 8549 28 3600 DR-63G PG 66.994 17.385 34.011 23. 348 6368 0 23 6100 LM6000PF (15ppm) 58.700 7955 11.590 15 12.700 7270 10.430 14.130 8300 7665 10.080 10.250 13. MECHANICAL DRIVE GAS TURBINES 2017 Basic Specifications 2017 EDITION Manufacturer Heat Rate Continuous Output At ISO Conditions Catalog Page Reference Maximum Output Shaft Speed (rpm) Model Number Pressure Ratio bhp kW Btu/hph kJ/kWh GE OIL & GAS * MS7001(EA) 115.787 5890 0 32 3930 LMS100-PB 131.682 31.0 5200 UGT25000 (DU80) 34.593 7031 0 18 6500 PGT25+ 42.5 5000 UGT25000 (DN80) 35.300 5960 0 32 3930 151 LM6000PG 70.845 16.500 8370 11.840 10 9450 THM 1304-12N 16. 139 MGT6200 9250 6900 7480 10.000 7070 10. 201 MFT-8 35.400 16.638 23.800 26.818 54.828 6363 0 22 6100 PGT25+G4 46.681 98.5 3700 * This company is not represented in the 2017 Supplement with a section describing its products.787 52.518 8.630 86.142 7348 0 13 3000 PGT25 31.910 26.520 130.061 34.400 WWW.NET CTSS .227 7718 0 13 3600 M9001(E) 174.555 5687 0 42 3428 GTR & PC "ZORYA-MASHPROEKT" * UGT6000 (DT71) 8715 6500 8080 11.0 8200 UGT8000 (DT70) 11.320 11 9450 MITSUBISHI 127.400 16.285 19.196 7580 0 40 3428 LMS100-PB+ 148.8 5000 ASE-40 3038 2265 10.870 26.CTSSNET.254 110.6 8200 UGT15000 (DG90) 22. MAN DIESEL & TURBO SE 138.760 12.855 5917 0 28 3600 LM6000PF+ 72.5 5200 UGT16000 (DJ59L2) 22.700 6975 9865 21.500 8000 11.809 43.600 (OBERHAUSEN) THM 1304-10N 14.4 15.780 6582 9313 20.259 14.000 21. 5 1800 CNT-2002M 1972 1471 11.999 15.2 1800 SOLAR TURBINES INC.300 * This company is not represented in the 2017 Supplement with a section describing its products.896 16.885 18.1 7000 Titan 130 22.123 22.NET CTSS .3 15.5 1800 CNT-5401M 5322 3970 11. Titan 250 30.835 7.771 16.169 8.860 7395 10.718 7.000 22.1 1800 CNT-1001MR 1065 794 12.300 WWW.770 7020 9930 16.250 12.1 8855 Mars 100 15.360 14.CTSSNET.5 11.3 9500 Taurus 70 11.000 10.370 6360 9000 24.6 1800 CNT-1301M 1331 993 12.586 9.015 15. * CNT-401MR 400 298 16. Centaur 50 6130 4570 8485 12.2 1800 CNT-1601M 1598 1192 11.830 16.465 17.833 7.500 Saturn 20 1590 1185 10. MECHANICAL DRIVE GAS TURBINES 2017 Basic Specifications 2017 EDITION Manufacturer Heat Rate Continuous Output At ISO Conditions Catalog Page Reference Maximum Output Shaft Speed (rpm) Model Number Pressure Ratio bhp kW Btu/hph kJ/kWh NIIGATA POWER SYSTEMS CO.870 10.657 8.618 17.3 16.6 1800 CNT-2601M 2662 1986 11.2 1800 152 CNT-3101M 3194 2383 11.500 Centaur 40 4700 3500 9100 12.150 8320 7190 10.605 Taurus 60 7700 5740 7950 11.898 16.490 16.900 11.5 1500 CNT-2001M 2130 1589 11.7 22.1 9500 Prime Movers Tab Mars 90 13.220 9860 7655 10.1 1800 CNT-601MR 665 496 16.000 22.814 4.170 16.814 16.2 1800 CNT-4101M 4259 3177 10.655 6.564 8.854 8.640 4.232 7.427 16. LTD.2 14. K 450 12.000 500 75.525 100 25.35 3500 1 2600 X X SF 28 940 65 950 510 Various Various 900 12.000 200.000 100.000 SDFC 5000 100.000 MP 1000 45.000 X E/I SF 2030 140 1050 565 400 180 3000 15.000 SC 2000 100.000 X X E/I SF/DF 4 2000 138 1015 546 640 147 2000 13.000 X I SF 2030 140 1050 565 400 180 3000 15.000 P 500 6000 X E/I SF 1160 80 900 480 3000 15.200 153 MYR 14. B.000 X E/I SF 2030 140 970 520 3000 12.000 X X E.000 C 500 6000 X E/I SF 1160 80 900 480 3000 15. 192 E.000 100.000 10.320. I SF 100 2000 138 1050 566 1.000 (Part of Siemens Power & Gas Multistage Division) Engineered 1.000 X DF 435 30 570 300 660 100 3000 16.000 X X E.000 750 18.000 336 8950 X X SF/DF 3 950 65 950 510 63 29 2000 18. Q. N 750 140.000 750 14.000 X E/I SF 2030 140 970 520 3000 12.000 Single Stage Engineered 670 100.35 4000 1 3000 X X SF 25 2000 138 1000 538 220.000 Single Stage Standard 1.000 500 15.CTSSNET.000 SANC 2000 100. 115.000 X I SF 2030 140 1050 565 400 180 3000 15.NET CTSS .000 GE OIL & GAS * SNC 2000 100.000 670 104.000 A5/A9 20.400 X X E SF 5 900 62 950 482 40 18 500 8500 Third Cover.000 600.000 Multistage ELLIOTT GROUP YR 1 3500 1 2600 X X SF 5 1500 103 1000 538 34 15 500 7100 R.000 X E/I SF 2030 140 1050 565 400 180 3000 15. MC 1000 45. I SF 25 915 63 950 510 441.000 WWW.000 SAC 2000 100. MECHANICAL DRIVE STEAM TURBINES 2017 Basic Specifications Cycle Frame Type Configuration 2017 EDITION Manufacturer Output Range Speed Range (rpm) Maximum Inlet Temperature Maximum Steam Flow Maximum Inlet Steam Pressure hp kW SF = Single Flow DF = Double Flow Condensing Back Pressure E = Extraction I = Injections Catalog Page Reference Model Type Number Frame Sizes min max min max PSI bar °F °C lb/s kg/s min max DRESSER-RAND BUSINESS * Standard 135 33.000 X SF 2030 140 1050 565 400 180 3000 3600 * This engine builder is not represented in the 2017 Supplement with a section describing its products. I SF/DF 3 1900 131 932 530 1500 1800 WWW.000 50.000 X E.000 X I DF 4 435 30 750 400 15. I SF 2030 140 1004 540 500 225 16. MECHANICAL DRIVE STEAM TURBINES 2017 Basic Specifications Cycle Frame Type Configuration 2017 EDITION Manufacturer Output Range Speed Range (rpm) Maximum Inlet Temperature Maximum Steam Flow Maximum Inlet Steam Pressure hp kW SF = Single Flow DF = Double Flow Condensing Back Pressure E = Extraction I = Injections Catalog Page Reference Model Type Number Frame Sizes min max min max PSI bar °F °C lb/s kg/s min max MAN DIESEL & TURBO SE 138.000 X E.NET CTSS .300 2000 80.000 X X E.000 X E SF 10 2060 142 1040 560 485 220 2600 19.000 X E/I SF/DF 7 1885 130 1004 540 14.000 1000 160.000 67.300 2000 80.000 MITSUBISHI HEAVY 127. I SF.000 BL or BH 2700 107. I SF 2030 140 1004 540 500 225 16.000 67.000 X I SF 10 2060 142 1040 560 183 83 2600 19.500 SST-300 45. DF 2465 170 1050 565 660 300 20. I SF 1 1595 110 970 520 10.500 MITSUBISHI 127. SST-600 200. INDUSTRIES COMPRESSOR 201 201.000 X X E.300 2000 80.000 X E/I SF 6 1885 130 1004 540 16.500 (OBERHAUSEN) 139 DK 1342 215.000 50.000 2000 120.000 * This engine builder is not represented in the 2017 Supplement with a section describing its products.000 201 MXL or MXH 2700 107.500 23. I SF 2 1740 120 1004 540 12. EBL or EBH 2700 107.000 50. I SF Modular 2395 165 1049 565 3000 18.000 SST-060 6000 X X SF 3 1900 131 986 530 10.CTSSNET.000 B 67.000 SST-110 8000 X X E.000 154 INTERNATIONAL SHIN NIPPON * C 67.000 SIEMENS * SST-200 10.000 X SF 10 2060 142 1040 560 368 167 2600 25.000 SST-500 100.000 150.000 X X E. DG 1342 215.000 14.000 EL or EH 2700 160.600 SST-050 750 X SF 2 1465 101 932 500 4500 10.000 50.000 X E SF 10 2060 142 1040 560 368 167 2600 25.000 X X E.000 1000 160. 60 Y 98 Y A/A HKH (IC7A0W7) 355 560 130 2500 2 to 8 11 IM 50. 60 Y 1 5000 98 1 N A/A A/W O (Continues) NTG 450 1600 1500 8000 2 to 12 3 11 IM N/A Y 1 3600 98 1 N A/W WWW. F3 355 560 500 2500 2 to 12 3 11 IM 50.000 2 3 14 IM 50.000 2 to 30 3 14 IM 50. 60 Y 98 Y A/A HKL (IC611) 500 1250 400 16. 60 Y 98 Y A/W HRM Slip Ring 500 1250 500 20. 60 Y 98 Y GE POWER CONVERSION * FL 280 450 200 800 2 to 8 3 11 IM 50.4 1 IM 50.CTSSNET. 60 Y 1 3600 98 1 Y R N3 450 1600 500 40. 60 Y 0 3000 Y W HKM (IC81W ) 450 1250 300 35. 4.000 2 to 8 15 IM 50. 60 Y 1 3600 98 1 N A/A A/W O N1 630 1250 4000 20.NET CTSS .000 2 to 24 15 IM 50. 60 98 Y A/W Special Motors 355 1400 35. ELECTRIC MOTORS 2017 Basic Specifications Cooling 2017 EDITION Manufacturer VFD Operation Motor Type Frame Size Voltage Range (kV) Poles Speed Range For VFD Operation Explosion Proof Available Output Range (kW) Frequency Hz A/A=Air/Air A/W=Air/Water R=Rib-Coated O=Open Catalog Page Reference Model Designation Motor Efficiency (%) At Rated Operating Point Normal Power Factor (cos Phi) At Rated Operating Point min max min max (2.000 2 to 30 15 IM 50.000 2 to 24 15 IM 50. SM) (50. 60 Y 98 Y W MKH (IC7A0W7) 200 630 37 2500 2 to 10 0. 6) min max (IM. 60) (Y/N) min max (Y/N) BALDOR * QR-25 3 to 25 HP 182 284 3 18 4 200 575 60 N 89 85 Y A/A QT 3 to 15 HP 182 254 3 11 4 200 575 60 N 89 85 Y A/A QTS 1 to 5 HP 143 184 1 4 4 208 230 60 N 89 85 Y A/A QRDS 5 to 30 HP 184 286 4 22 4 200 575 60 N 89 85 Y A/A QRDT 5 to 30 HP 184 286 4 22 4 200 575 60 N 89 85 Y A/A ELIN MOTOREN GMBH * HKG (IC411) 355 560 200 2200 2 to 18 11 IM 50. 60 Y 1 3600 97 1 N R * This company is not represented in the 2017 Supplement with a section describing its products. 60 Y 1 5000 98 1 N A/A A/W O AKG 355 560 200 1800 2 to 12 3 11 IM 50. 60 Y 98 Y R 155 HKR (IC511) 710 1250 400 8000 2 to 24 15 IM 50. 60 Y 3600 Y R.000 100.8.8 IM/SM 50. SM) (50. A/W. W.000 2 6 11 SM N/A Y 500 6500 99 1 N A/W MGV 450 800 1500 20. 6) min max (IM. 4.000 ANY 2 13 IM 50. TEAAC. * JS2000 355 710 630 5000 2 to 12 3 6 IM 50.600 18. WPII. TEWAC WWW.000 97.8.6. TEWAC TEFC.6. WPII. TM21-G 315 900 110 23. 60) (Y/N) min max (Y/N) GE POWER CONVERSION * MS 800 1600 7500 50. TEWAC TEFC.000 2.000 15.10 3 13.10 3 13.000 2 3 9 IM N/A Y 3. SM 50.8 IM 50.000 100.000 2. TM21-H 315 1200 110 25.5 0. 60 Y 3.89 Y TEAAC.000 4 to 30 3 14 SM 50.NET CTSS .000 2. 60 Y 1 3600 97. 60 Y 1 3600 97. O Specialized Series TOSHIBA MITSUBISHI-ELECTRIC * High-Speed Custom 315 1200 500 80. TEWAC INDUSTRIAL SYSTEMS CORP.4. 60 Y 5 60 95 90 Y A/A.CTSSNET. 60 Y 1 1800 98 1 N A/A A/W O TM 1000 1800 15.4. 60 Y 5 60 95 90 Y R SIEMENS AG * SIMOTICS HV 156 315 1000 150 7000 2.5 0. 60 Y 1 3600 97.4.6.8. O High Power Series SIMOTICS HV 100.10 3 13.8. SM 50. 60 Y 15. ELECTRIC MOTORS 2017 Basic Specifications Cooling 2017 EDITION Manufacturer VFD Operation Motor Type Frame Size Voltage Range (kV) Poles Speed Range For VFD Operation Explosion Proof Available Output Range (kW) Frequency Hz A/A=Air/Air A/W=Air/Water R=Rib-Coated O=Open Catalog Page Reference Model Designation Motor Efficiency (%) At Rated Operating Point Normal Power Factor (cos Phi) At Rated Operating Point min max min max (2.5 0. R.6. A/W.8 IM/SM 50.4. 60 Y 3600 Y A/A.89 Y TEAAC.5 0. O Modular Series SIMOTICS HV 900 1600 70.000 ANY 2 13 IM 50.000 98 1 N INTEGRATED HITACHI LTD. A/W. (TMEIC) High-Power Custom 315 1200 10.10 2 11 IM 50. O JF2000 250 500 55 2250 2 to 12 3 6 IM 50.900 Y A/A. A/W.000 2 3 13 IM. 60 Y 4800 Y A/A.000 ANY 3 13 IM.89 Y TEAAC. W Comapct Series SIMOTICS HV 315 800 280 19.89 Y * This company is not represented in the 2017 Supplement with a section describing its products. 2 300 24 Pulse VSI 3 Level Diode IGBT IM or SM W MV7615 9000 5. MV7927 27.300 3.0 300 36 Pulse VSI 3 Level Diode IGBT IM or SM W MV7927 AFE 27.000 10.3 300 24 Pulse VSI 3 Level Diode IGBT IM or SM A MV7312 AFE 13.800 3.3 300 AFE VSI 3 Level IGBT IGBT IM or SM A 157 MV7315 15.CTSSNET. VARIABLE SPEED DRIVES 2017 Basic Specifications 2017 EDITION Rectifier Type Drive Type Manufacturer Step Number Of Inverter Output Cooling Semiconductors Motor Type Output Range (kW) (VSI.6 300 AFE VSI 3 Level IGBT IGBT IM or SM W MV7821 21.3 300 AFE VSI 3 Level IGBT IGBT IM or SM A MV7607 7000 5.000 10. (6.9 100 12 Pulse LCI 6 Pulse Thyristor Thyristor SM A WWW.400 6.6 300 AFE VSI 3 Level IGBT IGBT IM or SM W MV7616 15. AFE) LCI) Pulse System) Rectifier Inverter (IM.0 300 3 x 36 Pulse VSI 7 Level Diode IGBT IM or SM W SD7104FA66 4000 1.000 6.000 10.000 3. SM) W=Water GE POWER CONVERSION * MV7303 3800 3.000 10.300 3. 12. (6.3 300 AFE VSI 3 Level IGBT IGBT IM or SM W MV7310 10. CSI.3 300 24 Pulse VSI 3 Level Diode IGBT IM or SM A MV7315 AFE 13.000 8.2 300 24 Pulse VSI 3 Level Diode IGBT IM or SM W MV7609 10.NET CTSS .0 300 36 Pulse VSI 3 Level Diode IGBT IM or SM W * This company is not represented in the 2017 Supplement with a section describing its products. Motor Voltage (kV) Model Designation Max.12. 24.6 300 24 Pulse VSI 3 Level Diode IGBT IM or SM W MV7609 AFE 8000 6. Output Frequency (Hz) Catalog Page Reference min max 36 Pulse. 24 A=Air Max. 18.3 300 AFE VSI 3 Level IGBT IGBT IM or SM W MV7306 6900 3.3 300 12 Pulse VSI 3 Level Diode IGBT IM or SM W MV7310 AFE 8800 3.0 300 2 x 36 Pulse VSI 5 Level Diode IGBT IM or SM W 3xMV7927 81.6 300 24 Pulse VSI 3 Level Diode IGBT IM or SM W MV7618 18.5 100 6 Pulse LCI 6 Pulse Thyristor Thyristor SM A (Continues) SD7308FAC6 8000 2.0 300 AFE VSI 3 Level IGBT IGBT IM or SM W 2xMV7927 54.300 3.3 300 AFE VSI 3 Level IGBT IGBT IM or SM W MV7312 13.000 6.3 300 12 Pulse VSI 3 Level Diode IGBT IM or SM W MV7303 AFE 3800 3.300 6.000 10.3 300 12 Pulse VSI 3 Level Diode IGBT IM or SM W MV7306 AFE 6900 3.2 300 36 Pulse VSI 3 Level Diode IGBT IM or SM W MV7913 13.6 300 24 Pulse VSI 3 Level Diode IGBT IM or SM W MV7618 AFE 14. 000 4.9 100 12 Pulse LCI 6 Pulse Thyristor Thyristor SM A SD7425WFCC 25.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4402-25 2000 4.0 100 12 Pulse LCI 12 Pulse Thyristor Thyristor SM W SD71280WFCC 80. MV4403-30 2250 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4404-50 3750 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4402-20 1500 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4401-04 300 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4403-35 2500 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4403-40 3000 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4402-15 1100 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4404-45 3250 4.8 100 12 Pulse LCI 6 Pulse Thyristor Thyristor SM A SD7625FAC6 25.000 11.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4401-08 600 4. 24.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A * This company is not represented in the 2017 Supplement with a section describing its products.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4401-07 500 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4401-06 450 4. 24 A=Air Max. 12.4 100 12 Pulse LCI 12 Pulse Thyristor Thyristor SM W SD7860WFCC 60.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4401-12 1000 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4402-17 1300 4. AFE) LCI) Pulse System) Rectifier Inverter (IM.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4401-09 650 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A 158 MV4401-05 375 4. SM) W=Water GE POWER CONVERSION * SD7615FAC6 15.0 100 12 Pulse LCI 12 Pulse Thyristor Thyristor SM W MV4401-03 250 4. VARIABLE SPEED DRIVES 2017 Basic Specifications 2017 EDITION Rectifier Type Drive Type Manufacturer Step Number Of Inverter Output Cooling Semiconductors Motor Type Output Range (kW) (VSI. (6.CTSSNET.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A MV4401-10 750 4.1 90 AFE VSI 5 Level IGBT IGBT IM or SM A (Continues) MV6601-03 385 6. Output Frequency (Hz) Catalog Page Reference min max 36 Pulse.000 5.000 8. CSI.000 11.12.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A WWW. (6.NET CTSS . Motor Voltage (kV) Model Designation Max. 18.000 5.4 100 12 Pulse LCI 12 Pulse Thyristor Thyristor SM W SD7640WFCC 40. (6.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6603-22 2200 6. (6. Motor Voltage (kV) Model Designation Max. 12.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6603-16 1650 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6603-27 2750 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6606-30 3025 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6606-33 3300 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6603-22 2200 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6601-05 550 6. SM) W=Water GE POWER CONVERSION * MV6601-03 385 6. AFE) LCI) Pulse System) Rectifier Inverter (IM.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6603-24 2475 6.12.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6601-10 1100 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6601-08 825 6.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6606-38 3850 6.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6606-30 3025 6. 24 A=Air Max. MV6606-33 3300 6.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6603-13 1375 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6603-19 1925 6.CTSSNET. 24. CSI.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6603-27 2750 6.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6601-05 550 6.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A WWW.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6601-08 825 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6606-38 3850 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6603-24 2475 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A 159 MV6603-16 1650 6.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A (Continues) MV6606-44 4400 6. 18. Output Frequency (Hz) Catalog Page Reference min max 36 Pulse.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6606-44 4400 6.NET CTSS .6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6601-10 1100 6.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A * This company is not represented in the 2017 Supplement with a section describing its products. VARIABLE SPEED DRIVES 2017 Basic Specifications 2017 EDITION Rectifier Type Drive Type Manufacturer Step Number Of Inverter Output Cooling Semiconductors Motor Type Output Range (kW) (VSI. SM) W=Water GE POWER CONVERSION * MV6606-49 4950 6.800 3300 140 12p. W Silcovert GN 7800 20. 24 A=Air Max. 24p.900 3300 100 12p. 18. 12. SM W 160 Silcovert TH 400 21. Output Frequency (Hz) Catalog Page Reference min max 36 Pulse.000 N/A Mechanical N/A N/A N/A IM.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6606-55 5500 6. SM A.12. W Planetary Gear pos. SM A. W VOITH TURBO 113 Any Variable Speed motor Motor is operated 1000 50. AFE LCI 6. AFE VSI 6 Diode/IGBT IGBT IM A. VARIABLE SPEED DRIVES 2017 Basic Specifications 2017 EDITION Rectifier Type Drive Type Manufacturer Step Number Of Inverter Output Cooling Semiconductors Motor Type Output Range (kW) (VSI. 30p. SM A.CTSSNET. 12 Thyristor Thyristor SM A.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A NIDEC ASI * Silcovert TN 1100 18. CSI.000 6600 95 6p. direct online sible Any Geared Variable motor Motor is operated 1000 30. 36p VSI 6 Diode IGBT IM.NET CTSS . 24p. 24. 24p. direct online sible Any * This company is not represented in the 2017 Supplement with a section describing its products. (6.200 7200 300 18p. W Silcovert NH 1300 23. Motor Voltage (kV) Model Designation Max. (6.000 N/A Mechanical N/A N/A N/A IM. motor Motor is operated Variable Speed Coupling 100 10.000 N/A Mechanical N/A N/A N/A IM. W Speed Coupling pos. SM A. AFE VSI 6 Diode/IGBT IGBT IM. 12p. AFE) LCI) Pulse System) Rectifier Inverter (IM. direct online sible WWW.6 75 36 Pulse VSI 5 Level Diode IGBT IM or SM A MV6606-49 4950 6. 24p. W pos.800 6600 140 36p VSI 6 Diode IGBT IM. SM A. W Silcovert S 1500 45.6 75 AFE VSI 5 Level IGBT IGBT IM or SM A MV6606-55 5500 6. 26 WWW. Ft.NET CTSS .CTSSNET. Compressor Horsepower Selection Chart (Brake Horsepower Per Million Cu.) 2017 EDITION DISCHARGE PRESSURE (PSIG) 25 50 75 100 125 150 175 200 250 300 350 400 450 500 550 600 650 700 750 800 850 900 950 1000 1050 1100 1150 1200 0 65 99 128 144 156 168 178 187 203 218 233 233 241 248 254 260 266 272 277 282 286 291 295 299 303 307 311 315 3 10 35 63 85 104 121 131 140 149 163 175 186 196 205 214 223 231 228 233 237 242 245 250 253 257 260 264 267 270 20 43 62 78 92 106 118 126 139 151 160 170 178 186 193 199 206 212 218 225 231 226 229 232 236 239 242 245 STAGE 30 29 47 62 74 85 96 107 123 133 143 152 159 167 173 179 185 191 196 201 206 211 216 221 226 230 224 227 40 36 50 61 72 81 90 107 121 130 138 145 152 158 164 170 175 180 185 190 194 198 202 206 210 214 218 50 26 41 52 61 70 78 93 106 119 127 134 141 147 153 158 163 168 173 177 181 185 189 193 196 200 203 60 32 44 53 61 69 83 95 108 118 125 131 137 143 148 153 158 162 166 170 174 178 182 185 188 192 70 25 37 46 54 61 74 86 97 109 117 123 129 135 140 145 149 153 157 161 165 169 172 176 179 182 80 30 40 47 54 67 78 89 98 109 117 122 127 132 137 142 146 150 153 157 161 164 167 171 174 2 90 24 34 42 49 61 72 81 91 100 109 116 121 126 131 135 139 143 147 150 154 157 160 163 166 100 28 37 44 55 66 75 84 92 100 109 116 120 125 129 133 137 141 144 148 151 154 157 160 STAGE 125 25 32 44 54 63 71 78 85 92 99 106 113 117 121 124 128 131 134 137 140 143 146 161 150 22 35 45 53 60 67 74 80 86 92 98 103 110 114 118 121 124 127 130 133 135 175 27 37 45 52 57 60 71 76 82 87 92 97 102 107 112 115 118 121 123 126 200 30 38 45 52 58 63 68 73 78 83 88 92 96 101 105 110 113 116 119 250 26 33 40 46 51 56 60 65 69 73 77 81 85 88 92 95 99 102 SUCTION PRESSURE 300 23 30 36 41 46 50 54 58 62 66 69 73 76 79 83 86 89 350 21 27 33 38 42 46 50 53 57 60 63 67 70 73 75 78 400 25 30 35 39 43 46 50 53 56 59 60 64 67 70 450 23 28 32 36 40 43 46 49 52 55 58 60 63 1 500 22 26 30 34 38 41 44 46 49 52 54 57 550 20 25 20 32 36 39 41 44 46 49 51 STAGE 600 23 27 30 34 37 39 42 44 46 650 22 26 29 32 35 38 40 42 700 22 25 28 30 33 36 38 750 20 24 27 29 32 34 NOTE: 1 MMSCFD MEASURED 14.7 AND 60°F 3 SUCTION TEMPERATURE 100°F NOT CORRECTED FOR COMPRESSIBILITY 4 NATURAL GAS 2 “N”=1. A multi-stage turbine uti- • Internal combustion engines lizes either a Curtis or Rateau first stage followed by one or Special considerations for the use of prime movers as drives more Rateau stages. psi sf = specific entropy of saturated water. including: In a single-stage turbine.org. and speeds. lb/hr S = piston stroke. steam is accelerated through one cascade of stationary nozzles and guided into the rotating • Steam turbines blades or buckets on the turbine wheel to produce power. Oklahoma 15 74145. Hz TSR = theoretical steam rate. They offer the highest overall turbine pressure to operate over a range of speeds in contrast to a turbine used to ratio for a given set of inlet conditions and therefore require the drive an electric generator which runs at nearly constant speed. a single-stage turbine will have a lower capi- for compressor.TECH BRIEF The following section covering Prime Movers has been reproduced. Btu/(lb • °F) BMEP = brake mean effective pressure. 15-4). Btu/lb ρ = density. A cooling me- Significant hardware differences exist between these two ap. 13th edition published by the Gas Processors Suppliers Association. 6526 East 60th Street. For a given Mechanical drive steam turbines are major prime movers shaft horsepower. blower. sq in. plications. Single-stage turbines are usually limited to about 2500 horsepower although special designs are available for larger STEAM TURBINE TYPES units.gpaglobal.CTSSNET. because of the lower efficiency of the single-stage turbine. www. lb/(hp • hr) s = specific entropy of superheated steam. by permission. A Ra- • Gas turbines teau design has one row of buckets per stage (Fig. Only variable speed process drivers will be covered Non-condensing or back-pressure turbines exhaust steam at here. The complete Engineering Data Book can be ordered SECTION from GPSA. dium is required to totally condense the steam. in. Btu/lb v = velocity.NET CTSS 15-1 . and pump applications. Typical ranges for each design parameter are: Inlet Pressure. ft f = frequency. 15-1 Nomenclature N = number of power strokes per min A = area. Steam is extracted from. Prime Movers Prime MoversFor ForMechanical Drives Mechanical Drives “Prime movers for mechanical drives ” is a common term Single Stage/Multi-Stage for machines made for transferring mechanical energy to pumps and compressors. psig saturated – 700 through the turbine is a function of the overall turbine pressure Horsepower 5 – 100. horsepower. lb/cu ft hg = specific enthalpy of saturated steam. Steam turbines tal cost but will require more steam than a multi-stage turbine are available for a wide range of steam conditions. 15-2). 15-3). An uncontrolled turbine accepts or pro- vides steam based only on the characteristics of the steam sys- FIG. P = number of magnetic poles in motor ASR = actual steam rate. ft/sec hf = specific enthalpy of saturated water.000 Condensing turbines are those whose exhaust pressure is below Steam turbines used as process drivers are usually required atmospheric. Admission or extraction units may be either con- trolled or uncontrolled. the turbine at some point between the inlet and exhaust • Impulse or reaction (Fig. psig 30 – 2000 Condensing/Non-Condensing Inlet Temperature. • Single-stage or multi-stage Extraction/Admission • Condensing or non-condensing exhausts Some mechanical drive steam turbines are either extraction or admission machines. Btu/(lb • °F) D = diameter. lb/(hp • hr) h = specific enthalpy of superheated steam. °F saturated – 1000 The energy available in each pound of steam which flows Exhaust Pressure. Btu/lb 2017 EDITION 162 WWW. Btu/(lb • °F) F = steam low. A Cur- tis design has two rows of buckets per stage and requires a set • Electrical motors of turning vanes between the first and second row of buckets to redirect the steam flow (Fig. pressures above atmospheric and are usually applied when the Mechanical drive steam turbines are categorized as: exhaust steam can be utilized elsewhere. Tulsa. for generators are not included in this chapter. rpm 1800 – 14. from the Engineering Data book. Below 2500 horsepower the choice between a single and a multi-stage turbine is usually an economic one. Speed. or admitted • Extraction or admission to. lowest steam flow to produce a given horsepower.000 ratio (inlet pressure/exhaust pressure) and inlet temperature. sg = specific entropy of saturated steam. stationary nozzle. maximum inlet velocities are usually limited to 150 ft/ design concepts: impulse and reaction.S. in general. 15-3 Rateau Design Curtis Design tem to which the extraction or admission line is connected. the pressure drop per stage is divided equally between the stationary nozzles and the Inlet Control Valves rotating blades (Fig. For given horsepower. trip-and-throttle valve can be used to modulate the steam flow bine is used. In reaction designs. a controlled extraction (or admission) tur. if the horsepower associated with the fully open and its primary function is to shut off the steam extraction or admission flow is greater than 15% of the total supply in response to a trip (shutdown) signal. a reaction turbine will. In general. speed and The primary function of the inlet control valve(s) is regula- steam conditions. During normal operation this valve remains valve steam turbines will have from three to eight control valves 15-2 2017 EDITION 163 WWW. may be posi. A controlled turbine will control the flow of extraction or admis- sion steam based on some process measurement such as pres- sure or flow. Multi-stage turbines may have a single inlet control valve or tioned between the steam supply and the turbine inlet control several control valves to regulate the inlet steam. A trip-and-throttle valve or stop valve. These valves may also close in response to a shut- in the same turbine span. turbines with large pressure ratios suffer smaller efficiency losses than tur- Trip and Throttle Valve/Stop (Block) Valve bines with smaller pressure ratios (Fig. For a given amount of throttling. reduces the thermal performance of the turbine. In an impulse turbine sec. tion of the steam flow to provide the appropriate horsepower proximately three times more stages than an impulse turbine and speed. during start-up and can be either manually or hydraulically positioned from zero lift to 100% lift.CTSSNET. 15-2 FIG. to minimize the pressure drop through the trip-and-throttle ployed in the steam path design and are divided into two major valve. 15-7). In order Turbines are further categorized by the philosophy em. or both. Most U. Velocities above this level will usually result in high pres- the pressure drop for the entire stage takes place across the sure drops which will reduce turbine efficiency. 15-6). employ ap. TECH BRIEF FIG.NET CTSS . The stop valve can only be Impulse/Reaction positioned either in the closed or fully open positions. In addition a turbine horsepower. Throttling which occurs across the control valve(s) turbines are of the impulse type. mechanical drive steam down signal. Typical multi- valve(s) (Fig. 15-5). This efficiency loss is a function of the control valve design and overall turbine STEAM TURBINE COMPONENTS pressure ratio. In these cases it is important to identify (Fig. TECH BRIEF FIG.NET CTSS . Most con- 15-3 2017 EDITION 164 WWW. 15-9). As the load on the unit is reduced one or both of these stage buckets (single flow. valves is incurring a throttling loss (Fig. Non-con- hand valves can be closed to reduce throttling loss. Multi-valve turbines have higher efficiencies at re- all blade resonance and to verify that all stresses are well below duced loads because only the flow through one of the control the material strength. triple flow).CTSSNET. although the design objectives remain the same. it is seldom possible to avoid all blade resonance because of the wide operating speed range. 15-6 Turbine Types Single Valve with Hand Valves Nozzles/Blades (Buckets) On constant speed turbines a design objective is to avoid all bucket resonances at the operating speed. For the turbine Turbine exhaust casings are categorized by pressure service shown in Fig. 15-4 Extraction/Admission Flow Turbines FIG. 15-6 both hand valves would be open at or near (condensing or non-condensing) and number of rows of the last full load. 15-10 densing exhausts are usually cast steel with most of the appli- shows the efficiency advantage at reduced loads. Turbines with a single control valve will often employ hand Exhaust Casings valves to improve efficiency at reduced loads. double flow. cations between 50 and 700 psig exhaust pressure. On variable speed turbines. 15-5 FIG. 15-8). Fig. improving the turbine efficiency and reducing Moisture Protection the impact erosion on the buckets. In addition. Maximum exhaust flange velocities are typically 450 ft/sec. can be used to remove a large percentage of the moisture. as the water is tems employed on mechanical drive turbines.NET CTSS . which are in.0 densing exhausts are steel fabrications although some utilize cast iron construction. the water droplets strike the sta. Stainless steel moisture As steam expands through the turbine both the pressure shields can also be used to minimize the impact erosion of the and temperature are reduced. sensed by a fly-ball governor with hydraulic relays providing tionary components. ternal to the turbine. non-condensing exhaust applications. moisture separators. also causing erosion. Velocities above this level will usually re- sult in substantial increases in exhaust hood losses and will decrease turbine efficiency. 15-7 FIG. tem was developed and utilized analog control circuitry with 15-4 2017 EDITION 165 WWW. Shaft speed is centrifuged from the blades. TECH BRIEF FIG. The water droplets which are formed strike the buckets Mechanical governors were the first generation control sys- and can cause erosion of the blades.0 FIG.CTSSNET. Where the moisture the input to the control valve. the steam crosses the saturation line thereby introducing moisture into the steam Control Systems path. 15-10 Single-Valve with Hand Valves Performance Characteristic (Typical Non-Condensing Turbine) Turbine Pressure Ratio = 8. 15-8 Multi-Valve Inlet FIG. 15-9 Loss in Available Energy of Steam due to 10% Throttling Multi-Valve vs Single-Valve Performance Characteristic (Typical Non-Condensing Turbine) Turbine Pressure Ratio = 8. On most condensing and some stationary components. A second generation control sys- content is greater than 4%. Inlet Pressure 600 psia tropic) process. isen. Efficiency can range from a low of Required Horsepower 6000 hp 40% for a low horsepower single-stage turbine to a high ap. The major advan. the back-up governor as. Determine: Techniques to Improve Efficiency • The actual steam rate (ASR). A microprocessor is used and the con. example. Part trol logic is programmed into the governor. There are numerous loss mechanisms which Inlet Temperature 750°F reduce the efficiency from the isentropic such as throttling loss- es. Operation at Part Load draulic relays with electronic circuit boards.. Using Figs. friction between the steam and the nozzles/ Exhaust Pressure 2 psia buckets. throttling losses. Speed 7000 rpm proaching 90% for a large multistage. isentropic exhaust the cost to produce steam over the life of the turbine. the number of stages utilized can range from the few. 15-11 through 15-19 and 24-30 and 24-31 allow esti- STEAM TURBINE EFFICIENCY mates to be made of steam rate. • The approximate number of stages. steam leakage. est possible to develop the load reliably to the thermodynami- cally optimum selection. Multi-Stage Condensing Turbines FIG. A third generation control system was developed and replaced the electronic cir. load efficiency varies as a function of speed. EXAMPLES Figs. 24-30 and 31. TECH BRIEF the fly-ball governor replaced by speed pick-ups and the hy. Most equipment driven by steam turbines are centrifugal cuitry with digital logic.CTSSNET. and the num- tage of this system is the ability to utilize two governors ber of stages. For • The inlet and exhaust nozzle diameters. FIG. and the inlet and exhaust nozzle diameters. Various techniques are employed to maximize turbine effi- ciency. By assuming horsepower to vary as the cube of simultaneously. etc. each capable of governing the turbine alone. each designed to attack a specific loss mechanism. percentage of the design efficiency (Fig. multi-valve turbine. Spill bands can be utilized to minimize • The steam rate at a partial load of 4000 hp and 6100 rpm. High efficiency nozzle/bucket profiles are available to reduce friction losses. Exhaust flow guides are Solution Steps available to reduce the pressure within the exhaust casing.NET CTSS . 15-11 Part Load Efficiency Correction Factor vs Percent Power Multi-Valve Steam Turbines 15-5 2017 EDITION 166 WWW. If speed the turbine part load efficiency can be approximated as a the primary governor incurs a fault. 15-12 Basic Efficiency of Multi-Valve.e.e. bearing losses. 15-11). The follow- Factors Affecting Efficiency ing examples illustrate the use of these figures: The objective of the steam turbine is to maximize the use of Example 15-1 — Given a steam turbine application with the the available steam energy where the available steam energy is following characteristics: defined as the difference between the inlet and exhaust ener- gies (enthalpies) for a 100% efficient constant entropy (i. turbine efficiency. flow. number of stages. the theoretical steam rate (TSR) The specific features employed on a given application are may be determined from the difference in the inlet enthalpy usually based on the trade-off between capital investment and and the theoretical exhaust enthalpy (i. sumes control of the turbine and provides diagnostic informa- tion to the operator. machines where horsepower varies as the cube of speed. 9200) x = 0.9200 Btu/(lb • °F). 24-30. Had sf = 0.6109 Btu/(lb • °F) pressure of 2 psia absolute.2 Btu/lb Substituting Btu = (hp • hr)/2544: Enthalpy change = (–444.8229 (vapor fraction in the exhaust) Exhaust enthalpy = (0.0 psia: exhaust-vapor entropy been equal to the inlet entropy.1750 Btu/(lb • °F) the exhaust-vapor entropy been below the inlet entropy. Fig.1750 and 1. sg = 1. TECH BRIEF enthalpy). 15-14) FIG. but first the inlet and exhaust states should be con. and equating the inlet and exhaust entropies: 1.NET CTSS . 24-31): °F). Had the Exhaust conditions at 2.1750) + (1 – x)(1. Since the inlet entropy is within h = 1379.8229)(1116.2 – 1379.2°F).e. 24-31 instead of 24-30 would be applicable.6109 = x (0. the ex- haust would be single-phase vapor (i. Multi-Stage Non-Condensing Turbines Letting x equal the liquid fraction in the exhaust.1771)(94. the as- sumed two-phase exhaust would have been incorrect and Fig. 15-14 FIG.729 (Fig.9200 Btu/lb • °F) hf = 94.4 Btu/lb this range.727 lb/(hp • hr) Basic efficiency = 0.2 Btu/lb Basic Efficiency of Multi-Valve. 24-31 for superheated steam indicates that the in- let is superheated (i.03 Btu/lb FIG. firmed.03) + (0..CTSSNET.4 = –444.2°F (first column Fig. the liquid and vapor entropies are 0.e. the theoretical exhaust must be two-phase. and gives an inlet entropy of 1.2) = 935. 24-31) Inlet superheat = 750 – 486 = 264°F Superheat efficiency-correction factor = 1. 15-15 Superheat Efficiency Correction Factor Superheat Efficiency Correction Factor for Condensing Turbines for Non-Condensing Turbines 15-6 2017 EDITION 167 WWW.2/2544) = (–1/5. 15-12) Inlet saturation temperature = 486. at its dewpoint). 750°F is above the saturation tempera.727)(hp • hr)/lb TSR = the absolute value of the inverse of the enthalpy change = 5.1771 1 – x = 0. From Fig.6109 Btu/(lb • values at 700°F and 800°F on Fig. Inlet conditions at 600 psia and 750°F (the average of the ture of 486. 15-13 hg = 1116.2 Btu/lb Enthalpy change = 935. for saturated steam at the turbine exhaust s = 1.03 (Fig. 97 lb/(hp • hr) between 1. = 47.CTSSNET.051) (47.43 lb/(hp • hr) (0. 15-12.03)(0.71) = 0.800 lb/hr Available Energy (theoretical)(i.43) = 33. 15-16) A 30 in. 15-16 Inlet Pressure 250 psig Speed Efficiency Correction Factor for Condensing Outlet Pressure 100 psig and Non-Condensing Turbines Inlet Temperature 500°F Horsepower 900 hp Speed 5000 rpm FIG.96) (0. Non-Condensing Turbines 15-7 2017 EDITION 168 WWW.3 in.e.051) (47. NPS (minimum) inlet nozzle would be selected.100 RPM and assuming A 4 in.73/0.729)(1.800) D= Nine stages would provide increased efficiency but at addi- (0. seven stages from Fig.719 The number of stages may be estimated using Fig.8 in.97 lb/(hp • hr) would be acceptable. TECH BRIEF Speed efficiency-correction factor = 0.051) (F) D= Eq 15-1 (1.0057 lb/ft3 @ 2 psia Actual Steam Rate = 5. At partial load of 4000 hp and 6.5 and 2 stages per 100 Btu/lb of available energy F = (6000 hp) 7. 15-17 Pressure Ratio Efficiency Correction Factor.96 is obtained.68 ρ = 0. 15-18.NET CTSS .68 = 8.957 (Fig. Corrected efficiency = (0. exhaust nozzle would be selected.800) F = (4000) (8. From Fig. ments for a multi-stage turbine and a single-stage turbine at the following conditions: FIG.. or. Efficiency = (0.0057) (450) (0.727/0. 15-11.2 Btu/lb Number of Stages (ρv) (0. Number of Stages ρ = 0.957) = 0.719 = 7. D = 4.88 lb/ft @ 600 psia and 750°F 3 (2) (444) = = 9 (approximately) (100) (0.5) (444) = = 7 (approximately) (100) A reasonable rule of thumb for maximum velocity of the in- let steam is 150 (ft/sec). the isentropic enthalpy change calculated above) The inlet and exhaust diameters may be estimated from the equation: = 444. a part load efficiency factor of ap- proximately 0.88) (150) tional cost.71.700 lb/hr D= Example 15-2 — Determine the ASR and total steam require- D = 30. is a reasonable rule of thumb.100 RPM is estimated to be 0. Drawing a horizontal line from the 7000 RPM indicates that ASR = 5. the basic effi- For exhaust sizing a maximum steam velocity of 450 ft/sec ciency at 4000 hp and 6. 99) (1.3 lb/(hp • hr) hf = 308.8 Btu/lb Efficiency-correction factor for speed = 1. TECH BRIEF Solution Steps TSR = the absolute value of the inverse of the enthalpy change = 33.99 (Fig. the turbine inlet is superheated.9 – 1261. and the exhaust is Inlet saturation temperature = 406.5 Btu/lb = 47.99 psia at 340°F. 15-13) Examining Figs.CTSSNET.5918) ASR = [75 lb/(hp • hr)] (0.7 psia: Efficiency-correction factor for pressure ratio = 0.0 °F (interpolating two-phase.01 (Fig.5873 = x (0.0041)(308.9/2544) = (–1/33.66) (0.97)] sg = 1.9959)(1189. 114.93) (Fig.7 psia)/(264.9 Btu/lb F = [52. 15-15) h = 1261. get the following for 114.0041 = 70 lb/(hp • hr) 1 – x = 0.5)(hp • hr)/lb) Single-Stage Application FIG. From Fig.7 psia). 24-31): Inlet superheat = 500 – 406 (Fig.433 interpolating linearly between 89. 15-18 Stages Required per 100 Btu/lb of Available Energy as a Factor of Normal Turbine Speed 15-8 2017 EDITION 169 WWW.9 Enthalpy change = 1185. 15-19) x = 0. 24-31) Inlet conditions at 250 psig (264.8 = –75.5 lb/(hp • hr) For a multi-stage turbine: Basic efficiency = 66% (Fig.3 lb/(hp • hr)] (900 hp) hg = 1189.01) (0.5918 Btu/(lb • °F) = 52. and equating the inlet and exhaust entropies: For a single-stage turbine 1.4872 Btu/(lb • °F) ASR = [33.100 lb/hr Letting x equal the liquid fraction in the exhaust. 15-17) sf = 0.e. 24-31) = 94°F s = 1.NET CTSS . between 260 and 280 psia on Fig.9) + (0.7 psia) = 0.97 (Fig. 24-30 Pressure ratio = (114.64 psia at 320°F and 117.9959 (fraction vapor in exhaust) F = [70 lb/(hp • hr)] (900 hp) Exhaust enthalpy = (0. 24-30 and 31 in the same way as in Exam- ple 15-1.000 lb/hr = 1185.7 psia) and 500°F (interpolat- ing linearly between 240 and 260 psia on Fig.5 lb/(hp • hr)]/[(0. 15-19 Enthalpy change = (–75.4872) + (1 – x) (1.5) = 63. 15-16) Exhaust conditions at 100 psig (i.5873 Btu/(lb • °F) Efficiency-correction factor for superheat = 0.9 Btu/lb Substituting 1 Btu = (hp • hr)/2544: FIG. General Installation Gas turbines are extensively used in all phases of the gas industry as a source of shaft power. the gas turbine requires a minimum of rou.000 hp tine maintenance. lightweight design of gas turbines makes them years the gas turbine has evolved into two basic types for high- ideally suited for offshore platform installations. as they became more efficient and durable. the heavy duty industrial gas turbine is normally rameters of the turbine (pressures. Where high power output is required. stationary use.). This can often be done by an operator at a location remote from the actual turbine installation. compact size. process. TECH BRIEF GAS TURBINES tion levels. • Minimal maintenance.CTSSNET. remote sites. The relatively light weight. 35. The industrial gas turbine has certain advantages FIG. GAS TURBINE TYPES • Short installation time. The gas turbine was first widely used as an aircraft power Compact. The main advantages of gas turbines must be quickly installed in the field. specified. and above. However. temperatures. Heavy Duty Maintenance The industrial type gas turbine is designed exclusively for Once installed. The gas turbine is often are: delivered on an integral one-piece baseplate with all auxiliary equipment installed and tested by the manufacturer. of gas turbines make them an attractive choice where power and transport natural gas. 15-20 Typical Gas Turbine Skid Layout 15-9 2017 EDITION 170 WWW. struction and start-up time are minimized. Lightweight Design plant. vibra. They are used to drive compressors. or any application where size and sign and the aircraft derivative design. power stationary applications: the industrial or heavy-duty de- erating sets. and other equipment required to produce. Over the The compact. Thus. portable gen. and simple design generators. etc. light weight design.NET CTSS . con- • Compact. weight are important considerations. speed. they were adapted to the industrial marketplace. It is important to monitor the operating pa. Some of these are: tions are important such as offshore installations. In a single shaft design. an asset where weight limita- quirements. sets). • Less frequent maintenance. ration. A split shaft design is advantageous where the driven equip- ment has a wide speed range or a high starting torque. The single shaft design is simpler. Gas turbine designs are also differentiated by shaft configu- • Available in larger horsepower sizes. all rotating components of the gas turbine are mounted on one shaft. ing components (including the driven equipment) must be ac- bines are: celerated to idle speed during the start cycle.CTSSNET. compressor is able to run at its most efficient speed while the FIG. The air • Quick overhaul capability. In a split shaft design. The power turbine shaft. The driven equipment is connected to the engine design which has been adapted for industrial use. Single Shaft/Split Shaft • Can burn a wider variety of fuels. TECH BRIEF which should be considered when determining application re. • Higher efficiency than industrial units. It requires a powerful starting system since all the rotat- Some of the advantages of the aircraft derivative gas tur. requir- engine was originally designed to produce shaft power and later ing fewer bearings. • Lighter and more compact. Aircraft Derivative the air compressor rotating components are mounted on one shaft.NET CTSS . 15-21 Gas Turbine Internals 15-10 2017 EDITION 171 WWW. and is generally used where the speed range as a pure jet. and the power turbine rotating components are mounted An aircraft derivative gas turbine is based on an aircraft on another shaft. The adaptation to stationary use was relatively of the driven equipment is narrow or fixed (as in generator simple. 15-24. use a mineral based oil. Combined Cycle Instead of using the hot exhaust gas for regeneration. GAS TURBINE CYCLES The basic gas turbine cycle is termed the Brayton cycle. This pre- heating of the combustion air thus reduces the amount of exter- nal heat input needed to produce the same work output. The gaseous com- bustion products are then expanded back to the atmosphere through a turbine. typical of heavy duty turbines. 15-23 axial flow or centrifugal compressor and an axial or radial flow turbine. 15-22. Babbitt type sleeve and thrust bearings. a constant pressure external heating pro- cess. 15-24 available energy loss is due to irreversible heat input and is il- lustrated in Fig. The oil type used depends on the bearing construction of the particular turbine. the overall thermal efficiency is increased. This FIG. 15-26 shows schematically a typical installation and its TS diagrams. Simple Open Cycle Simple Open Cycle The simple open cycle gas turbine takes atmospheric air into the compressor as the working substance. this approach uses exhaust gas to generate steam. Since the steam cycle does not require any additional fuel to generate power. Driven equipment such 15-11 2017 EDITION 172 WWW. and finally a constant pressure external cooling process which returns the working substance to the inlet state of the compression process. A sche- matic and TS diagram of the ideal Brayton cycle are shown in Fig. A heat exchanger or regenerator is Regenerative Ideal Brayton Cycle placed in the system to transfer heat internally from the hot exhaust gas to the cooler air leaving the compressor. They are mineral and fire-resistant synthetic based oils. 15-22 split shaft design allows a much smaller starting system since only the air compressor shaft is accelerated during the start Ideal Brayton Cycle cycle.NET CTSS . AUXILIARY SYSTEMS Lube Systems Two types of oils are used in lubricating gas turbine equip- ment. A diagram of this cycle is shown in Fig. The FIG. The turbomachinery used in the process includes an FIG. an isentropic expansion process. The turbine in this system derives enough power from the high temperature gas to drive both the compressor and load. the air enters the combustion chamber where the tem- perature is raised by the combustion of fuel. evaporator. In the basic Rankine cycle. The ideal Brayton cycle is a closed cycle consisting of an isentropic compression process. 15-25. The system schematic is illustrated in Fig. The steam leaving the boiler is expanded through a steam turbine to gen- erate additional power. Fig. 15-25 condenser and feed water pump completing a basic Rankine Ideal Brayton Cycle Available Energy cycle. This steam can be used either as a supplement to the plant steam system or to generate additional horsepower in a Rankine cycle.CTSSNET. the hot exhaust gas passes successively through the superheater. The cycle is closed by the addition of a FIG. and economizer of the steam gen- erator before being exhausted to the atmosphere. Regenerative Ideal Brayton Cycle The use of a regenerator in an ideal Brayton cycle acts to reduce the amount of available energy lost by external heat ex- change. Following com- pression. TECH BRIEF power turbine speed varies with the driven equipment. 15- 23. bearing pumps and return it to the reservoir. used to extend the life of a high gine mounted pumps are used to scavenge oil from the main efficiency filter further downstream. Coalescers — These filters are used to remove moisture from the inlet air system. dirt particles from the inlet air. combined lube system can be provided for the train. gear. Self-Cleaning — These filters are composed of a number of FIG. By reducing the con- taminants which contribute to corrosion. TECH BRIEF as compressors. wanted dirt from entering the gas turbine. An oil Prefilters — These are medium filters usually made of cot- scavenging system is also typical of these gas generators. Air Filtration High Efficiency Media — These filters remove smaller The primary reason for inlet air filtration is to prevent un. and fouling. thus There are various types of filters. Inertial — This type removes the larger particulates from tion type ball and/or roller bearings. En. Marine or Demister — These filters are used in marine the gas turbine life is extended.CTSSNET. 15-26 Combined Cycle 15-12 2017 EDITION 173 WWW. and generators also use this type oil. ton fabrics or spun-glass fibers. lows: Aircraft derivative gas generators all incorporate anti-fric. A synthetic oil is used in the inlet air. erosion. this service and is provided in a separate system from the min- eral oil system used to lubricate the driven equipment.NET CTSS . The main types are as fol- a common. environments to remove both moisture and salt. The reverse blast of air also there is generally no need for an elbow. It does. 15-31) Humidity (below) FIG. and humidity.9979. the conditions such as ambient air temperature. Heat rate is usually expressed in terms of Btu/(hp • hr) or Btu/(kW • hr) based on the Acoustics lower heating value of the fuel. The second most objectionable noise is produced by the gas generator and power turbine and is radiated from the Power and heat rate both vary depending on environmental casing. Power take-offs include any devices such as oil pumps.0016. 15-27 For changing relative humidity. and heat recov- Arctic High Efficiency Media with ery equipment (if any) which creates a back pressure on the Anti-Icing or Self-Cleaning turbine. To expensive method for obtaining some of the required noise re. with acoustic baffles is needed and the exhaust ducting should be sound insulated. gas turbine to produce the output power. across the system. The ISO Conditions: Ambient Temperature = 59°F = 15°C most common are the use of silencers and enclosures. Inlet loss is the Desert Inertial and Media or Self. and the heat rate changes only slightly. baromet- casing noise is more objectionable since it contains more noise ric pressure. TECH BRIEF high efficiency media filter “banks. Btu (LHV) Heat Rate. In this system. hp • hr The noise associated with the intake is characterized as 3414 = high frequency noise.NET CTSS . Thermal efficiency = bine installation are the intake. the least All gas turbine performance is stated in ISO conditions. a reverse blast of air removes built-up dirt on the filter and lowers the pressure drop. Additional silencing is corrected for the following: usually necessary and can be attained by the use of acoustic baffles before the elbow. fined. however. a set of stan- dible. The inlet Altitude = 0 ft (sea level) noise is the first area considered since this is where the largest Ambient Pressure = 29. If an enclosure is used. Similarly. 15-27 suggests take-offs have been subtracted. a Type of Environment Suggested Filtration typical correction factor for the heat rate is 1. Consequently. nization) conditions have been defined as follows: A variety of methods can be used to attenuate noise. Urban/Industrial Inertial & High Efficiency Media Performance is also affected by other installation variables including power take-offs and type of fuel used. The ex. some type of filtration is always recommended. pressure drop which occurs as the outside air passes through Cleaning the inlet filters and plenum. For example. etc. the ISO conditions must be duction is to place an elbow at the inlet. generators. 15-28) Inlet Losses (Fig. It is particularly useful in colder climates bine exhaust noise. when performance is in a frequency range where the ear is most sensitive. which are directly driven from the gas turbine Offshore Demisters output shaft and thus reduce the available output power. the power output does not Gas Turbine Air Filtration change. kW • hr sensitive. and casing radi. Altitude (Fig. arrive at site rated horsepowers. Inlet noise is the loudest Relative Humidity = 60% directly in front of the inlet opening. Therefore. for an increase in relative humidity from 60 to 100 percent. altitude. heated air from the gas GAS TURBINE PERFORMANCE generator discharge is introduced through distribution mani- folds immediately downstream of the inlet air silencer. where ice build-up is a problem. However. This type of noise is the loudest and most Btu (LHV) disturbing to the ear since it is in a range where hearing is most Heat Rate.” Air is drawn through the sary to provide gas and fire detection and fire extinguishing media at a low velocity and. Some- times it is necessary to correct power and/or heat rate for the 15-13 2017 EDITION 174 WWW. ated noise. Heat rate and thermal efficiency The noise created by a gas turbine engine is considerable are related as follows: and must be reduced to protect plant personnel and minimize 2544 environmental impact. the exhaust. exhaust loss is the pres- Tropical Inertial & Media sure drop through the exhaust stack.92 in. In order to compare different gas turbines.CTSSNET. Fig. Hg amount of sound power is produced. at a predetermined pressure drop equipment inside the enclosure. This filter can be used The last major source of noise to be silenced is the gas tur- in any environment. 15-29) Casing radiated noise can be reduced by using an acoustical Exhaust Losses (Fig. stated for a gas turbine. The performance of a gas turbine is usually expressed in terms of power and heat rate. filtration for various types of environments. silencers. 15-30) enclosure over the turbine. it is neces. possess a considerable amount of energy dard conditions known as ISO (International Standards Orga- which results in a detectable pressure change. Power is the net power available The selection of a filtration system is largely dependent on at the output shaft of the turbine after all losses and power the site location and operating conditions. a typical correction factor is 0. a silencer removes any ice that has built up on the filter. Although the exhaust noise contains more energy. Heat rate is a measure of thermal efficiency or the amount Since filters do protect the gas turbine and help extend its of heat energy (in the form of fuel) which must be input to the useful life. the ambient conditions must be de- haust noise is a low frequency noise which is only slightly au. The main sources of noise in a gas tur. For a de- Rural Country High Efficiency Media crease to zero percent. Temperature (Fig. Since most turbines exhaust vertically. Another method of eliminating icing problems is to install an anti-icing system. 965) (0.03) Heat rate (site) = 7370 Btu/(hp • hr) The above calculation procedures may vary slightly with dif- ferent manufacturers but will follow the same principles. 15-28. respectively. 15-30. Find power inlet loss correction factor from Fig.CTSSNET. the correction factor is 0. ex- haust loss correction factor. H2O Relative Humidity = 60% Fuel = Natural Gas Solution Steps Find the power altitude correction factor from Fig.9965) (0. For 2 inches of water.003)(1.500 (0.03) Heat rate (site) = [7090 Btu/(hp • hr)](1. 15-29.090 Btu/(hp • hr) Ambient Temperature = 80°F Altitude = 1000 ft (above sea level) Inlet Pressure Drop = 4 in. and 15-31. 15-28 performance brochure should be consulted for necessary correc. H2O Exhaust Pressure Drop = 2 in. Power (site) = power (0.984) (0.915) Power (site) = 23. Calculate the maximum available site power by multiplying maximum-no-loss power by each of the correction factors. FIG.800 hp For the heat rate find the inlet loss correction factor. the correction factor is 0.9965. Find power exhaust loss correction factor from Fig.984) (0.965) (0. Example 15-3 — Calculate maximum available site power and heat rate for the example gas turbine at the following condi- tions: Turbine ISO Horsepower = 27. 15-32. For 1000 ft altitude. the correction factor is 0. 15-30.003 Temperature factor = 1. The following example shows the method of calculating per- formance for a gas turbine at site conditions using data typi- cally supplied in the manufacturer’s performance brochure. Find the power ambient temperature correction factor from Fig.915.03 Calculate site heat rate by multiplying no-loss heat rate by the correction factors. Altitude Correction Factor tions.0065 Exhaust loss factor = 1.500 Turbine ISO Heat Rate = 7. Basic specifications for some of the commonly used gas tur- bine engines are shown in Fig.0065)(1.0065) (1. For 4 inches of water.003) (1. Heat rate (site) = (Heat rate) (1. For 80°F the correction factor is 0. TECH BRIEF type of fuel used in the gas turbine.9965) (0. 15-29 Since relative humidity is 60% and fuel is natural gas. 15-29. The turbine manufacturer’s FIG. and ambient temperature correc- tion factor from Figs.NET CTSS .984.) Inlet loss factor = 1.965. (Note: Heat rate is not affected by altitude. 15-31. 15-14 2017 EDITION 175 WWW. no Inlet Loss Correction Factor corrections are required.915) Power (site) = 27. but are a significant consideration when operating on liquid fuels. 15-15 2017 EDITION 176 WWW. compressor dis- charge temperature. CO emissions for distillate and other liquid fuels are generally higher than for natural gas. Similarly. It is unique in its ability to burn a wide variety of fuels making each application unique in terms of exhaust emissions. and products of erosion and corrosion in the hot gas path. the CO and UHC emissions are of secondary importance to NOx emissions. and operation of the unit. Like CO emissions. because most gas turbine units on the market today have good combustor designs. and actu- ally may increase. and local authorities have issued standards and codes to control pollution of the atmosphere. the emission rates of NOx are higher for these units. Sulfur oxide emissions from pipeline natural gas are virtually zero while wellhead gases. they are directly related to combustion efficiency. TECH BRIEF FIG. 15-31 late and smoke emissions are usually small when burning natu- Ambient Temperature Correction Factor ral gas. gas turbine engine emissions recently have become a major factor in the design. coal gases. 15-30 Gas Turbine Emissions Exhaust Loss Correction Factor The gas turbine. however. Gas turbine particulate emissions are influenced by the fuel properties and combustion conditions. organic NOx. particulates can be minimized by appropriate fuel treatment. firing temperature. However. The formation of thermal NOx is on the order of parts per million (by volume) or ppmv. Nitrogen oxides are categorized into two areas according to the mechanism of formation. This is because the fuel is burned with ample excess air to ensure complete combustion at all but minimum load conditions.CTSSNET. Sulfur oxides (SOx) exhausted from gas turbines are a direct function of sulfur content in the fuel. Various fed- eral. state. However. Particu- FIG. in general.” while that due to oxidation of organically bound nitrogen in the fuel is referred to as “organic NOx. Sulfur oxides can be eliminated by re- moving sulfur compounds from the fuel. Efforts to reduce thermal NOx by reducing flame temperatures have little effect on. selection. However. Of the exhaust components the most significant are the ox- ides of nitrogen (NOx). ash. the conversion of organic NOx is virtually 100%. is a low emitter of exhaust gas pollutants relative to other heat engines in similar service. NOx formed by oxidation of free nitrogen in the combustion air or fuel is called “thermal NOx. and other fuels may con- tain significant quantities of sulfur in the form of H2S. re- duction of NOx formation also produces increased inefficiency. UHC emissions can be reduced by proper combustor design for maximum efficiency. Two general approaches are used for NOx reduction: • T he use of an inert heat sink such as water or steam in- jection. The high temperature and oxygen content during combustion tends to favor the formation of SO3 and SO2 at equilibrium.NET CTSS . The amount of NOx produced is a func- tion of the fuel burned.” As implied by the name. ambient non-combustibles. Particulates generally refer to visible smoke. and residence time in the combustion zone. Carbon monoxide (CO) emissions occur because of incom- plete combustion of fuel carbon. Since the trend towards high turbine efficiencies leads to higher pressure ratios and firing temperatures. Unburned hydrocarbons (UHC) are formed by the incom- plete combustion of fuel. process gases. thermal NOx are mainly a function of the stoichiometric flame temperature. 6 28.9 851 LM6000 PF 58809.2 5985.0 993 CRYSTAL LM6000 PD 58809.9 3780 1578 280.9 6500 151.0 963 MS5002C POWER 39520 8714 9.7 7052.3 6207.4 17.6 7900 103.4 4670 308.8 6500 137.7 20.8 932 MS5002E 42912.8 4670 311.7 23 6100 198.902 6316 23.4 954 MS5002D POWER 45553 8413 10.1 783 MS9001E 175272 7357.1 7042.469 6816 17.9 3600 662.9 846 LM6000 PC SAC 59663.7 6187.0 959 THM 1304-10R 12606 7011 10 9030 1787 100.3 915 PGT25 DLE 31194.2 17.0 1004 CRYSTAL PGT25+DLE 41673.9 971 MS5002C 37950.0 855 DR-63G PG 66.9 8700.Rand VECTRA 30G 31.1 7900 103.3 1016 LM6000 PC SAC 59384.7 6500 138.NET CTSS .9 6510 1530 149.9 6793. TECH BRIEF FIG.5 6100 185.5 947 MS5002D 43717.1 10.2 849 VARIABLE IGV MS7001EA 121362 7584.1 7620.102 6347 22.5 5971.7 948 PGT25+G4 DLE 45164.6 6510 1571 198.8 7900 103.7 934 PGT25+SAC 42070.9 6500 151.1 12. courtesy of Diesel & Gas Turbine Publications.9 8.5 6100 184.4 6974.3 3600 274.9 12.6 6207.CTSSNET.0 932 THM 1304-11 15019 8206 10.9 3600 276.8 4670 274.6 6756.3 28.1 28.6 40 3600 456.6 17 5714 225.7 3930 1666 259.6 912 GE10-2 16288.9 6984.4 6510 1521 190.2 979 VECTRA 40G4 45.8 9030 1823 108.6 901 PGT16 19143.2 23 6100 197.3 5160 322.2 3600 278.4 1006 DR-63G PC 59.0 1011 LMS100 134370 5767.9 851 MS6001B 58955.3 8411.6 1001 MAN Diesel & Turbo SE THM 1203A 8046 10870 7.7 19.0 941 Data reproduced by permission from Diesel & Gas Turbine Worldwide Catalog. 15-16 2017 EDITION 177 WWW.3 3600 274.1 19.9 27.4 12. °F lb/s Temp °F hp Dresser.4 21.8 3000 926.4 8140.0 THM 1304-10 13008 8715 10 9030 1787 100.8 6208.3 28. 15-32 2011 Basic Specifications — Gas Turbine Engines (Mechanical Drive) Power At ISO RATING CONDITIONS Rating Heat Rate Power Pressure Model (ISO (LVH) Shaft Turbine Inlet Exhaust Flow Exhaust Ratio Rating) Btu/hp-hr RPM Temp.9 850 FIXED IGV LM6000 PC SAC OPEN IGV 59558.8 5976.2 5985.3 955 PGT25+G4 SAC 45492.0 895 PGT20 DLE 24926.2 21.8 928 PGT20 SAC 24300.9 15.822 6054 29.2 15.1 3600 278.0 983 PGT25 SAC 31205.1 4670 270.436 6042 27.2 7762.7 1017 VECTRA 40G 42.8 7800 1724 78.4 5967.3 907 GE Oil & Gas GE10-2 DLE 15907. 5 869 Mars 100 16000 7370 17.0 RB211 .7 950 Taurus 70 10310 7310 16.3 15500 41.5 959 Taurus 60 7700 7965 11.8 824 Trent 60 WLE 79120 6074 35.0 959 LM6000 60346 Rolls-Royce 501-KC5 5500 8495 9.4 34.8 10000 86.CTSSNET.9 928 SGT-400 18000 7028 16.0 975 LM2500-PH 36210 5986 19.2 968 Avon2648 21923 8323 9.0 918 RB211 .GT62 41450 6585 21.7 210.6 Trent 60 DLE 70418 5939 34 337.GT61 44650 6285 21. °F lb/s Temp °F hp THM 1304-12 16226 8001 11 9030 108.3 9400 88.3 358.9 13650 43.4 869 Data reproduced by permission from Diesel & Gas Turbine Worldwide Catalog.5 46.7 214.3 16500 41.1 8500 110.1 254.8 1031 SGT-500 26177 7373 13 215.0 1009 SGT-700 42960 6805 18 6930 208.0 RB211 .7 9500 93.1 7000 150.0 799 Avon2656 22807 8022 9.6 179. TECH BRIEF FIG.8 209.NET CTSS .3 3600 167.3 968 Centaur 40 4700 9125 10.6 179.3 941 Titan 250 30000 6360 24. courtesy of Diesel & Gas Turbine Publications.5 13950 47.4 1009 SGT-200 10300 7616 12.9 919 SGT-300 11000 7738 13. 15-32 (Cont’d) 2011 Basic Specifications — Gas Turbine Engines (Mechanical Drive) Power At ISO RATING CONDITIONS Rating Heat Rate Power Pressure Model (ISO (LVH) Shaft Turbine Inlet Exhaust Flow Exhaust Ratio Rating) Btu/hp-hr RPM Temp.6 923 Mars 90 13220 7655 16.0 1013 FT8 34690 6615 19.G62 39600 6705 20.5 5775 188.0 788 RB211 .7 22300 14.H63 59005 6247 25.H63 50848 6134 23 235.2 1060 501-KC7 7400 7902 13.0 982 SGT-750 49765 6362 23.8 6405 249.5 11400 58.0 932 LM2500+(PK) 41840 6440 22 3600 192.9 696 SGT-600 34100 7250 14 8085 177.8 833 Centaur 50 6130 8500 10.3 63.6 Siemens AG Energy Sector SGT-100 7640 7738 14.6 11525 64.8 864 Solar Turbines Incorporated Saturn 20 1590 10370 6.0 959 THM 1304-14 17701 7881 11 9030 108. 15-17 2017 EDITION 178 WWW.9 3600 152.5 856 MTU Friedrichshafen GmbH LM2500-PE 30180 6784 17.1 905 Titan 130 20500 7025 16.0 916 RB211 . tors are slightly more energy efficient. fuel. tion. TECH BRIEF • Modifications of fuel-air ratios and combustor design. the lower termi- Modification of Fuel-Air Ratio and Combustor Design nal voltage will increase the temperature rise of the squirrel An increased number of gas turbines are available with low cage winding during acceleration. Two areas of ELECTRICAL SYSTEM caution in the design of this system must be considered. Electric motors can be built ent special system problems. 3600 rpm synchronous motors have been built. This results in a greater voltage drop on may actually contribute to them. induction motors tend to draw more starting cur- the rate of CO emissions increases with the rate of water injec. power system voltage and capacity. nomical for this range because of the high cost of rotor construc- The induction motor has the advantage of simplicity. Critical items to consider are load character- istics for both starting and running conditions. voltage NOx design based on modifications to fuel-air ratio and combus. It is a rug. NOx content in flue gas as low as 10–25 ppm can be designs. load control re. catalytic combustion is lected over a wide range. however. low NOx turbines are available. For applications above 2500 hp requiring speed increasers. induction motors are normally preferred. such as a fan or compressor. Induction Motors bustion zone in terms of flame stability and dynamic pressures. induction machine. both for single-fuel and dual-fuel Once started the induction motor is a stable machine. with rated power factor of unity. and any condi. A suddenly applied load of 125% can easily cause the motor to pull out of synchronism with the elec- Proper motor application is essential if reliable performance trical system. These designs may reduce the full load efficiency of the achieved by this method. Also In general. the system when the motor is started. It is therefore recommended to motors. syn- Torque characteristics of the motor can be varied by design to chronous motors may be more economical at 1250 hp and above. For 1200 rpm loads. As a rule of thumb. or constant speed may favor synchronous Above this. is to be achieved. low inrush. petrochemical Once synchronized and running. However. 1200 rpm unity-power-factor synchronous motors should be tages that often make it the logical choice for industrial drive evaluated against 1800 rpm motors since the lower-speed mo- applications at lower power ratings. the characteristics of gas turbine emissions must be considered for each application. and operation. bility and continuity may be achieved by using large induction pecially for dual-fuel systems. Electric motor drives offer efficient operation and add flexi- bility to the design of petroleum refineries. greater than 22. leading. If the motor is driving a high inertia load. 15-18 2017 EDITION 179 WWW. or even lagging. They may tend to pull out of syn- with characteristics to match almost any type of load. A gradually increasing load from zero to 125% of rated load will posed to weather and atmospheric contaminants. match the requirements of the driven load and the available power supply. In summary. Load speed can be exact. Most systems from most vendors. power factor and efficiency. Water or Steam Injection — Water or steam injection is an effective way to reduce NOx exhaust emissions. This is. They can chronism on voltage dips that induction motors can ride through. It is best to furnish a power supply that will limit the voltage drop to 20% Different vendors have different approaches to effectively or less when starting the largest motor on a fully loaded bus. However. Starting. Induction motor are usually a more economic choice. accomplished at the expense of lower carefully review the need for dual-fuel low NOx machines.. Its 900 to 1800 rpm — Synchronous motors above 5000 hp are principal disadvantages are that it operates at lagging power widely used for pumps and for centrifugal compressors with factor and has higher inrush (starting) current. motors can easily ride through a 25 to 30% dip in system volt- age caused by external faults or switching. Overall system sta- Low NOx designs make the gas turbines more complex. and gas processing plants. es. since each is unique to Synchronous Motors the turbine. It is not effective in reducing organic NOx emissions and same size and speed. control is simple and no excitation equipment is required. All these factors The synchronous motor is usually easier to start than an are important in matching the gas turbine to the job. slower speed In general it can accelerate higher load inertias than synchro. be easily accommodated. Up to about speed increasers. synchronous motors pres- plants. or squirrel-cage induction motors nous motors and usually will do so in less time. motors below 5000 hp. When applying large synchronous machines to a system it is quirements.CTSSNET. motors with step-up gears. control the fuel-air ratio to reduce NOx content. high ef- 5000 horsepower. rent at a lower power factor than synchronous motors of the tion. induction and synchronous motor costs converge.000 hp) two-pole ged machine and has an outstanding record for dependability. pull-in. A-C MOTOR TYPE AND SELECTION Speed One of the first considerations in motor selection is to choose 3000 to 3600 rpm — Synchronous motors are seldom eco- between a squirrel cage induction and a synchronous motor. This will help as- tions at the plant site that could affect the type of motor certain if the electrical system is capable of supporting the mo- enclosure. drops on starting greater than 20% may require special motor tor design. Power factor improvement is available being researched. The system voltage drop on starting is less for a given horsepower motor. The need for power-factor correction. and pull-out torques can be se- In addition to these two methods. Although large (i.NET CTSS . installation. motor during normal operation by one or two percent. The constant-speed synchronous motor has inherent advan. Inadequate design could adversely affect hardware life. synchronous motors ELECTRIC MOTORS have less thermal capacity in their windings and may be more severely taxed when accelerating high inertia loads. be designed to operate reliably in outdoor locations where ex. The first is the dynamic effect that water injection has on the com.e. important to perform a transient load study. and synchronous motors are often chosen. tor demands under transient conditions. ficiency. 1 nerable to them. 1.4 86.800 217. and possible lower cost.3 57.0 84.4 13.7 3.800 92.6 Weather-Protected Type I 1.8 18.5 9.2 75. In many instances the in. Approx.6 Weather-Protected Type II 125 1. Induction speed range are normally handled by standard induction mo- tors.0 89. It is more expensive than the WP-I but minimizes the entrance of 150 1. 1.800 31.800 71.0 Drip-Proof 40 1.9 84.0 vironmental conditions under which the motor must operate. the lower the 1. 1.3 kV).0 75.5 88.5 91.0 94.0 15-19 2017 EDITION 180 WWW.200 2.3 78.5 84.200 46.5 89.5 84.8 34.0 91.9 81.2 75.800 1.200 10.7 more open the enclosure is to the atmosphere.5 91.5 89.800 139.0 68.5 91.9 75. 1. It is essentially a 75 1.0 vary from a routine procedure to a complex study requiring a complete electrical system analysis.4 84. Chem. Maintenance is less than for WP-I types.800 24.5 87.7 93.7 12.9 1.7 94.5 91.0 or a higher voltage transmission from the electric utility might 1.0 Motor Voltage 2 1.2 93.5 90.2 29.1 ical contaminants in gaseous form may be carried into a WP-II machine with the ventilating air and attack parts that are vul.200 13.800 48.2 92.8 75.800 2.5 87.200 86. 10 1.800 36.0 86.1 6. 100 1.800 112.0 The proper selection of voltage for a given motor drive can 1.200 2.0 164. such as 800 hp at 720 rpm.800 7.0 93.0 MOTOR ENCLOSURES 1.2 90.5 Motor enclosure selection should be predicated upon the en.5 85.1 58.0 115.5 93. Enclosures frequently used in a-c mo.5 91.6 This is the more commonly used outdoor enclosure. In general.0 84.6 72.200 25.1 88.5 plant distribution system is well established at a particular 1.800 2.CTSSNET.5 93.5 69. 200 1.5 3.2 91.800 18. synchronous motors should be considered at 1000 hp and above.0 91.2 35.0 1.4 These are generally used only indoors or in enclosed spaces not exposed to severe environmental conditions.0 water and dirt.NET CTSS .7 9. 1.9 3.800 59.9 47. 15 1. At high voltages (4 kV and above).5 sure satisfactory winding and bearing life.0 1.7 19.3 kV bus so no prob- 1.8 88.5 86.5 84.0 46.0 136.0 144.9 88. 1. 20 1.0 214. FIG. However.6 68.0 nomical at even lower horsepowers. 3 1.7 tion and any chemical contaminants in the area. Considerable maintenance may be required to en.200 68. 1.5 lem is involved in purchasing a standard motor of that voltage.5 be necessary.6 drip-proof guarded motor with heaters and outdoor bearing 1.4 78.6 requirements will depend upon general cleanliness of the loca.7 90.2 93.8 2.200 114.0 seals and is very susceptible to weather and atmospheric con- tamination.0 2.800 4. A new distribution voltage level. 1 1.7 94.2 93.200 5.6 90.0 89.200 29.0 first cost of the machine but the higher the maintenance costs that may be necessary.5 voltage. 30 1.0 This is the least costly outdoor machine.0 91.8 90.800 12. the 25 1. 60 1.4 25.0 90. the synchronous motor becomes more eco- 1-1/2 1.0 174.200 34. 700 hp at RPM Load 600 rpm. Standard High Standard High Efficiency Efficiency Efficiency Efficiency Below 514 rpm — The synchronous motor should be con- sidered for sizes down to 200 hp because of higher efficiency.2 Directly related to this is the amount of maintenance required to provide long-term reliability and motor life.800 167.5 88.200 19.0 tors are listed below.5 very large units are to be added.3 90.200 168.2 93. when 1.200 142.0 91.0 78.800 9.1 4.0 84.5 90.0 93.2 93. Maintenance 50 1.5 72. 15-33 Energy Evaluation Chart Motor requirements below 500 hp in the 900 to 1800 rpm NEMA Frame Size Motors.200 3. The new machine may be small com- 5 1.7 95.200 58. many factors must be consid- ered.0 95.200 222.0 91.0 24.7 94.2 29.0 90.7 93.0 214. and 600 hp at 514 rpm.9 86.0 91.5 91. In more complicated cases additional substation capacity may 7-1/2 1. Efficiency in Amperes Based 514 to 720 rpm — Synchronous motors are often selected HP Full Load on 460V Percentage at Full above 1 hp per rpm.200 7.6 86.0 86. say 2300 (2.5 pared to available system capacity on the 2.1 1.5 improved power factor.5 2. a new transmission line.6 7.0 109. TECH BRIEF For 900 rpm loads.2 be necessary to accommodate the new machine. • Recovering energy of compression on the downhill side of tional capital cost for a cooling water system. a 4-pole motor has a speed range from 1500 through above its synchronous speed by a suitable prime mover. set by the connected power system. Only the operating speed range separates one mode of With Fluid Couplings behavior from the other. constant speed. thereby increasing the speed of the turbine.CTSSNET. tor — only the frequency. in the same casing. However. In large sizes. It will breathe during sary to the induction generator as to the alternator. Smaller generators (down to 300 kW) are finding many uses. ergy. flashes. with a frequency range from 50 to An induction generator is simply an induction motor driven 120 hertz.NET CTSS . quency without being tripped off the line. • P roducing electric power from the expansion of geother- mal steam. Normally the induction generator does not differ in any as. Besides low cost and simplicity of control an and the turbine to the driven shaft. depending upon the number of magnetic poles it has in accordance with the formula: THE INDUCTION GENERATOR 120f The induction generator can be used as a convenient means rpm = Eq 15-2 P of recovering industrial process energy that would otherwise be wasted. The speed change does directly affect the power out- The totally enclosed water-to-air cooled machine uses an air put of the generator and therefore the temperature of its wind- to water heat exchanger to remove heat generated by motor ings. sentially a pump discharging to a power-recovery turbine. TECH BRIEF Totally Enclosed Forced Ventilated (TEFV) The synchronous generator needs precise prime-mover speed control to maintain its output at correct frequency. A fluid coupling 15-20 2017 EDITION 181 WWW. The turbine speed is varied important benefit is that the induction machine is instantly by varying the amount of fluid in the casing. combustibles surrounding the machine by sparks. variable speed drives offer an economical means of reduc- The TEFC enclosure minimizes the maintenance required ing energy requirements in many areas of operation. shutdown but often a breather filter is used to remove particu- late contaminants. It is more efficient than a TEFC motor be. or A standard a-c motor operating at 60 hertz will operate at a explosions which may occur within the machine casing. both sically the same as the differences between induction and syn. It is also designed to prevent the ignition of tors. chine. Excess steam or compressed gas can often drive such a However. whatever the driv- en speed. voltage and frequency remain Cooled (TEWAC) constant. if the input frequency can be varied in accordance generator to convert useless energy to valuable kilowatts. For many years variable speed applications relied on either cause of the large external fan. However. When con- TEFV enclosures can be used indoors or outdoors in dirty or nected to a public utility system such a machine cannot be al- hazardous environments. then a wide range of speeds can be obtained. Unless other machines are coupled into the same drive to losses. Totally Enclosed Fan Cooled (TEFC) • G enerating power through expansion of compressed gas- This is the highest degree of enclosure for an air cooled ma. with the speed requirements. whose enclosure is designed and constructed to withstand an They can be used with both induction and synchronous mo- internal explosion. The pump is connected to the driver shaft chronous motors. Increasing the convertible from generator to motor operation or vice versa. the TEFC motor has an air-to-air heat ex- changer. are higher because of the necessity to continuously supply it with cooling water. Totally Enclosed Water-to-Air For the induction machine. These motors are quite expensive especially in large sizes because of the high volume of cooling air required SPEED VARIATION relative to motor size. cause it does not have the external fan to drive. These are ba. for these very dirty applications. It is the quietest enclosure available and will usually dampen speed swings. For example. shaft driven fan. excluding any addi. es in cryogenic production. d-c motors or a constant speed a-c motor coupled to various me- chanical systems to provide the range of speeds required. TEFC motors are usually noisy be. Its first cost is Among them: greater than WP-II but less than TEFC. results in production rather than consumption of electric ener- gy. fluid increases the circulation between the pump and turbine. Fixed Speed Electric Motors pect of electrical or mechanical construction from an induction motor. Internal motor air is recirculated around the outside • R ecovering energy from single-stage waste steam tur- of the tubes while outside air is driven through the tubes by a bines in the 5-175 psig inlet pressure range. The speed of an equipment item driven by a fixed-speed Important differences exist between the induction generator electric motor can be varied with a fluid coupling. These motors are indicated for use in Because of the continuing increase in the cost of electric en- very dirty or hazardous locations. Since the motor cooling air is piped in lowed to deviate more than a fraction of a cycle from rated fre- from a separate source the influx of dirt and gaseous contami. Operating costs a natural gas pipeline. Maintenance is minimal depending upon changes do not affect the voltage or power output of the genera- the cleanliness of the cooling air. the machines will breathe when shut down and vapor and gaseous contaminants Variable Frequency Electric Motors can be drawn into them. This 3600 rpm. Solid- Explosion-Proof state electronics provide an effective means of speed control for An explosion-proof machine is a totally enclosed machine a-c motors by changing the frequency of the electrical signal. speed nants is minimized. close control of rpm is almost as neces- result in the lowest maintenance costs. This is es- and the more widely used synchronous generator. compressor to increase the density of the combustion air before it is inducted into the cylinder. The time and cost associated with engine four-stroke-cycle which is completed in two crankshaft revolu. in engine cylinder. For Two-Stroke-Cycle — The four cycle engine requires two rev- example. Many subclas. or gas derived from coal which contain hydrocar- bons. Dual-Fuel — Dual-fuel engines may operate in one of two modes. typically 4. A compression stroke which raises the pressure and tem. the typical efficiency for electronic speed control is olutions of the crankshaft for each power stroke. sifications are used to describe engines according to their speed. liquefied petroleum gas later type of supercharger is commonly called a turbocharger. cycle arrangements. This specification covers knock resistance of a gas stream in an internal combustion en- limits for three grades of fuel which can be purchased commer. some cases on the order of 10%. Most spark ignition engines can be easily modified to bons (hydrogen and carbon). fires one or more spark plugs per cylinder to ignite the air/fuel whether liquid or gaseous. They are often referred to as gas engines or gasoline engines and Methane Number resemble in appearance (except perhaps for size) and operation the engines used in automobiles. The pilot fuel provides less than 10% of the position. Speed ginning of the expansion stroke and spontaneously ignites. peratures and pressures which degrade the components of the engine.1 The methane number is a function of gas com- fuel for ignition. and uses a reference fuel blend of methane. The fuel is injected into the cylinder at the very be. The type and quality of the fuel can have a significant teristics and behavior of an individual fuel source. This Spark Ignition — Natural gas. Other gas sources. The expansion or power stroke from the ignition and combustion of the fuel mixture. TECH BRIEF costs less than electronic speed control but is less efficient. will have different composi- dling and preparation of the fuel as well as to the design of the tions. (LPG). An intake stroke to draw the fuel/air mixture into the There are differences in the prediction of methane number. methane number of 100. Dur- ing the intake stroke only air is introduced into the cylinder. cially (Fig. Most process plant engines are used to drive equipment pression of air alone causes a higher temperature to be reached in with a limited range of speed requirements. The two-stroke-cycle is completed type. Com- INTERNAL COMBUSTION ENGINES bustion air intake occurs at the end of the expansion and the beginning of the compression stroke. The determination of methane number is done via a pre- Four-Stroke-Cycle — Most spark ignition engines use a scribed engine test. This cycle is applicable both to compression ignition to 70% at 50% speed. are composed primarily of hydrocar- mixture. A broad range of liquid fuels can be burned some inert. Two types of supercharging are common: mechanical com- bustion engines.NET CTSS . Engine knocking must be avoided as it can cause excessive tem- its for the fuels they recommend be used in specific engines. Compression Ignition (Diesel) — Engines that use heat of compression as the ignition source are almost always referred Natural gas is a mixture of gases. rate prime mover and exhaust turbine driven compressor which obtains its power from expansion of the engine exhaust. testing makes this method an impractical approach to deter- tions and consists of the following piston strokes: mining the methane number of a fuel source. In practice the ignition method also defines pressors driven by an engine auxiliary output shaft or a sepa- the fuels or range of fuels used. Accordingly. gine.CTSSNET. selected to operate near the point of highest efficiency. increasing or decreasing gears may be used to match an engine 15-21 2017 EDITION 182 WWW. products. There are a num- ber of correlations available to determine methane number. For gaseous effect on the service life of the engine. it is necessary to understand the charac- engine. and other de. and hydrogen. mechanical configuration. It may also Typical natural gas streams have a methane number rang- operate on a gaseous fuel with a pilot injection of liquid diesel ing from 75–98. Supercharging increases the Engine Types power output from a given cylinder size by increasing the en- gine mean effective pressure. such as only part of the engine requiring significant changes. with a methane number of 0. One mode is as an ordinary diesel engine. but for a fluid output from the same size engine. for example pipe- in a diesel engine provided proper attention is paid to the han. High voltage electrical energy Most of the fuels used in internal combustion engines today. 3. Consequently. and which can be the cylinder. depending on the coupling make and and spark ignition engines. etc. in one revolution of the crankshaft and consists of two piston strokes: the compression stroke and the expansion stroke. the methane number is the determining parameter for under an ASTM designation D-975. the two-stroke-cycle was de- coupling is about 95% at normal speed. Different sources of natural gas. Natural gas is the most popular and burn any of the above fuels. 15-34). Ignition and combustion Internal combustion engines are classified according to the occurs at the end of the compression and beginning of the ex- type of fuel used and the method of fuel ignition. digester gas. vised to access the proprietary methods of their engine manu- perature of the mixture. It is comparable to the motor octane number of gasoline. LNG. the reader is ad- 2. pansion stroke. and can range from 50 veloped. line natural gas. some combustible and to as diesel engines. Spark ignition and compression ignition are the two meth- ods of initiating combustion used in reciprocating internal com. 1. facturer to determine the suitability of a gaseous fuel for a par- ticular application. CNG. with a total fuel energy at full load. are also used in engines with varying degrees of success. Engine manufacturers will specify the minimum methane number of the fuel source required for their engines. Engine manufacturers may also publish lim. Speed The four cycle diesel engine operates in a similar fashion. Often the fuel delivery system is the widely used of the petroleum gases. Diesel fuels are classified fuels. or gasoline are the fuels used in spark ignition engines. Com. To get a higher about 92–95% from minimum to normal speed. Supercharged Engines — A supercharged engine has a sign characteristics. An exhaust stroke to free the cylinder of combustion 65 or greater. but ranges of typical values are given. FIG.NET CTSS . tion for every 10°F above the rating temperature. Output per unit of displacement. and reduced emissions.e. For an aircraft engine the first and third items may be the most important. Viscosity at 104°F Centistokes Min 1. Four commonly used measurements are: Engine Energy Balance 1.CTSSNET.e. cooling-water pump.e.05 0.50 ration of naturally aspirated engines. BMEP. % by Wt 0.05 0. New thermal-barrier coatings (TBCs) insulate PERFORMANCE RATING many engine components from thermal shock and reduce heat losses that would otherwise decrease thermal efficiencies. they will operate well over large ranges of speed just as main combustion chambers effectively igniting leaner air/fuel an automobile engine does. ASTM D-975 (1995) Classification ture will also reduce the power output. As a general rule the low. and on the site conditions. (bhp) (i.05 2. Specific weight. Internal combustion engines are clas. diator fan. 15-34 ditions. the manufacturers must be consulted. or for turbocharged en- Ash. 15-35 includes engine power ratings.000) Heat rejected to turbo aftercooler 4–9 BMEP = Eq 15-3 (S) (A) (N) Heat rejected to exhaust 25–30 The value of N is equivalent to RPM for two-stroke-cycle Heat rejected to atmosphere engines. surface heat loss) 3–6 indicates how much turbocharging increases the brake horse- power which is the power delivered to the driven equipment by The mechanical power is the sum of the brake horsepower the engine output shaft. heat rejections and exhaust con- tions. High speed engines are often selected for tronically controlled fuel injection incorporates ambient and standby or intermittent applications. High inlet air tempera.01 0.g. and the power to drive such engine auxiliaries as a lube-oil pump. % by Wt Max 0.e.0 • H eat rejection at the power-end exhaust manifold [1500 to 3000 Btu/(bhp • hr) with jacket water cooling. lengthened the periods between but will usually require more maintenance than a medium or overhauls. Low speed — below 700 rpm New technologies have reduced specific weights (i. Water and Sediment.3 1.5 • F uel-gas requirements (i. Although internal com. Specific fuel consumption. “lean burn”) resulting in higher efficiencies and lower emissions. and so forth). High speed engines can offer weight and space advantages increased fuel efficiencies. and 1% reduc. Fig. (lb or Btu)/(bhp<$E• >hr) A gas engine converts the combustion energy in the fuel to mechanical power and heat. and alternator (for a spark ignition engine). 1500/3000 feet and 90°F according Flash point. Mechanical power 30–40 The relationship between brake mean effective pressure Heat rejected to cylinder cooling 25–40 (BMEP) and brake horsepower (bhp) is given below. Engines are rated for various altitudes above sea level (i.0 (bhp • hr). Operation in areas of low atmospheric pressure (high altitudes) will reduce the power output. % Max 0. Distillation °F Following are gas-engine design parameters. % by Vol Max 35 35 – 15-22 2017 EDITION 183 WWW. make and Min – 540 – model.e. Aromaticity.10 gines. The power delivered is directly related to atmospheric con. psi distributed as follows: 3. BMEP (i. specific fuel re- ary engine in continuous service with no space or weight limita. barometric pressures) and 1-D 2-D 4-D ambient temperatures (e. A rule of thumb for derating naturally aspirated engines is 3. 1500 feet and 85°F. LHV]. quirements (i. while for a station. tion and emissions over full operating ranges.9 5. °F Min 100 125 130 to DEMA. The combustion energy is usually 2. and RPM divided by two for four-stroke cycle. Heat rejected to oil cooler 3–5 (bhp) (33.05 0. “heat rates”). Precisely programmed elec- low speed engine. lb/bhp).35 – power for each 1000 ft above the rating altitude. High speed — above 1500 rpm • Heat rejection at the lube-oil cooler [300 to 900 Btu/(bhp Medium speed — 700 to 1500 rpm • hr)]. mixtures (i. Sulfur.5% reduction in Carbon Residue. available shaft power).. The values 90% Pt Max 550 640 – vary considerably depending on the engine type.e.1 24. For exact de. lb/bhp % Range 4.4 4. • Heat rejection at a turbo aftercooler if applicable [100 to sified according to speed in the following broad categories: 500 Btu/(bhp • hr)]. TECH BRIEF with a particular service. bhp/cu in. the first item would be of primary importance.15 0.e. portant measure of performance. % by Vol Max 0. Many engine de- bustion engines are usually selected to run over a limited speed signs include pre-combustion chambers that jet flames into the range. other important operating conditions to minimize fuel consump- er the speed the longer the service life. heat rate) [6500 to 8500 Btu/ Max 2. ra- The intended use of the engine will determine the most im. Several measurements of performance can be used to com- pare engines. or 800 to Cetane No. Min 40 40 30 1500 without].01 0. Grades of Diesel Fuel. A machinery expert should be recovered from the cooling circuits for cylinder jackets. refinery. From Fig. nomic criteria and improves as the engine size increases. The values are based on full AUXILIARIES design operating power at the speeds noted for various altitudes above sea level and ambient temperatures. and petrochemical indus- creased from a typical regular value of 33% to 75% by recover. 15-36. Fundamental = 2. an engine’s thermal efficiency can be in. centrifugal pumps. generators. axial compressors. and applied external loads (such as gear perature heat at about 180°F. Hydrodynamic journal bearings are found in all types of ciency. oil cooling. and running clearance. Fig. and gas compressors. and engine.0 MMBtu/hr Surface Finish — High speed gears are classified as preci- Exhaust heat per bhp = 4740 – 2867 = 1873 Btu/(bhp • hr) sion quality gears. LHV) turbomachinery are: The total heat rejected is calculated from the following equa. and worm.9% 7284 United States). electric motors. For example. pad pivot offset angle. turbo aftercooling. Low tem. LHV 2. This section will focus on en- recovery can increase the overall thermal efficiency to as high closed high speed helical gear reducers or increasers commonly as 75%.NET CTSS . ciprocating compressors. load at the bearing. and fans driven by turbines Solutions Steps and motors. pad arc angle.e. Heat rate = 7284 Btu/(bhp • hr). and orienta- surface heat loss to the atmosphere tion of the bearing (on or between pads).900 rpm. • Plane cylindrical tion: • Pressure dam Heat Rejected = (Heat Rate – 2544) Btu/(bhp • hr) • Tilting pad The heat rejected to the engine exhaust gas is calculated from the following equation: For all bearing types. used in the natural gas. can be mesh or pump volute loadings). and centrifugal pumps driven by motors. “herringbone”) gearing (predominant in the Thermal efficiency = = 34. such as tilt- Btu/(bhp • hr) heat rejected to cylinder cooling. for such as space heating. 15-35 High Speed Gears — High-speed gears are generally de- fined as having either or both of the following: Full Power = 1480 bhp 1. 100 x 2544 Thermal Efficiency = The hydrodynamic bearing types most commonly found in Heat Rate (Btu/(bhp • hr). Below 300°F water vapor will condense with CO2 absorption. usually used on centrifugal compressors. turbo = 1953 + 298 + 427 + 189 There are units operating with pitch line velocities in excess intercooling. There are many different types of open gears such as spur.000 hp. the fundamental geometric parame- ters are journal diameter. gravity It is technically feasible to recover part of the heat. and radiation = 2867 Btu/(bhp • hr) of 35. A heat recovery arrangement is illus- trated in Fig. lube oil consulted for further details concerning types of bearings and and turbo charged air.000 ft/min and transmitting 30. recovered by heat exchange with engine exhaust.000 ft/min. Heat rejected to water cooling. Some bearing types. electric generators. Pinion speed of at least 2. The thrust Total heat rejected = 4740 [Btu/(bhp • hr)] 1480 bhp bearing is usually on the low speed shaft.CTSSNET. tries. steam turbines.77 MMBtu/hr Rating Factors and Calculation Methods for Involute Spur and Helical Gear Teeth. oil density. Example 15-4 —Calculate the thermal efficiency.. Heat helical. TECH BRIEF ditions for a variety of gas engines. turbines. blowers. ing number of pads. 77°F and sea level. typically called “thermal effi. ing about 60% of the heat normally rejected to the coolant and Speed Increasers and Reducers — Speed increasers are exhaust. have additional geometric variations includ- cooling. Pitch line velocities above 5. The key operating conditions are oil viscosity. Therefore: Gearing — High speed gears can be selected with either single helical gearing (used extensively in Europe) or opposed 100 x 2544 double helical (i. Gears and resulting corrosion. preload. oil ing pad bearings. Speed reducers are used on re- RPM. and its full power rating. rotary positive displacement compres- sors. Higher level heat at above 300°F can be their applications and designs. length-to-diameter Exhaust Heat = Total heat rejected minus the sum of the ratio. spiral bevel. Technical feasibility depends upon the eco. Bearings An engine’s power efficiency. which include pumps. total heat re.” is calculated from the following equation: industrial turbomachinery. and total exhaust heat for a Waukesha L7042GL at 1200 industrial combustion engines. rotating speed. and jected. Pros and cons of each type of gear design are Heat rejected per bhp = 7284 – 2544 = 4740[Btu/(bhp • hr)] numerous with double helical gearing being more efficient be- cause there is only one thrust bearing required. = 7. page 14 of AGMA 2001-C95. 15-37 shows a minimum surface finish and quality required for various pitch line velocities as recom- Total exhaust heat = 1873 [Btu/(bhp • hr)] 1480 bhp mended in Figure 1. 15-23 2017 EDITION 184 WWW. acid formation. 00 1094 G3406 NA 215 1800 4 Not Avail. Note: Figures may be approximate due to variations in engine services and are representative of new engines only. 7507 2890 Note (1) 45 301 6.00 1047 G3306 NA 145 1800 4 Not Avail.28 989 G3606 LE 1775 1000 4 Not Avail. 7237 1008 230 617 270 10. 7712 2694 402 157 313 6. 7635 2179 344 435 311 9.85 856 G12CM34 6135 750 4 Not Avail. 6629 614 306 469 238 12.05 847 G3608 LE 2370 1000 4 Not Avail.85 1089 G3304B NA 95 1800 4 Not Avail.09 653 G16CM34 8180 750 4 Not Avail.16 912 G3516 LE 1150 1200 4 Not Avail.74 1101 G3306B NA 145 1800 4 Not Avail. 7875 2679 404 N/A 316 7.83 846 G3516 LE 1340 1400 4 Not Avail. Refer to manufacturer for exact information. 6649 604 306 470 238 12. 304 700 Not Avail. 8066 2651 395 139 323 7. 1342 GTA8.3 175 1800 4 152 7369 1642 Not Avail. 5839 361 414 757 120 6. 7205 1056 194 607 255 10. 7510 1630 258 408 285 9. 1341 QSL9G 175 1800 4 142 8088 2634 Not Avail. na 388 Not Avail. 6605 607 304 435 237 11. 208 791 Not Avail.9 99 2200 4 99 8454 2051 Not Avail. 7418 2763 Note (1) 81 297 6. 1347 KTA19GC 380 1800 4 144 8091 2317 Not Avail. 5839 361 383 757 120 6. 7775 2503 409 N/A 311 6.06 1064 G3306B TA 205 1800 4 Not Avail. 7254 938 230 698 304 10.96 806 G3412 TA 500 1500 4 Not Avail.39 975 G3516 TA 1050 1200 4 Not Avail. na 488 Not Avail.3 118 1800 4 103 8455 2335 Not Avail.90 985 Engine Ratings and Operating Parameters G3520B LE 1725 1400 4 Not Avail.62 985 G3508B LE 690 1400 4 Not Avail.42 992 G3520B LE 1480 1200 4 Not Avail.03 838 G3616 LE 4735 1000 4 Not Avail. na 651 Not Avail.43 1039 G3406 TA 276 1800 4 Not Avail.62 931 185 G3512 TA 790 1200 4 Not Avail. 149 404 Not Avail. 7405 1886 281 427 238 9. 7845 2532 414 N/A 313 7.90 857 G3612 LE 3550 1000 4 Not Avail. 7800 2725 431 54 312 6. 1179 GTA855 256 1800 4 132 8439 2863 Not Avail.62 914 G3508 LE 670 1400 4 Not Avail. Exhaust Full Speed Speed Strokes Per BMEP [Btu/(bhp·hr)] Jacket Water Intercooler/ Surface Heat rate Exhaust ENGINE (bhp) (rpm) Cycle (psi) LHV Cooler Oil Cooler Aftercooler Loss [lb/(bhp·hr)] temp °F Caterpillar G3304 NA 95 1800 4 Not Avail.00 653 Cummins G5.84 788 G3508 TA 524 1200 4 Not Avail. 8098 2673 423 152 324 7. 7775 2486 371 N/A 311 6. 286 636 Not Avail. 1197 WWW. 7301 1018 195 670 266 10.61 974 G3412C LE 637 1800 4 Not Avail. 7455 1259 195 520 255 10.07 1069 G3408 TA 332 1500 4 Not Avail.53 1004 G3408 NA 255 1800 4 Not Avail. 7324 1896 283 392 238 9.NET CTSS . 7402 1933 288 457 254 9. 7368 1838 274 493 254 9.CTSSNET.92 823 FIG. 7700 2789 441 170 260 6. 7875 2574 421 N/A 316 6.e. 7595 2108 333 402 310 9.58 892 15-24 G3512 LE 860 1200 4 Not Avail. 1077 G855 188 1800 4 97 8528 2692 Not Avail.50 957 G3408C LE 425 1800 4 Not Avail.78 1160 G3306 TA 203 1800 4 Not Avail.96 834 G3512B LE 1035 1400 4 Not Avail. 347 388 Not Avail. 1341 KTA38GC 760 1800 4 144 7942 3012 Not Avail. 6629 605 306 446 238 11. Heat Rejection Btu / (bhp · hr) Cylinder Cooling 2017 EDITION Full Power at Full Fuel Reqmt Turbo Atmosphere i. 15-35 G3512 LE 1005 1400 4 Not Avail.80 873 G3516B LE 1380 1400 4 Not Avail. 7824 2812 445 187 277 6. 7643 2392 378 N/A 305 7. 1327 TECH BRIEF G8. Note: Figures may be approximate due to variations in engine services and are representative of new engines only. Refer to manufacturer for exact information. Heat Rejection Btu / (bhp · hr) Cylinder Cooling 2017 EDITION Full Power at Full Fuel Reqmt Turbo Atmosphere i.e. Exhaust Full Speed Speed Strokes Per BMEP [Btu/(bhp·hr)] Jacket Water Intercooler/ Surface Heat rate Exhaust ENGINE (bhp) (rpm) Cycle (psi) LHV Cooler Oil Cooler Aftercooler Loss [lb/(bhp·hr)] temp °F Wartsila (4) 6L34SG 3,621 750 4 287 5,435 9L34SG 5,431 750 4 287 5,435 725 (5) (6) 295 (5) 233 (5) (7) 94 (5) 9.82 779 12V34SG 7,241 750 4 287 5,435 744 (5) (6) 295 (5) 214 (5) (7) 94 (5) 9.82 779 16V34SG 9,655 750 4 287 5,435 20V34SG 12,069 750 4 287 5,435 700 (5) (6) 295 (5) 240 (5) (7) 92 (5) 9.84 797 Waukesha F18G 240 1800 4 96 7570 2788 225 — 204 6.45 1064 F18GL 400 1800 4 160 7123 1875 243 473 155 9.37 836 F18GSI 400 1800 4 160 7523 2285 423 195 248 6.57 1116 H24G 320 1800 4 96 7897 2984 234 — 184 6.73 1098 H24GL 530 1800 4 160 7120 1879 242 475 138 9.37 838 H24GSI 530 1800 4 160 7497 2294 423 194 213 6.55 1114 L36GL 800 1800 4 160 7114 1874 241 473 120 9.36 838 L36GSI 800 1800 4 160 7389 2335 371 188 178 6.45 1116 P48GL 1065 1800 4 160 7092 1924 237 472 110 9.33 836 P48GSI 1065 1800 4 160 7373 2318 366 188 157 6.44 1113 186 15-25 F3521G 515 1200 4 96 7336 2470 383 — 336 6.41 1059 F3521GL 738 1200 4 138 7383 2054 314 432 199 10.99 703 F3514GSI 740 1200 4 138 8180 2577 409 162 439 6.97 1169 FIG. 15-35 (Cont’d.) F3524GSI 840 1200 4 158 8037 2489 376 165 402 6.85 1192 L5790G 845 1200 4 96 7446 2550 378 — 375 6.50 1044 L5774LT 1280 1200 4 146 6961 1670 360 303 277 9.07 842 L5794LT 1450 1200 4 165 6995 1687 337 358 247 9.11 849 L5794GSI 1380 1200 4 158 7665 2249 348 129 438 6.51 1136 Engine Ratings and Operating Parameters L7042G 1025 1200 4 96 7351 2469 382 — 316 6.42 1058 L7042GL 1480 1200 4 138 7284 1953 298 427 189 10.84 710 L7042GSI 1480 1200 4 138 7833 2430 243 190 401 6.84 1126 L7044GSI 1680 1200 4 158 7919 2350 343 150 389 6.74 1179 P9390GL 1980 1200 4 138 7198 1784 321 446 165 10.72 762 P9390GSI 1980 1200 4 138 7930 2518 262 194 320 6.93 1177 12V275GL+ 3625 1000 4 220 6550 596 262 708 83 11.77 820 16V275GL+ 4835 1000 4 220 6579 620 219 734 81 11.82 812 Notes TECH BRIEF (1) The heat rejected to the oil cooler is included with that to the jacket-water cooler. (2): G3508B LE, G3512B LE, G3516B LE, G3520B LE, G3600, GCM34 and G3300B engine information based on 0.5 gram NOx rating (3): All G3300, G3400NA, G3400TA and G3500 engine information based on catalyst setting (4) Performance data is based upon the A2 version at High Efficiency setting and reference conditions in accordance with ISO 3046/1-6 (5) tolerance 10% (6) Jacket water circuit (HT circuit) includes jacket and HT charge air cooler heat (7) LT charge air cooler portion only WWW.CTSSNET.NET CTSS TECH BRIEF FIG. 15-36 Example Engine Heat Recovery Arrangement Gear Ratings Scuffing Temperatures — The scuffing or flash tempera- ture index is the calculated temperature of the oil in the gear Various parameters affecting the durability, strength ratings, mesh. This temperature is arrived at by calculating the tem- and scoring temperatures include: perature rise of the lubricant in the mesh and adding it to the Horsepower — The horsepower rating of high speed gears inlet oil temperature. The temperature rise for a given set of is determined from the durability rating and strength rating on gears increases with the tooth loading, speed, and surface finish the gear or pinion as specified in AGMA 6011-G92, Specifica- (i.e. increasing roughness). tions for High Speed Helical Gear Units. In addition, the rating The temperature of the gears will increase as the pitch is is limited by the scuffing temperature as determined in accor- decreased, pressure angle is decreased, or helix angle is in- dance with AGMA 217.01, Information Sheet, Gear Scoring De- creased. sign Guide for Aerospace Spur and Helical Power Gears, and Annex A of AGMA 2001-C95. Design Factors Durability — The durability hp rating for a specific gear The following design factors must be considered for high set is primarily dependent on the speed and allowable contact speed drives. stress of the gear and does not vary significantly with tooth size. The allowable contact stress is dependent on the surface Housings — Must be of rugged design for strength and ri- hardness of the gear or pinion tooth and varies with material gidity to maintain precise alignment of gears and bearings. composition and mechanical properties. Bearings — Should be split-sleeve, babbitt lined, steel- Strength — The strength hp rating for a specific gear set backed precision journal bearings with thrust faces for axial varies mainly with the speed, allowable fatigue stress of mate- loads. Fixed pad or tilting pad (Kingsbury type) should be used rial, and with tooth thickness. The tooth form, pressure angle, where required. Tilt pad radial bearings may also be required filet radius, number of teeth, helix angle, and pitch line velocity for high rpm, high load applications. also affect the strength horsepower rating. Shafts — Precision machined from heat treated, high qual- Allowable fatigue stress is dependent on the tensile strength ity alloy (4140 is common) steel. Adequately sized to rigidly of the material and varies with heat treatment and chemical maintain gear alignment and protect from overload. composition. 15-26 2017 EDITION 187 WWW.CTSSNET.NET CTSS TECH BRIEF Couplings FIG. 15-37 A coupling is required to connect a prime mover to a piece of Gear Quality driven machinery. The purpose of a coupling is to transmit rotary motion and torque from one piece of machinery to Pitch Line Surface Quality Minimum Gear another. A coupling may also serve a secondary purpose such as Velocity (RMS) Quality Number accommodating misalignment of the two pieces of equipment. (ft/min) (micro inches) There are two general categories of couplings: rigid and Under 8,000 45 10 flexible. 8,001 – 10,000 32 11 Rigid Couplings — Rigid couplings are used when the two 10,001 – 20,000 32 12 machines must be kept in exact alignment or when the rotor of one machine is used to support the rotor of another machine. 20,001 – 30,000 20 12-13 Very precise alignment of machine bearings is necessary when Over 30,000 16 12-14 using this type of coupling. Manufacturing tolerances are also extremely important. One common application for rigid couplings is in the pump industry where the prime mover, Pinions — Normally cut integral with shaft from a high generally an electric motor, is positioned vertically above the quality forging that is through hardened or surface hardened by pump. carburizing or nitriding. Grinding is the most common finishing method but precision hobbing, shaving, or lapping are also used. Flexible Couplings — Flexible couplings, in addition to transmitting torque, accommodate unavoidable misalignment Gears — Usually made from a high quality forging that is between shafts. Mechanically flexible couplings provide for through hardened or surface hardened by carburizing or nitrid- misalignment by clearances in the design of the coupling. The ing and is separate from the low speed shaft. Gear may be inte- most common type of mechanically flexible coupling is the gear- gral with the shaft when operating conditions require. Grinding type. Material flexible couplings use the natural flexing of the is the most common finish method but precision hobbing, shav- coupling element to compensate for shaft misalignment. Metal, ing, or lapping are also used. elastomer, or plastic having sufficient resistance to fatigue failure may be used for the flexing element of the coupling. Many Dynamic Balance — Balance all rotating elements to as- types of flexible couplings are in common use and selection for a sure smooth operation at high rpm. particular application depends on many factors including cost, Seals — Shaft seal should be of the labyrinth type, with horsepower, shaft speed, and reliability. A specialist should clearance between shaft and seal of 0.020 to 0.030 inch. To pre- always be consulted for proper selection on any critical piece vent oil leakage through the clearance, the labyrinth is made of equipment. interlocking with grooves machined in the cap to create air back pressure during rotation to retain the lubricant. Vibration Monitoring High speed gears are usually used on critical process trains The oldest and most basic type of vibration measurement where down time is quite costly and catastrophic failure must involved the use of the human senses to feel and listen to a be avoided at all costs. Therefore, gear drives are becoming machine. The basic approach has not changed, just the method. more and more instrumented. Optional monitoring equipment It was always difficult to justify enough time for one individual, often specified by users include: or a group of individuals, to acquire periodic measurements on a large number of machines. Also, with the advent of high speed, • Vibration probes and proximitors (to measure shaft vi- high performance machines, failures can occur faster than per- bration). sonnel can react. In addition, very subtle changes can occur over a long period of time, making it difficult to realize by the • Keyphasors (provide timing and phase reference). human senses, but still affecting the machine’s mechanical sta- • Accelerometers (measure casing acceleration). bility and safety. Vibration monitoring is simply the full-time electronic measurement and monitoring of vibration levels from • Direct reading dial type thermometers in stainless ther- a given machine. Typically, the monitoring responds to the mowells (measure bearing temperature). overall signal input from the transducer regardless of the source • Resistance temperature detectors (RTDs) and thermo- of vibration (in-balance, bearing wear, coupling problems, mis- couples (measure bearing temperature). alignment, etc.). • Temperature and pressure switches (alarm and shut- A typical vibration monitor provides two levels of alarm: down functions). alert and danger, that can be adjusted to fit the characteristics of a given machine. These set points have associated relays Lubrication which can be connected to external audible or visual annuncia- tors on the control panel. If the alert or danger set point is ex- The majority of high horsepower, high speed gears are lubri- ceeded, the monitor and annunciator will alert operations and cated from a common sump which also lubricates the driving maintenance personnel of this event. Ideally, the alert alarm and the driven equipment. These systems are normally de- will indicate that the machine condition has changed signifi- signed to operate with a high grade turbine oil with a minimum cantly, but allow some discrete time before the machine is in a viscosity of 150 SSU at 100°F. A good operating pressure range dangerous condition. For most applications, if the machine does for the oil is 25 to 50 psi, with 25 micron filtration. reach the danger level of vibration and continued operation would probably result in machine failure, automatic shutdown is mandatory regardless of the time lag that has occurred be- tween alert and danger signal. 15-27 2017 EDITION 188 WWW.CTSSNET.NET CTSS TECH BRIEF There are three types of vibration sensors: (1) accelerome- BIBLIOGRAPHY ters, (2) velocity transducers, and (3) proximity probes. For most large critical machinery, and certainly for machinery with Brown, T., Cadick, J. L., “Electric Motors are the Basic CPI Prime Mov- fluid film-type bearings, the important measurement to be ers,” Chemical Engineering, Vol. 86, No. 6, 1979. made is rotor motion relative to the machine bearing or bearing Gartmann, Hans, Editor, “DeLaval Engineering Handbook,” McGraw- support. For this application, the proximity probe transducer Hill Book Company, 1970. has proven to be the most reliable indicator of machinery mal- Karassik, I. J., Krutzsch, W. C., Fraser, W. H., Messina, J. P., Editors, functions. “Pump Handbook,” McGraw-Hill Book Company, 1976. The proximity probe is a noncontacting transducer, typically Kosow, I. L., “Control of Electric Machines,” Prentice-Hall, 1973. installed on the bearing or bearing housing, and observes the rotor radial dynamic motion and position with respect to the Kubesh, John T., “Effect of Gas Composition on Octane Number of Nat- bearing clearance. This same type of proximity probe can be ural Gas Fuels,” SwRI-3178-4.4, GETA 92-01, GRI-92/0150, May 1992. used to measure axial position and vibration as well. Kubesh, John, King, Steven R., Liss, William E., “Effect of Gas Compo- sition on Octane.” For machines which exhibit significant amounts of casing motion, it may be necessary to add to this system a seismic Molich, K., “Consider Gas Turbines for Heavy Loads,” Chemical Engi- transducer measuring machine casing vibration. Some unique neering, Vol. 87, No. 17, 1980. applications dictate that measurements are necessary in the Neerken, R. F., “Use Steam Turbines as Process Drivers,” Chemical high frequency region, where accelerometers are typically em- Engineering, Vol. 87, No. 17, 1980. ployed. “Number of Natural Gas Fuels,” Society of Automotive Engineers, Inc., The American Petroleum Institute (API) has published a SAE 922359, 1992. specification describing vibration monitoring systems, API 670, “Vibration, Axial Position, and Bearing Temperature Monitor- Obert, E. F., “Internal Combustion Engines,” International Textbook Co., 1968. ing Systems.” Salamone, D. J., “Journal Bearing Design Types and Their Applications to REFERENCE Turbomachinery,” Proceedings of the Thirteenth Turbomachinery Sympo- sium, Turbomachinery Laboratories, Department of Mechanical Engi- 1. Malenshek, M., Olsen, Daniel B., “Methane number testing of neering, Texas A&M University, 1984. alternative gaseous fuels,” Fuel 88 (2009), pg 650–656. Sawyer, J. W., Editor, “Gas Turbine Handbook,” Gas Turbine Pub- lications, Inc., 1966. Spletter, Kathy, Adair, Lesa, “Processing ,” Oil and Gas Journal, May 21, 2001. CTSS Because ... The Illustrated Dictionary Of Essential Process Machinery Terms Why struggle through useless Internet search results for technical terms? Order your copy today: http://dieselpub.co/dictionary 1.800.558.4322
[email protected] “PACKING” has nothing to do with Paperback, 204 pages 15-28 US$24.95 Plus Shipping luggage or travel. CONVERSION FACTORS SI — METRIC/DECIMAL SYSTEM TEMPERATURE CONVERSION TABLES* ABBREVIATIONS CONVERSION FACTORS By Albert Sauveur abs absolute To Convert To S.I. Multiply To Old Multiply 0 to 100 100 to 1000 – cont. ata atmosphere absolute From Metric By Metric By C F C F C F C F Btu British thermal unit English -17.8 0 32 10.0 50 122.0 110 230 446 349 660 1220 -17.2 1 33.8 10.6 51 123.8 116 240 464 354 670 1238 Btu/hr British thermal unit/hour -16.7 2 35.6 11.1 52 125.6 121 250 482 360 680 1256 °C Celsius sq. in. mm2 645.16 cm2 6.4516 sq. ft. m2 0.0929 m2 0.0929 -16.1 3 37.4 11.7 53 127.4 127 260 500 366 690 1274 cfm cubic foot/minute -15.6 4 39.2 12.2 54 129.2 132 270 518 371 700 1292 lb/cu.ft. kg/m3 16.0185 kg/m3 16.0185 -15.0 5 41.0 12.8 55 131.0 138 280 536 377 710 1310 cm centimeter lbf N 4.4482 N 4.4482 -14.4 6 42.8 13.3 56 132.8 143 290 554 382 720 1328 cm2 square centimeter lbf/ft N/m 14.5939 N/m 14.5939 -13.9 7 44.9 13.9 57 134.6 149 300 572 388 730 1346 cm3 cubic centimeter Btu kJ 1.0551 kcal 0.252 -13.3 8 46.4 14.4 58 136.4 154 310 590 393 740 1364 cu.ft. cubic foot Btu/hr W 0.2931 kcal/hr 0.252 -12.8 9 48.2 15.0 59 138.2 160 320 608 399 750 1382 °F Fahrenheit -12.1 10 50.0 15.6 60 140.0 166 330 626 404 760 1400 Btu/scf kJ/mm3 37.2590 kcal/nm3 0.1565 -11.7 11 51.8 16.1 61 141.8 171 340 644 410 770 1418 ft/sec foot/second in mm 25.400 cm 2.540 -11.1 12 53.6 16.7 62 143.6 177 350 662 416 780 1436 ft-lb foot-pound ft m 0.3048 m 0.3048 -10.6 13 55.4 17.2 63 145.4 182 360 680 421 790 1454 gal gallon yd m 0.914 m 0.914 -10.0 14 57.2 17.8 64 147.2 188 370 698 427 800 1472 lb kg 0.4536 kg 0.4536 -9.44 15 59.0 18.3 65 149.0 193 380 716 432 810 1490 hp horsepower -8.89 16 60.8 18.9 66 150.8 199 390 734 438 820 1508 in inch hp kW 0.7457 kW 0.7457 -8.33 17 62.6 19.4 67 152.6 204 400 752 443 830 1526 in. Hg inch mercury psi kPa 6.8948 kg/cm2 0.070 -7.78 18 64.4 20.0 68 154.4 210 410 770 449 840 1544 in. H2O inch water psia kPa abs 6.8948 bars abs 0.0716 -7.22 19 66.2 20.6 69 156.2 216 420 788 454 850 1562 psig kPa gage 6.8948 ata 0.070 -6.67 20 68.0 21.1 70 158.0 221 430 806 460 860 1580 kcal kilocalorie -6.11 21 69.8 21.7 71 159.8 227 440 824 466 870 1598 in. Hg kPa 3.3769 cm Hg 2.540 kg kilogram in. H2O kPa 0.2488 cm H2O 2.540 -5.56 22 71.6 22.2 72 161.6 232 450 842 471 880 1616 kJ kilojoule -5.00 23 73.4 22.8 73 163.4 238 460 860 477 890 1634 °F °C = (°F -32) 5/9 °C = (°F -32) 5/9 -4.44 24 75.2 23.3 74 165.2 243 470 878 482 900 1652 kPa kilopascal °F (Interval) °C (Interval) 5/9 °C (Interval) 5/9 -3.89 25 77.0 23.9 75 167.0 249 480 896 488 910 1670 kW kilowatt ft-lb N•m 1.3558 N•m 1.3558 -3.33 26 78.8 24.4 76 168.8 254 490 914 493 920 1688 L liter mph km/hr 1.6093 km/hr 1.6093 -2.78 27 80.6 25.0 77 170.6 260 500 932 499 930 1706 m meter ft/sec m/sec 0.3048 m/sec 0.3048 -2.22 28 82.4 25.6 78 172.4 266 510 950 504 940 1724 cu. ft. m3 0.0283 m3 0.0283 -1.67 29 84.2 26.1 79 174.2 271 520 968 510 950 1742 mm millimeter -1.11 30 86.0 26.7 80 176.0 277 530 986 516 960 1760 m2 square meter gas (US) L 3.7854 L 3.7854 -0.56 31 87.8 27.2 81 177.8 282 540 1004 521 970 1778 m3 cubic meter cfm m3/min 0.0283 m3/min 0.0283 0 32 89.6 27.8 82 179.6 288 550 1022 527 980 1796 m3/min cubic meter/minute scfm nm3/min 0.0268 nm3/hr 1.61 0.56 33 91.4 28.3 83 181.4 293 560 1040 532 990 1814 1.11 34 93.2 28.9 84 183.2 299 570 1058 538 1000 1832 mph mile per hour 1.67 35 95.0 29.4 85 185.0 304 580 1076 N Newton 2.22 36 96.8 30.0 86 186.8 310 590 1094 To Convert To S.I. Multiply 2.78 37 98.6 30.6 87 188.6 316 600 1112 N/m2 Pascal From Metric By 3.33 38 100.4 31.1 88 190.4 321 610 1130 Nm3/hr normal* cubic meter/hour Old Metric 3.89 39 102.2 31.7 89 192.2 327 620 1148 psi pound/square inch 4.44 40 104.0 32.2 90 194.0 332 630 1166 psia pound/square inch absolute cm2 mm2 100. 5.00 41 105.8 32.8 91 195.8 338 640 1184 psig pound/square inch gage kcal kJ 4.1868 5.56 42 107.6 33.3 92 197.6 343 650 1202 6.11 43 109.4 33.9 93 199.4 scf standard* cubic foot kcal/hr W 1.16279 6.67 44 111.2 34.4 94 201.2 1000 to 1630 scfm standard* cubic foot/minute cm mm 10. 7.22 45 113.0 35.0 95 203.0 C F C F sq square kg/cm2 kPa 98.0665 7.78 46 114.8 35.6 96 204.8 538 1000 1832 816 1500 2732 bars kPa 100. 8.33 47 116.6 36.1 97 206.6 543 1010 1850 821 1510 2750 atm kPa 101.325 8.89 48 118.4 36.7 98 208.4 549 1020 1868 827 1520 2768 *“Normal” = 0°C and 1.01325x105 9.44 49 120.0 37.2 99 210.2 554 1030 1886 832 1530 2786 Pascals cm Hg kPa 1.3332 37.8 100 212.0 560 1040 1904 838 1540 2804 *“Standard” = 59°F and 14.73 psia cm H2O kPa 9.8064 566 1050 1922 843 1550 2822 nm3/hr nm3/min 0.0176 100 to 1000 571 1060 1940 849 1560 2840 C F C F 577 1070 1958 854 1570 2858 38 100 212 77 170 338 582 1080 1976 860 1580 2876 MILLIMETERS (mm) TO INCHES (in) 43 110 230 82 180 356 588 1090 1994 866 1590 2894 49 120 248 88 190 374 593 1100 2012 871 1600 2912 (1 millimeter = 0.03937 inch) 54 130 266 93 200 392 599 1110 2030 877 1610 2930 mm in mm in mm in mm in mm in 60 140 284 99 210 410 604 1120 2048 882 1620 2948 1 0.039 21 0.827 41 1.614 61 2.402 81 3.189 66 150 302 100 212 413 610 1130 2066 888 1630 2966 2 0.079 22 0.866 42 1.654 62 2.441 82 3.228 71 160 320 104 220 428 3 0.118 23 0.906 43 1.693 63 2.480 83 3.268 Note: The numbers in bold face type refer to the temperature either in degrees Centigrade or Fahrenheit 4 0.157 24 0.945 44 1.732 64 2.520 84 3.307 which is desired to convert into the other scale. If converting from Fahrenheit degrees to Centigrade degrees, 5 0.197 25 0.984 45 1.772 65 2.559 85 3.346 the equivalent temperatures will be found in the left column; while if converting from degrees Centigrade to 6 0.236 26 1.024 46 1.811 66 2.598 86 3.386 degrees Fahrenheit, the answer will be found in the column on the right. 7 0.276 27 1.063 47 1.850 67 2.638 87 3.425 8 0.315 28 1.102 48 1.890 68 2.677 88 3.465 9 0.354 29 1.142 49 1.929 69 2.717 89 3.504 10 0.394 30 1.181 50 1.968 70 2.756 90 3.543 11 0.433 31 1.220 51 2.008 71 2.795 91 3.583 VOLUME PISTON SPEED WEIGHT/HORSEPOWER 12 0.472 32 1.260 52 2.047 72 2.835 92 3.622 CONVERSION FACTORS CONVERSION FACTORS CONVERSION FACTORS 13 0.512 33 1.299 53 2.087 73 2.874 93 3.661 14 0.551 34 1.339 54 2.126 74 2.913 94 3.701 1 L = 61.02 cu. in. 1 m/s = 196.9 ft./min. 1 kg/metric hp = 2.235 lb./hp 15 0.591 35 1.378 55 2.165 75 2.953 95 3.740 10 cu. in. = 0,164 L 100 ft./min. = 0,51 m/s 1 lb/hp = .4474 kg/metric hp 16 0.630 36 1.417 56 2.205 76 2.992 96 3.779 17 0.669 37 1.457 57 2.244 77 3.032 97 3.819 18 0.709 38 1.496 58 2.283 78 3.071 98 3.858 L cu. in. m/s ft./min. kg/metric hp lb/hp 19 0.748 39 1.535 59 2.323 79 3.110 99 3.898 20 0.787 40 1.575 60 2.362 80 3.150 100 3.937 KILOGRAMS (kg) TO POUNDS (lb) (1 kilogram = 2.20462 pounds) kg lb kg lb kg lb kg lb kg lb 1 2.204 21 46.297 41 90.390 61 134.482 81 178.574 2 4.409 22 48.502 42 92.594 62 136.687 82 180.779 3 6.614 23 50.706 43 94.799 63 138.891 83 182.984 4 8.819 24 52.911 44 97.003 64 141.096 84 185.188 5 11.023 25 55.116 45 99.208 65 143.300 85 187.393 6 13.228 26 57.320 46 101.413 66 145.505 86 189.598 7 15.432 27 59.525 47 103.617 67 147.710 87 191.802 8 17.637 28 61.729 48 105.822 68 149.914 88 194.007 9 19.843 29 63.934 49 108.026 69 152.119 89 196.211 10 22.046 30 66.139 50 110.231 70 154.324 90 198.416 11 24.251 31 66.343 51 112.436 71 156.528 91 200.621 12 26.455 32 70.548 52 114.640 72 158.733 92 202.825 13 28.660 33 72.753 53 116.845 73 160.937 93 205.030 14 30.865 34 74.957 54 119.050 74 163.142 94 207.235 15 33.069 35 77.162 55 121.254 75 165.347 95 209.439 16 35.274 36 79.366 56 123.459 76 167.551 96 211.644 17 37.479 37 81.571 57 125.663 77 169.756 97 213.848 18 39.683 38 83.776 58 127.868 78 171.961 98 216.053 19 41.888 39 85.980 59 130.073 79 174.165 99 218.258 20 44.093 40 88.185 60 132.277 80 176.370 100 220.462 2017 EDITION 190 WWW.CTSSNET.NET CTSS .913 52 69.042 96 130..028 67 89..263 90 91 122.. being the same as its use will continue to be permitted. this being the same as a kilopascal. ampere A SPECIFIC CONSUMPTION second squared.. the millibar The SI unit of temperature is Kelvin (K). units/power units so that energy consumption of an though.079 kilogram-force meter (kgf m). or 0.540 44 59.472 41 55.....981 34 46.828 42 56.. for engine performance purposes..871 90 120..484 86 116.005 64 85.986 hp (LHV) of Fuel (measured in Btu/lb or kJ/g for liquid 2 2..189 88 118.. as PTC 17..447 again. character is used without the degree symbol (°) nor...774 34 45. so direct conversions can be 20 27..491 27 36.656 64 86.982 61 81.341 hp 1 lb/hph = 608.184 43 58.. One Watt is a kilometer is a meter x 103.. for example..... this heat value of the fuel whether liquid or gaseous The base SI unit for linear dimensions will be the being based on the SI unit of work. The American Society of Mechanical Engineers 1°C = 273 K Surry.. Btu/hph X 1...820 40 53.438 77 103. is the Newton (N)....0000102 kgf/cm2.. second s kilogram.102 kgf m Btu/kWh X 1.754 98 132..300 59 79.626 33 44. A 14 18.....710 69 92.638 78 105.533 only 0..000145 lbf/in2 or 0...756 75 100..914 30 31 40.387 27 36... this unit being one thousandth of a bar.848 87 116.235 94 126..102 1 Nm = 0.165 57 77.145 lbf/in2 or 0. PS..3 g/kWh to SI units.NET CTSS .433 33 44.. gram (kg) will continue to be used as the unit of versally used. One Newton (1 N) is 11 14.847 28 37. which is ment of lube-oil consumption will be quoted in liters 3 4..300 63 85...751 31 41. These tables are reproduced from the booklet 1 kgf/cm2 = 0.. grade) scale.10197 12 16.051 70 93.956 kPa).128 85 115. this is a very small unit...15°C on the Celsius (centi.. Known System of Units (Systeme International d’ Unites)... this being based on the For Liquid Fuel 8 10. The SI system.001 sure.807 Nm = 7.456 36 48.056 3. Thus the SI unit of measurement for net spe.0102 a temperature of -273.368 66 89.896 45 61....779 78 104.380 hand..28084 feet (ft). so measure.. which is a kilogram meter per Length...504 lbf/in2 or 8 10...166 66 88.....530 89 119.277 56 75.208 47 63.. KILLOWATTS (kW) TO HORSEPOWER (hp) (1 Kw = 1.120 79 105.435 69 93..577 95 127. will no longer apply for force. so the kilogram in effect should Amount of substance..033 (lb/hph) equivalent to 0.....484 83 111..964 3 4.843 43 57...975 93 126. multiples ranging from exa (1018) to atto (10-18): A equal to one Joule per second (1 J/s).502 42 56.....341 hp = 1...687 95 128.. PK.. On the other TEMPERATURES 10 13. meter m second squared...069 bar is still permitted.553 92 123.867 45 46 60..728 28 37.. Thermodynamic temperature .870 kgf/cm2.. energy and type. gives it an acceleration of one meter per Electric current ..825 84 112.36 g/kWh horsepower (CV...7457 kW.001644 lb/hph = millimeter is a meter x 10-3. meter... is founded on seven base units..159 per square meter (kN/m2)..319 49 66.907 71 96.254 53 71....369 68 91....020 kgf/cm2.233 60 81.963 48 65.415 74 99..715 gram force (kgf) and one member is equal to Heat Rate (Btu/hph) = LVH (Btu/ft3) 14 18. and the 12 16..mole mol Kilowatt Hour (kWh)...CTSSNET. The 1 g/hph = 1.589 61 82.607 47 63....351 Heat Rate (Btu/hph) = LVH (Btu/lb) X sfc 10 13. 5 6 6. One Watt (1 W) is cific energy consumption is expressed: g/kWh..420 Or 19 25.... Then mally employed with other scales of temperature.. 13 17.503 72 97.746 g/hph = 0. 118 Ewell Road. 1 1.337 35 47.. the gram (g).742 53 71.761 39 52..803 temperature of zero degree Kelvin is equivalent to 16 21.143 82 109.00134102 horsepower..014 metric 1 g/metric hph = 1..184 44 59. mass.802 81 108.941 99 132..5 lbf/in2 = 1..138 kgf m 1 kgf m = 9...024 123.. Surbiton. it will continue to be common parlance to internal combustion engine referred to net power use the word “weight” when referring to the mass of an object..098 54 73.. being equivalent to just 1 g/kWh = 0.889 European engine designers favor the bar as the unit 1 liter/h = 0..682 22 29.. so for engine ratings the 0....840 87 117.386 52 70.251 46 62.738 lbf ft = 0.0197 kgf/cm2 made by adding or subtracting 273.374 kilogram-force (kgf)..724 67 90...549 48 64. 0.398 97 131...461 80 107... In its Section 2.360 metric hp HEAT RATE kW hp kW hp kW hp kW hp kW hp 1 hp = 0... one bar being 100.161 41 54. 17 23.. the tables below give examples..623 1 metric hp = 0..214 74 100. candela cd ambiguous term.918 96 128..000 Pascal (100 1 Imp gal/h = 4.675 42..055 = kJ/kWh 1 lbf ft = 1. and 1 hp being the equivalent of 0.737562 pound-force (lbf ft)..35582 Nm) Although it has been decided that the SI derived Although the metric liter is not officially an SI unit.779 25 33.. since this is an Luminous intensity.601 of pressure.618 57 76.. which is becoming uni..245 6 8.312 1.521 58 78.772 84 113....712 22 29.341 k/kWh British unit of horsepower is equal to 1. Undoubtedly. The Kelvin unit is identical in interval 19 25. so being virtually the same as the 9 12......231 50 67.572 51 68..34102 hp) 1 kW = 1.349 80 108..926 76 103..069 29 38.959 58 77.067 23 31.987 115. is based on low unsaturated The derived SI unit for power is the Watt (W).392 71 95..049 37 50..397 16 21.664 63 84.046 25 26 33.454 55 74.282 100 134.270 32 43.736 g/metric hph To give an idea of how currently used units convert kilowatt (kW) is used...364 24 32.687 65 87. absolute zero K Distribution Press Ltd.356 Nm = 0.. and equal to 0.746 kW = 1..546 liters/h 7 9.)..356 21 28.733 72 96.791 69.. Use of Celsius 1 lbf/in2 = 0...177 one Newton per square meter (1 N/m2).097 76 101..669 is the Newton meter (Nm). for which the SI unit urements are given.890 49 65..646 (sfc) specific fuel consumption (measured in lb/hph TORQUE or g/kWh). POWER output.619 92 124..526 34.641 60 80... KT6 6HA England.515 18 24.. etc.233 lbf ft LUBRICATING-OIL POUNDS FORCE FEET (lbf ft) TO NEWTON METERS (Nm) PRESSURE AND STRESS CONSUMPTION (1 lbf ft = 1..212 91 122. The Newton is that force which. kilogram kg when applied to a body having a mass of one Time.738 equal to 0. but it is important to note that the kilogram these being: both the FPS and corresponding SI units of meas..423 24 32.196 88 119.079 68 92.... so one Newton meter (1 N m) is X sfc (ft3/hph) 15 20.. Description and Definition of Terms..877 59 79. Also adopted is heat only be used as the unit of mass. while a very small unit of power.115 35 46.259 97 130.101972 To convert these units to SI units: 17 22.98 bar “Vehicle Metrics” published by Transport and 0 K = 273°C.226 to the Celsius unit.692 of length – the meter (m).936 55 73.22 Imp gal/h 5 6.....Kelvin K Fuel consumption measurements will be based on the currently accepted unit.305 fuel and Btu/ft3 or kJ/m3 for gas fuel) multiplied times 4 5..202 29 39.410 30 40..061 82 111.600 98 131..147 70 94.705 81 109.135 26 35.558 11 14. For Gaseous Fuel 13 17..331 94 127.341 21 28....023 23 30..582 1 bar = 14...074 73 97. in 1973 published its Performance Test Codes for 2017 EDITION 191 WWW. 1 kW being equal to 1.116 40 54..808 73 98. 4 5.797 37 49.. So many per hour (liters/h).821 2 2.993 79 107..346 61... which is the equivalent of 14..328 The derived SI unit for torque (or moment of force) 7 9..944 62 84.894 93 124.... and one meter is equal to kilo....323 62 83.2248 pound-force (lbf) or 0.705 8... and the “Weight” in itself will no longer apply.595 54 72.417 83 112. Mass .138 38 50....014 metric hp Heat Rate is a product of Lower Heating Value 1 1.. For indications of “weight” the original metric kilo- for determining power output and fuel consumption... there is a school that favors the kiloNewton 15 20.. mechanical..092 32 42.810 56 75.715 seems to be favored to indicate barometric pres.414 = kJ/kWh 18 24.693 36 48.735 kW = 0.030 50 51 67..668 currently accepted metric equivalent.282 77 104.466 100 135. this code is intended for tests of all WEIGHTS AND LINEAR for which the abbreviation SI is being used in all types of reciprocating internal combustion engines DIMENSIONS languages.012 65 88.....570 75 101..761 20 26... lbf ft Nm lbf ft Nm lbf ft Nm lbf ft Nm lbf ft Nm unit for pressure and stress should be the Pascal (Pa).... SI UNITS… THE INTERNATIONAL STANDARDS SYSTEM The system outlined here is the International Reciprocating Internal Combustion engines.507 85 86 113.479 39 52..405 38 51.010 SI unit of force — the Newton (N) – and the SI unit 9 12.552 89 120. with a wide range of multiples and sub- quantity of heat – the Joule (J).110 99 134.. com . Texas. World-scale olefin processors turn to Elliott for steam turbines and compressors that deliver unmatched reliability. n Challenge: Build a world-scale olefin plant to process plentiful. Who will you turn to? C O M P R E S S O R S n T U R B I N E S n G L O B A L S E R V I C E The world turns to Elliott.elliott-turbo. n Result: Three trains of reliable. efficient Elliott steam turbines and compressors ensure the customer’s competitive advantage in world markets. efficiency and value over the life of their investment. www. low-cost shale gas.n Customer: Vertically integrated global petrochemical company. They turned to Elliott for a long-term partnership and long-term service. net COMPRESSION TECHNOLOGY SOURCING SUPPLEMENT COMPRESSOR Dedicated To Gas Compression Products & Applications . COMPRESSION SOURCING TECHNOLOGY SUPPLEMENT INSTRUMENTATION & CONTROLS The Industry’s Leading Reference Tool For Packagers. Purchasers And Training Providers CTSSnet. COMPRESSION SOURCING TECHNOLOGY SUPPLEMENT INSTRUMENTATION & CONTROLS The Industry’s Leading Reference Tool For Packagers. Purchasers And Training Providers CTSSnet.net COMPRESSION TECHNOLOGY SOURCING SUPPLEMENT COMPRESSOR Dedicated To Gas Compression Products & Applications . column.pelella@ge. Contact consists of a two-section centrifugal compressor. at: laurence. while the separated gas containing the lighter com. Contact her 50% compression trains-in-parallel configuration is used. expander applications at GE Oil & Gas in Florence. The recycle allows increasing the inject- further separation unit (separation unit 1) where the heavier ed gas flowrate and maximizing the condensate recovery. The recovered condensate is routed to the conden- cilities processing the fluid extracted from production wells. The gas coming from the separation phase The main objective is to recover and stabilize the condensate 2 is named side stream gas (low molecular weight gas) and by increasing the amount of intermediate and heavy hydro. in the oil and gas industry. recovers flash gas primarily from the condensate stabilizer 2017 EDITION 193 WWW. Marco Pelella is engineering man.com.TECH BRIEF Un-Balancing Act A new control method for back-to-back compressors with a side stream in flash gas compression trains n Figure 1. sate export line. Usually a 2 x pander applications in GE Oil & Gas in Florence. Process simplified schematic.CTSSNET. FGC system. • Maximize the condensate recovery. The gas stream is sent to a gas compressors.com. • Maximize the well’s production by gas injection. The liquid coming from the initial separation unit and the • Maximize the gas injection. Contact The first section suction header. flash gas compres. him at: marco.NET CTSS . In order to handle the feed gas and the side stream gas rithms and systems development of the turbo machinery solutions characterized by different molecular weight. Figure 1 shows a simplified schematic The gas coming from the column is named feed gas (high of the typical process in which the FGC system operates. Italy. To reduce him at:
[email protected]@ge. The gas delivered by the FGC system is re- tion unit in order to separate the two/three phase mixture cycled back to the initial separation unit and to the injection and recover the liquid phase. Italy. LAURENCE CASALI AND MARCO PELELLA Introduction Generally. Italy. Figure 1 shows a typical schematic diagram of the flash gas ager for system operability of centrifugal compressor and turbo compression trains driven by fixed-speed electric motors. it is preferable to adopt a back- for system operability of centrifugal compressor and turbo ex.com. is used to feed the second section of the FGC system. David Rossi is a senior control technologist within the control algo. carbon components. components are condensed in order to recover additional The main purposes of the process described above can liquid. to-back configuration for the compressors. which are installed in the fa. BY DAVID ROSSI. common to both trains. each FGC train engineering department at GE Oil & Gas in Florence. Laurence Casali is principal engineer the footprint and the costs. separation unit 1 is sent to a further phase of separation sion (FGC) systems are designed to recover flash gas from (separation unit 2) followed by the condensate stabilizer condensate stabilization units. molecular weight) and is used to feed the first section of the The fluid taken from the wells is sent to the initial separa. be summarized as follows: ponents is sent to the injection compressors. In this way. The FGC has to devel. The pressure ratio across the entire com- of time. The end user provides the mass flow and the connecting the two sections’. Based on labyrinth seal design. leading to the pressure at a certain value set by the end user based on the reduction of the compressor performance (lower pressure requirement of the downstream units. A backpressure control valve (Figure 1) is located down. its typology and machine Both trains discharge into a common discharge header for arrangement. The effect of the molecular weight variation on the pressure scribed in this paper. The process requirements and the boundary conditions for the FGC system are provided by the end user. and the second one (intermediate drum) stream gas). cycling. it resulted that the leakages could not be ne- recycle to the inlet separators. an ideal gas: nipulating the recycle valves of each compression section. Back-to-back configuration. glected and had an impact on the operability of the FGC sys- tem. whole compression in two sections with an interstage pro- the pressure at the outlet of the separation unit 2 is con. n-1 The set points were provided by the process control system n R0 Pout n based on the process requirements. The requirement is to minimize the the first section may operate in partial recycle. On each suction header. recovers flash gas from the separation unit 2. Two balance drums are present: the first one (ex- The FGC system has to handle all the flow coming from tremity drum) connecting the first impellers of the two com- the column (feed gas) and the separation unit 2 (side pression sections. tion header pressure. high molecular weight on the first section (feed gas) and lower Based on the well-estimated condition. which leads to a further first section molecular weight leaning. send the excess produced gas to the flare and limit the suc. These leakages result in a significant drop of the gas mo- stream of the FGC system to keep the discharge header lecular weight processed by the first section. the compressor performance will contin- Original control philosophy uously worsen up to the potential complete off line condition. the first section and second section suction headers for The flash gas compressors are designed to operate with each operating condition (normal running and startup). Each FGC train consists of a two-section centrifugal bilizer column.CTSSNET. The performance reduction will result in additional re- op the required pressure ratio to feed the downstream units. Before the introduction of the new control strategy de. the control philosophy for an FGC sys. Due to the back- opening of the flare valves in order to limit the quantity of to-back configuration. Hpol= · ·T · -1 This control philosophy was based on the fact that the n-1 MW in Pin 2017 EDITION 194 WWW. also common internal labyrinth seal leakages were assumed negligible. TECH BRIEF n Figure 2. to both trains. the pressure at the outlet of the column is compressor with back-to-back configuration. the end user can molecular weight on the second section (mixture of feed gas also provide the estimated mass flow trends as a function and side stream gas). discharges (Figure 2). the first section recycled flow includes gas released to atmosphere and maximize the production. cess gas cooler. The two groups of impellers in series are trolled in order to ensure the desired separation (Figure 1). ratio).NET CTSS . In order Issues experienced at site to reach the required performance of the condensate sta. In case of low feed gas flow or low feed gas molecular weight. ratio for a fixed-speed compressor can be explained consid- tem with the configuration described above was to control ering the general formula of the Polytropic Head (Hpol) for the suction pressure of each compression section by ma. a flare line is installed to pression system is given by the process boundary conditions. The following section describes the issues experienced End user inputs at a specific site. These correspondent molecular weight delivered respectively to are the internal labyrinth seal leakages of the compressors. In addition. the internal labyrinth seal leakages from the second section. faced. This splits the regulated by a pressure controller (Figure 1). column. The section section suction header. considering that the FGC is a fixed pressure ratio to bring the compression train online. Closing speed application. Consequently. leading to an increased the discharge pressure is fixed by the process boundary absorbed power. the second section suction pressure Pout = outlet pressure and the first section discharge pressure are considered equal. the first section pressure ratio directly affects first section suction pressure. the side stream resulted in a second section molecular pends on the suction gas flow and molecular weight. In particular. This phenomenon led to some issues at site during both function of and Mu startup/loading and normal operations.CTSSNET. The opening of both the first section recycle Equation 2 shows that the Polytrophic Head developed by valve and the side stream led to a lightening of the molecu- a compressor section is constant for a given speed and flow lar weight in the first section causing a significant reduction coefficient (in first approximation the Mu influence can be of the first section pressure ratio. = head coefficient (nondimensional polytrophic head). TECH BRIEF n Figure 3. flow and molecular weight directly affect the curred from overcurrent. two is- u2 = peripheral speed at impeller outlet diameter sues were experienced during compression train startup/ loading phase. the electric motor trip oc- conditions. MW = molecular weight Since the first section discharge pressure corresponds to Tin = inlet temperature the second section suction pressure (for the sake of simplic- Pin = inlet pressure ity in the present paper. Under the same assumptions.NET CTSS . As Hpol= ( . neglected). from equation 1. where: n = polytropic exponent second section suction pressure: A decrease of molecular R0 = universal gas constant weight will result in an increase of suction pressure. 2017 EDITION 195 WWW.Mu) u22 explained above. the second section pressure ratio de. The first section was not able to achieve the desired it can be concluded that. Normal operation with recycle valves fully closed. the pressure ratio for a fixed-speed com- where: pressor operating on the surge control line (SCL) is directly af- = flow coefficient (nondimensional flow) fected by the gas molecular weight: the decrease of molecular Mu = machine Mach number weight will result in a first section suction pressure increase. Since weight higher than the normal one. But Hpol can be also written as follows: this is valid if pressure drops are neglected). flash gas speed compressor is directly related to the gas composition compression train 1 (FGC1) was started up and brought (i.e. Process schematic diagram. could not close. 2017 EDITION 196 WWW.NET CTSS . The same phenome- section molecular weight leaning and consequently bringing non occurred on FGC1. the pressure ratio of a fixed- livering the required discharge pressure. Then. de. the first increased above the first section header pressure. First Stage Suction Header (Feed) FGC1 FGC1 Driver Second Stage First Stage Discharge Internal Seal Header IT Labyrinth Leakage PT Second Stage Side Stream Suction V Header Throttling Valve THF1 V PIC PT To Production Recycle Valve PIC Separators PIC Throttling Recycle Valve Valve THS1 Backpressure PT PT PIC Control Valve PCV FGC2 FGC2 Driver Second Stage First Stage Internal Seal IT Labyrinth V Leakage PT Throttling Valve THF2 Throttling V Valve THS2 Recycle Valve Recycle Valve Bias PIC SP Feed_DCS n Figure 5. due to the recycle valve. Low feed gas flow operation: first section recycle valve opening. since the first section recycle valve the compression trains offline and causing production loss. However. starting to deliver the required discharge pressure. As previously described. Other issues were experienced in normal operation due to on line.CTSSNET. Two compression trains were running in order to handle decreased leading to the opening of the FGC2 first section the side stream flow and avoid flaring. Then. Flash gas compression train 2 (FGC2) was running. in particular. the FGC2 first section suction pressure low feed gas flow shared between the two trains. TECH BRIEF n Figure 4. leading to first ing that the first section went off line.. a process upset leading to a reduction of available feed gas As soon as FGC1 was on line. molecular weight) of the processed gas. the feed gas flow to FGC2 flow. indicat- section recycle valve opened on both trains. considering now the compressor’s second stream flow with a consequent molecular weight reduction section. More specifically. TECH BRIEF n Figure 6. the first section recycle valve recirculates the missing how minimizing the number of measurement devices by le- amount of flow.. industry.. the second section. flare PCV set point. to the right of out an on-stream analyzer. with the consequenc.. which should intervene only in case of minimum flow. This is sor’s first section operating point moves towards the SCL.. ing on both sections to the available measured parameters In the event of feed gas flow reduction. for which its pressure ratio is also a function of the produces the increasing of the second section suction pres- molecular weight. this will lead to leaning of the first process/machine variables. as described in the previous sections). In this feed gas (high molecular weight). from the anti-surge controller limiting the compressor op. the first compressor section. to maintain the unit in operation is the side stream flow to es (lean-out) already described in the previous sections. (pressures. reducing its pressure ratio capability and con. In view of these considerations. the reduction of feed gas results in a re. since the In the event of recycling in the first section. valve in the side stream line. Feed gas header pressure should not reach the limit with some margin to allow proper controllability).e. the compres. by the backpressure control valve. as the highest achievable limit (i. the only terms which can be controlled in order recycling lower gas molecular weight. the seal gas discharge pressure is fixed by the backpressure control leakage is also contributing to this increase.e. given the upstream maximum allowed pressure of the gas — to the rise of the first section suction pressure.CTSSNET.e. It is also a good example on SCL).e. The first By considering this crucial parameter.NET CTSS . a consequently introducing side stream gas flow as much throttling valve has been introduced in the feed gas inlet line. the second-stage suction pressure increases. The regulation system should exploit the capacity of the i. duction of its pressure ratio. an example of so-called inferential control in the oil and gas in case the flow is lower than the minimum amount to re. As explained. section gas. In the aim to Figure 5 shows the throttling valves added on both feed minimize the recycled flow on the first section. The side stream throttling valve control- the feed gas header pressure can be regulated just acting ler was developed based on the effects of the gas lean- on the throttling valve (i. reduces its performances if situation. requiring the introduction of a throttling Preventing this phenomenon became the main require. ment for the control system described [1]. keeping the compressor operating point on veraging the physic-based approach that connects different the SCL. Compressor startup with feed gas only. stream flow is adjusted accordingly: the flow is increased 2017 EDITION 197 WWW. while was not applicable. valve. valve. none of the recycle valves need to open. the upstream gas (THF1 and THF2) and side stream (THS1 and THS2) pressure cannot be further regulated by acting on the recycle lines for both compression trains. As a consequence. compression system by maximizing the feed gas flow and erating point on the SCL. as possible. THF in the following scheme). During normal operation. The side imposed by the flare located on the first suction header. with sufficient feed gas flow The direct measurement of the current gas composition availability. designed to operate with the otherwise the system will end to the offline condition. which will also contribute — together with the leaning formance. sure and consequently of the first section suction pressure. an increase of the side Moreover. applied in general to control product qualities with- main inside the compressor envelope (i. being the downstream pressure fixed sequently shifting the operating point down along the SCL. it is possible to section discharge pressure (being actually the same) follows indirectly estimate the overall compressor system per- suit. bance introduced to the compressor in operations. introducing an duced to manage compressor operation limits as follows: additional degree of freedom. alternative process configurations simple PID regulator. This is • Analyzing the interaction between the process/machine another reason that contributed to the introduction of the feed gas line throttling valve. normal operation. This kind of issue can be avoided by linking the open- ing of both first section recycle valves of the parallel trains. An adjustable balancing factor may by the process. which are not in the scope of this paper. reaching the SCL). etc. if allowed side stream flow adjustment. a low-pres- could deprive the running unit of the minimum feed gas flow sure limiting regulator acts on the side stream throttling required to prevent its lean out. limiting its open- molecular weight gas through the seal leakage. An electric motor current limiting the required pressure ratio. This activity included: amount of flow moved downstream to the process. i.e.. despite gas flow or gas composition chang. otherwise the compressor will never get to cannot be processed. but can be estimated with a good approximation.. in order to correct possible performance differences. Balancing the load of two or more parallel compressors — if the feed gas flow is enough to keep the first stage re- cycle valves closed — can be achieved by splitting the feed gas flow between the compressors. flar- Considering the low-feed gas flow availability.e. An adjustable balancing factor may be introduced startup and loading phases is essential to reduce the distur.e. the feed gas throttling valve down- stream pressure). An adjustable balancing factor may be introduced in order to correct possible perfor- mance differences between the two parallel trains. Similarly the feed fects the operability of parallel compressors. with some additional feature aimed to shall be adopted. the increasing of its suction pressure (i. The first section suction pressure control through the will result in flaring. even if minimized. between different operating conditions. even if only one of the recycle valves needs to increase creased if the pressure is going above the predefined limit. and the downstream pressure is regu- lated through the side stream flow. each feed gas throttling valve has the same inlet conditions. since it is filled by feed With the aim to minimize the issues during the imple- gas only. losing the unit that has opened the recycle valve first. Should this occur. the unit may reach its performed in full recycle mode. Throttling valves opening. The feed gas throttling valve (THF in the follow. forwarding flow to downstream process) • In case of lower side stream gas production. compressor performance degradation. typically ap. starting a ing this extra gas. This reduction corresponds to an increasing of flow to the other unit: the system will enter in the lean-out phenomenon.NET CTSS . additional regulators are intro- gas flow is split between the parallel units. if the upstream pressure can rise further.e. Also.CTSSNET. the running compressor’s pressure ratio ca. In fact. TECH BRIEF splitting of the incoming feed gas.. This is typically not desirable. Keeping both feed gas throttling valves at the same position results in an acceptable n Figure 8. ing. the side stream gas cannot driver power limitation. Feed gas flow to both compression trains. able that the excess of side stream gas. the available feed a PID regulator. Advanced dynamic simulation pability goes beyond its design. the parallel compressor shall This method permits to push the operability of the com. The proper regulation of valves to avoid the excessive reduction of the side stream the feed gas and side stream throttling valves during the header. During compressor startup. account for the delay on the loop response and nonlinearity The flash gas compressor leaning phenomenon also af. Initially. can be implemented with a at all. 2017 EDITION 198 WWW. In case the first section of any compressor is forced to re- cycle some gas (i. an advanced ing scheme) shall introduce a pressure drop limiting the dynamic simulation was performed. ferences between the two parallel trains. in consequently. in this case part of the feed gas be introduced. It is unavoid. results in lower feed gas flow to that unit. mentation of the new control software at site. Moreover. otherwise is de. • In case of abundant feed gas. increase its recycled flow in order to preserve the correct pressor to its physical limit within the boundaries imposed splitting of the feed gas. gas header pressure control can also be implemented as plied on flash gas processes. being completely filled with low loop acts on feed gas throttling valves.. The side stream will keep adjusting compressor while the parallel train is already online (i. Actual feed gas incom- ing flow is not measured. the compressor flow. n Figure 7. bringing the flare PCV above the set point. In this case. be introduced in order to correct possible performance dif- es. the opening ramp is When the feed gas flow decreases (between 200 and disabled and the valves of the parallel trains are regulated 500 seconds). the two compression trains are ini. the results relevant THF1 is regulated by the control system. the side stream throt. the side stream flow towards FGC2 will be enabled. Fouling and parallel unbalanced operation As soon as the feed gas flow is increased again to the ini. the an OPC protocol. Figure 8 shows that the feed gas flow compression trains and consequently. more detailed analysis showed that the root cause was the able side stream flow and no gas is sent to the flare anymore. Initially it was attributed to a re- about 2600 seconds. At from the end user. At and polytropic efficiency. normal- In this scenario. a decrease in the performance of both tial value (between 1200 and 1500 seconds). Then. while THF2 is to the following scenarios are presented: kept at a preset position in order to limit the feed gas flow • Feed gas flow reduction when two compression trains going to FGC2 and mitigate the disturbance on FGC1. gas flow. Once the valve cess constraints in order to acquire the entire side stream flow. In this way. the side stream compressors took place. The model included the process bound. At about 2000 seconds.NET CTSS . system. the FGC2 electric motor is started.CTSSNET. delivering flow ized with the expected values at a given speed. In case the 2017 EDITION 199 WWW. At this point. TECH BRIEF n Figure 9. while part of the side stream flow is sent to the flare. Some critical transient scenarios were about 800 seconds. During operations. Start up of one compression train while the parallel one Figure 9 shows the assessment of compressor perfor- is running mance in terms of measured efficiency and head. the loading se- • Startup of one compression train when the parallel one quence is enabled. The recycle valves start to close and is running. are running in parallel. FGC2 is initi- The dynamic model of an actual FGC system was devel. oped in Aspen HYSYS and linked to the actual control soft. while a increased. since the In this scenario. the FGC system can handle the avail. is balanced between the two compression trains. In this paper. identified and simulated. the first suction header flare set point is duction of molecular weight lighter than expected. FGC1 is initially running. presence of fouling on the internal surfaces of both rotoric and statoric parts. Once FGC2 reaches the rated speed. FCG1 is acquiring the total feed and the process production parameters. Then. parameters in order to optimize the control algorithm to the downstream process. both in terms of polytropic head throttling valve open and the flow to the flare decreases. The process conditions are downstream process. delivering flow to the downstream process. ated and brought online to achieve parallel train operation. FGC2 is able to deliver the re- The upset scenario is a reduction of the feed gas flow. while part of the side stream flow is sent to the flare. Figure 8 shows the feed gas flow to both compression ware (antisurge/load sharing/master performance) through trains during the scenario. downstream process. reaches the same opening of THF1. Feed gas flow reduction The FGC1 discharge pressure is constant. Performance reduction. the first section recycle valves open on both by the control system. compression train is already online delivering flow to the tially running in parallel. feed gas flow towards FGC2 is opened to pressurize the ary conditions in order to take into account the requirements compression loop up to the desired starting pressure. FGC2 is initially at standstill condition with the isolation valves • Pre-tuning the new control software. tling valves (THS1 and THS2) partially close (Figure 7) to prevent the molecular weight reduction on the first section. closed and the recycle valves fully open. quired discharge pressure and start to send flow to the the flow is increased again to the initial value and the first suc. At about 100 seconds. the compressor pressure ratio increases. the throttling valve THF2 tion header flare set point is increased according to the pro. At a certain point. while the FGC2 discharge pressure such that the total feed gas flow is handled by the FGC increases during the loading phase. is opened following a dedicated ramp. • Testing and validating the new control algorithm. in case of fouling. internal leakages that were supposed to increase over time. side stream was not minimized. 2017 EDITION 200 WWW. Furthermore the increase of performance ex- parameter. by changing the balancing factor pre- After cleaning the rotor and the statoric parts. valves parameters and bias factors).CTSSNET. Laurence Casal. to allow more flow into the more efficient was sent to the site and reinstalled in its casing. perienced during solvent injection upstream of the com- ed values is observed especially at high flows. independently by the flow compressor. This required unbalancing ing to restore the original performances. produces an Operating the two compressors in the above conditions increase of losses and a reduction of the input work co. Figure 10 compressor (first section throttling valves parameters). mization of side stream flow handled by the compressors. conditions remained fixed — confirmed the fouling as the since the increase of roughness on the internal surfaces. CTSS around value 1 in comparison with the other compressor performance that remained well below 1. measured values match the expected figures. in some operating conditions. the bundle viously described. since no seal replacement was carried out on the cleaned mance parameter is equal to 1. In other tion where the original control software was meant to equally words. the performance deviates from balance the flow through the two machines. the two compressors. a deviation from the expect. Lorenzo Gallinelli. Efficiency and head parameters of both compressors over time. [1] “Method and system for operating a back-to-back com- lated to a lower than expected molecular weight and the pressor with a side stream”. means running two different compressors in parallel opera- efficient that is proportional to the handled flow. pressor’s first inlet flange — while all the other operating This deviation has been attributed to a fouling issue. These parameters The performance of the cleaned compressor settled were tuned at site through a step-by-step procedure. Reference firmed that the decrease of performances could not be re.NET CTSS . the perfor. Inventors: David Rossi. while in the graph. coupled with a reduction of impellers widths. more on the choking side than on the figuration resulted in nonoptimized operation under the maxi- surge side of the compressor map. GE Patent Number 274627. the flared brought back to the OEM factory for inspection and overhaul. TECH BRIEF n Figure 10. and shows the trends over a one-month period of the efficiency allowing more margins from the suction header set point and head parameters of both compressors — the cleaned of the less efficient compressor (second section recycle one and the other that remained in operations. This also con. This control con- expected values. major cause of performance degradation over time. One of the two compressors’ bundles was dismantled and In other words. visit: • HC treating • Heat exchangers www.500 for GPA/GPSA members • Dehydration $3.GPAglobal. 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Held annually in August at the University of Tulsa. olefins and other contaminants in natural gas and natural gas liquids MIDSTREAM'S GREATEST RESOURCE www. but are not limited to: CLASS SIZE LIMITED.org/education/gas-chromatography-school .GPAglobal. G PA S C H O O L O F GAS CHROMATOGRAPHY A weeklong school that is dedicated to gas chromatography. Oklahoma. Lecture topics include. www. Mitsubishi Heavy Industries has established a world-scale manufacturing and service facility in Pearland. Responsive Aftermarket Support from Our Advanced Facility. OUR RAPID RESPONSE WE PROMISE IMMEDIATE SUPPORT. to provide rapid response for your product’s entire lifecycle. This state-of-the-art facility. ft. as well as advanced machine tools.NET CTSS .mhicompressor. of storage space.com/en 2017 EDITION 201 WWW. spare parts support and over 50. offers 24/7 emergency response for MCO-I machinery and all other manufacturers’ equipment. field service. Texas.CTSSNET.000 sq. THEN WE OVER DELIVER. When every minute of downtime matters. you need responsive support you can rely on. Pearland Works. Contact him at: erik.nl. tuned mass damper systems TNO since 2011 specializing in thermal and mechanical problems. cyclic stress levels. with expertise in fluid and structural dynam. Jan de Vreugd has been working in the optomechatronics department of Mechanical vibrations. More detailed explanation can Opto-mechanics in Delft. and consequently reduce vibration and ics. A possible method to increase more than 10 years. which is age (UGS) system. This paper summarizes the investigative work performed suction pulsation damper.TECH BRIEF Nontraditional Vibration Mitigation Methods For Reciprocating Compressor Systems CLD. He is specialized in the area of pulsation and vi. Erik Slis studied engineering physics at the Rijswijk Institute of For reciprocating compressor systems.CTSSNET. The target of the project was to optimize the use of CLD and TMD for reciprocating systems that experience excessive vibration n Figure 1. levels) can be increased significantly for both structures bration related problems of pipe systems. Contact him at: andre. He has been at TNO for is typically less than 5%. BY ANDRÉ EIJK BSC. Sept. TMD used for two different configurations Editor’s Note: This abridged paper was originally pre- sented at the 10th EFRC. This was the reason to start a research and development (R&D) project of which the target was to investigate the effective- ness of nontraditional mitigation techniques. 14- 15. AND JAN DE VREUGD PHD Summary Introduction Experience in several projects has shown that it was very difficult to solve the vibration problems from reciprocating compressors with the traditional mitigation measures.nl. reduction in dynamic response (vibration and cyclic stress cal consultant. Germany. can be achieved by the application of 2017 EDITION 202 WWW. DORUS DE LANGE MSC.nl.ejik@tno. The second configuration is a on the potential of using CLD and a TMD for two different large suction pulsation damper of an underground gas stor- configurations. pumps with a damped TMD or CLD. The large vibration levels of both con- a typical configuration for a pipe between the separator and figurations could not be mitigated with traditional vibration mitigation techniques. and constrained layer damping Contact him at: jan. the damping ratio. Constrained layer damping. Düsseldorf. 2016. levels in the field. This R&D project focused on the investigation of constrained layer damping (CLD) and tuned mass damper systems (TMD) for reciprocating compressor systems. majoring in applied physics. Measurements have shown that the André Eijk has been at TNO since 1979 and is a senior mechani.NET CTSS .devreugd@tno. and process equipment. TMD and CLD have been used for ships and space applications. Dorus de Lange graduated in Background CLD Systems 2011 with an MSc in space systems engineering from the TU Delft This chapter only summarizes some basic understanding and started working as a mechanical and thermal analyst at TNO on constrained layer damping. be found in several publications as listed in references 2-13.delange@tno. compressors. The first configuration is a U-pipe. ERIK SLIS BSC.slis@tno. the damping ratio Technology.nl. Contact him at: dorus. is not always sufficient. For an elastic material. Stress strain relation for different types of materials. therefore. the strain and stress response are perfectly in-phase. CLD. Hence. which is formed by laminating a damping layer (viscoelastic material) in be- tween two structural constraining base layers (Figure 1). dashpot with a coefficient of viscosity . At lower temperatures the polymer is in its glassy state. Measurements of the required material 2017 EDITION 203 WWW. Generalized Maxwell model. However. When the system deforms during vibration. shown in Figures 2 and 3. Viscoelastic material combines the properties of a purely elastic and purely viscous material. A viscous material has 90° phase shift between the strain and stress. The stress-strain relation for different materials is n Figure 5. while in the transition region the material possess the highest damping performance. ellipse (Figure 3). The required material data of the viscoelastic material shall be provided by the manufacturer. The damping dependency on temperature is schematically illustrated in Figure 5. If the damping. For these reasons the temperature effect of the damping properties must always be taken into account during the design of a CLD.CTSSNET. well-chosen and used in the right temperature regime.NET CTSS . Figure 6 shows the effect on damping [16] on the ap- plication of CLD in space structures. A viscoelastic mate- rial is somewhere in between the purely elastic and viscous behavior. Prediction of thermal- with a stiffness coefficient E and the viscous element by a mechanical stresses and deformations requires. The most common model is the Maxwell model as illus- terial under repeated cyclic loading is for that reason an trated in Figure 4. The slope of the major axis of the ellipse Viscoelastic materials. Temperature effect on loss factor. shear strains will be developed in the damping layer and energy is lost through shear deformation of the material. the input of accurate temperature-dependent properties. tic models are combinations of linear spring and dashpots. This results in an elastic energy storage during deformation and all energy is released during relaxation. The CLD consists of a “sandwich”. TECH BRIEF n Figures 2 and 3. The stress-strain relationship for a linear viscoelastic ma. like polymers and rubbers show is a measure of the stiffness and the area is a measure of large changes in properties with temperature variation. This re- sults in all energy being lost in a cycle. At high tem- peratures the polymer behavior is rubbery like. viscoelas. they The elastic element can be modelled by a linear spring can possess high damping properties. the provided data n Figure 4. for ex- A DMA [16]. especially for compressor and pump systems. the mechanical natural frequency 2017 EDITION 204 WWW. This can lead to fatigue failure of the TMD and mounting system. to the same fundamental natural frequency fn of the primary duce the vibration and cyclic stress levels of the structure. clic stress levels if not tuned well. the TMD becomes more effective and robust. stiffness. behavior of polymers. x1 represent the mass. if the MNF of the system after the installation of the troscopy. One of the disadvantages of TMD systems is that they n Figure 6. m2. measurements of the MNFs and are implemented in ANSYS [14]. and is typically tuned to the mechanical natural frequency (MNF) of the primary system. also known as dynamic mechanical spec. and they may even increase the vibration and cy- with a Dynamic Mechanical Analyser (DMA). TECH BRIEF relative high frequency (up to ≈100 Hz) when compared with civil structures. Schematic of a TMD. The measured damping characteristics and/or spring. However. ample. Also allowing one to determine the material properties such as the TMD shall always be designed with an adjustable mass complex modulus. If possible. In the design of a TMD. mode shapes of the structure can be used to tune the simu- lation model. The challenge in rotating equipment systems is the n Figure 8. n Figure 7. It is a com- monly applied and accepted method in the civil industry for buildings and bridges for low frequencies. damping and displace- ment of the structure of interest to which the TMD is mount- ed. c1. A sinusoidal stress is applied to the The TMD system must always be tuned in the field to sample and the deflection of the specimen is measured. In most applica- tions the mass ratio is designed to be in the range of 1-10%. must be tuned to a particular MNF for that reason.NET CTSS . stiffness. reducing the vibrations of the structure by increasing its effective damping ratio. x2 represent the mass. Demonstrating the effectiveness of a TMD. Additionally. This is normally done MNFs. This can happen. is a technique used to study and characterize TMD is shifted to a frequency where the amplitude of the materials and is very useful for studying the viscoelastic pulsation-induced force is larger. account for differences between the model and reality. The TMD concept was first applied in reducing the rolling motion of ships as well as ship hull vibrations. the passive damper is stretched and compressed. Measured quality factor as a function of temperature are typically effective over a narrow frequency band and for a particular material. c2. As the two masses move relative to each other (90 degrees out of phase).CTSSNET. damping and displacement of the TMD and F(t) represents the excitation force. k2. An example of a TMD is shown in Figure 7. They are not effective if the structure has several closely spaced properties are strongly recommended. The terms m1. it has not been applied for many structures in the oil and gas in- dustry. When the mass ratio increases. k1. system as shown in Figure 8. Background on TMD systems [17-19] The MNF of the primary system can be split into a lower A TMD is a passive device consisting of a mass. The most significant design variable for the damper is the mass ratio µ as de-fined in equation 1. where m1 and m2 are respectively the mass of the TMD and mass of the structure of interest. a spring f1 and higher f2 frequency by attaching a spring-mass tuned and a damper that is attached to a structure in order to re. For that reason.NET CTSS . ≈143 lbs. leading to a that the TMD is very effective. system. is low cost and easy to in- This was also calculated during the design of the system. This ratio is based on 2017 EDITION 205 WWW. Without additional damping of the TMD. 40 pipe system was generated and tuned to the measured Using an intermediate value of damping somewhere be. the leaf spring (Figure 12). From field measurements it the ANSYS [14] model. for the complete speed range. For that reason. Figure 11 shows elled. it is possible to control the vibration a way that the MNF of 57 Hz of the primary system is split of the primary system over a wider frequency range. of the damper fd is defined by equation 2 and. The ef. a CLD caused by the excitation of an MNF of 57 Hz by the cylinder was chosen because it has a relative large damping ratio stretch displacement of three times the compressor speed. the system has one degree of freedom with stiff.5 kg) (pipe has a weight of which is adhesively bonded to the spring (Figure 12). TECH BRIEF n Figure 9 (left). possible to shift them out of the complete compressor speed allowable vibration levels were experienced in the U-pipe range. It was calculated that the high vibrations would lead the different vibration levels as a function of frequency to fatigue failure. a very small mass of 5. and the dimensions have been ing ratio of 0. Besides that. can be achieved if the lowest MNF is increased up ratio of the damper opt can be calculated from equation 3. Figure 10 (right). leading to a safe and reliable system for the long the damped TMD is a factor of 26. stall. could be tuned by adjusting the lengthwise position of the of the spring leaf. which are easier and Equations 1. the additional damping measured at 57 Hz perpendicular to the plane of the pipe was also required to avoid fatigue failure of the TMD itself. mode shape. is achieved by the application of a CLD. µ= ƒd ƒ = 3µ m1 = n opt 8(1+µ) 3 This was one of the motivations to investigate nontradi- 1+µ tional vibration mitigation techniques. the application of If there is zero damping then resonance occurs at the two a CLD and damped TMD with CLD has been investigated in undamped resonant frequencies of the combined system f1 the research project for such a U-pipe configuration. In Tuned mass damper system this case. was shown that the difference between the calculated and The CLD has been adhesively bonded to both sides of measured vibrations were caused by a much lower damp. and f2. Original system as built. The next step was to design the TMD in such tween these extremes. further optimized with the ANSYS model. which has the effect of locking the spring k2. into a lower f1 and higher f2 MNF of respectively +20% and The damping of the TMD. A finite element model of a 6 in. It was measured that the high vibration levels were To dampen the vibrations of the pipe and TMD.CTSSNET. It was calculated that only the research program. the damping term. (152. This finally led to a rather stiff structure because of the absence of a stiff struc- m2 ture in close vicinity of the piping (Figure 10). Moreover. it was shown configurations installed between the separator and suction that the pipe vibrations would still exceed the allowable level pulsation damper (Figure 9). safe and efficient op- eration for the long term.4 mm) schedule ness of k1 and a mass of m1 + m2. which has been investigated in -20% around the MNF of 57 Hz.5 lbs. un. (2. The ratio of vibration levels loss in production. The high vibration levels were with the TMD installed. 2 and 3 cheaper to install to ensure a reliable.8% for both pipes while 2% had been mod. The viscoelastic properties of the CLD were measured but it was not clear why the measured vibration levels were with the DMA technique [16] and have been implemented in much higher than calculated. a fect of the damped TMD with a CLD will be demonstrated by simple leaf spring has been used for the spring and the TMD two examples that will be discussed in the next section. the system could not be (FRF: Frequency Response Function) and it can be seen operated up to maximum compressor speed. to 20% above the excitation frequency. Acceptable vibration and cyclic stress of the pipe without (blue line) and with (red dotted line) levels. The other extreme case occurs when there is infinite damping. the two MNFs f1 and f2 would always be Introduction excited by varying the compressor speed because it was not When activating a reciprocating compressor system. (≈65 kg) was required to achieve this. System with additional stiffening. Because the compressor has a large speed Example from a U-pipe configuration range variation. The CLD is also very effective because the ratio in vibration levels with and without the CLD is 23 for the mode of interest. The vibra. causing rotational compliance rather than full fixation. An impulse hammer excitation method has been vere vibration problems have occurred in several projects n Figure 13. From the FRFs. The second method of increasing the damping and so tion and cyclic stress levels will be reduced with the same reducing the vibration and cyclic stress levels was the in- factor if the pipe is excited with the same force at the fre. which means that the model differs from the actual system. which is in the same order of the calculated value of 26. So only the ratio of the vibration the fact that the frequency. Example of a large pulsation damper Introduction n Figure 12. Calculated FRFs for pipe and TMD to tune the mode noted that the absolute value of the vibration levels from shape at 57. TECH BRIEF used to measure the FRFs. Moreover it is n Figure 11. Measured FRFs of bare U-pipe (left) and with TMD (right). because the compressor can be operated over the entire speed range (worst-case scenario). Moreover it can be concluded that the The effectiveness of the CLD is largest when it is mounted ratio in vibration levels with and without the CLD mounted on the locations with the largest strain. If the compressor had Constrained layer damping a fixed speed. vestigation of the effectiveness of CLD added to the pipe. it can be concluded that the measured MNF of the lowest mode shape is 50 Hz instead of the calculated value of 57. For that reason. The FRFs of the pipe without and with the TMD are shown in Figure 13. the CLD has been mounted on the two vertical straight pipe sections of the U-pipe.CTSSNET. Figure 14 shows the test pipe with the CLD adhesively bonded to the vertical parts of the pipe.22 Hz. Figures 11 and 13 cannot be compared because the excita- tion methods are different. plates. which were shown to be very effective. This is even larger than the calculated value. Inspired by the results of the TMD and CLD of the U-pipe. quency f1 of 45 Hz. and is probably caused by the flexible mounting plate. the idea was pro- Measurements have been carried out on the test pipe posed to apply this also for a suction pulsation damper.22 Hz. This was caused by the flexural flexibility of the mounting plates. The measured ratio in vibration levels with and without the CLD is 20. For the U-pipe. the ratio would be much higher. The at the test laboratory with the TMD attached as shown in reason that a suction damper has been chosen is that se- Figure 12. 2017 EDITION 206 WWW.NET CTSS . This is in the same order of that of the damped TMD (Figure 11). f1 of 45 Hz can also be excited levels can be compared for that reason. TMD is very effective because the measured ratio in vibration levels with and without the TMD is 42. U-pipe with TMD. the on the TMD is a factor of three for the TMD and two for the largest strain will occur in the vertical parts at the mounting pipe system. TMD to tune mode 2 (vertical mode). TMD. and it was shown that it is sometimes very difficult to reduce the vibrations in the field to accept- able levels with traditional vibration mitigation measures. and (2) Vertical translation of the overhanging end. which support the suction dampers. The damper has a mass of 6614 lb. because experience has shown that these modes have exhibited large vibration problems. stiffening is not feasible anymore. The two investigated modes il- lustrated in Figure 16 are: (1) Rotation of the damper around the cylinder nozzles denoted as mode 1 at 27 Hz. For that reason the application of a CLD or a TMD could be a feasible solution to mitigate the vibrations. Suction pulsation damper. stiff structures. However. For that reason the focus was on the investigation of applying a damped TMD. (3000 n Figure 17. Frequencies between 50 and 100 Hz have been ob- served in several projects. n Figure 14. kg). which is much less than the values of the U-pipe.NET CTSS . it was not possible to test this in the field. Mode shape at 27 and 77 Hz. In general. The reduction of vibra- tion levels with a factor of two was not enough to achieve n Figure 15. Arguably. MNF far enough from the excitation frequencies. 2017 EDITION 207 WWW. Test pipe including the CLD. Preliminary calculations with the application of only CLD attached to the damper have shown that the damp- ing could be increased by a factor of two. n Figure 18. denoted as mode 2 at 77 Hz. TECH BRIEF acceptable vibration levels. with these dampers. because of the rather high frequencies and high eleva- tion of these dampers for large compressors. are applied to shift the n Figure 16. but a spare pulsation damper could be bor- rowed from RWE for the tests at the laboratory as shown in Figure 15. These are typical modes of such a damper. Unfortunately. A finite element model of the pulsation damper has been generated. and two typical mode shapes have been selected for improvement of the system.CTSSNET. cylinder stretch is the major source of most of the suction damper vibration problems. (75 kg) and 44 lb. Suction pulsation damper. 2017 EDITION 208 WWW.CTSSNET. For that reason. The damping effect of a CLD is largest at levels is 17 for mode 1 (f2) and 13 for mode 2 (f2). and the conclu- is shown in Figure 17. FRF of mode one of the pulsation damper.NET CTSS . one geometry was mode two. the minimum reduction factor of the vibration on both sides. Figure 18 shows the TMD mount. chosen with adjustable masses. TMD to tuned mode shape one (rotation around nozzles). The measured frequencies of mode one and n Figure 20. This the location with the largest strain. The spring of the TMD From the measured FRFs as shown in Figure 20 and was a leaf spring with a CLD layer adhesively bonded Figure 21. the minimum calcu- two are respectively 165 lb. Hz is a local resonance of the baffle choke tube inside The curved geometry also has the advantage of reducing the damper. Similar to the TMD of the U-pipe. A detailed view of the TMD the TMD. modes. sion is that the application of the damped TMD is very ed on the cap of the damper to tune mode two (vertical effective. n Figure 21. Figure 19 shows the TMD mounted to tune mode to determine the mass of the TMD for the two selected one (rotation around the nozzles). The mea- of the leaf spring as shown in Figure 17 and has been surements also show that the measured frequency of 76 achieved by applying a curved geometry at that location. which is a positive side effect. the first step was mode). (20 kg). This is at the “bottom” means that the quality of the model is good. The calculated mass for mode one and mode From the results of the calculations. lated ratio of quality factor of the damper without and with The target was to apply one TMD system that could be the damped TMD is a factor of 13 for mode one and 14 for used for both modes. This mode is also damped significantly by the cyclic stress in the TMD. TECH BRIEF n Figure 19. University of Dayton. in reducing the vibration and cyclic stress levels. the reduction factor is much Tuned Mass Dampers To Control Vibrations of Composite larger and reaches the quality factor at resonance of the Floor Systems. Constrained viscoelastic mechanical analyzer (DMA). must be widely known. (1996). Inc. pressor by applying multiple adjustable constraining The damping of the TMD with CLD has a very large effect bands with damping layers. Tabak. de Vreugd.P. (2005). 1969. D. Experiments with a large pulsation damper have shown [16] Dynamic Mechanical Analysis: A Practical a reduction factor between 13 and 17. D. which is significant. Haritos. [3] Y.J.A. CRC Press. The advantages of a CLD are that they are very effective [7] H. After detailed inspection of the TMD. PhD Inman. P. F. for lending the pulsation damper. [10] E. A. H. D. A. Damping of flexural waves by erties are strongly temperature dependent. Wan. G. [15] J. the MNFs in the field. Mohammed. treatments. is more beneficial to apply a damped TMD instead of a CLD [13] C.C. Gad. it is strongly recommended to measure. Pau. Z. by the curvature. Plunkett. be achieved with nontraditional vibration mitigation tech. 2013. damped sandwich beam with arbitrary with CLD. (1956). Human. shall be measured. Such a model requires the input of the damping. it cylindrical shell with minimal passive damping patches. Gordon. of passive constrained layer damping treatments for vi- if possible. system. J.” Engineering Journal/American Institute original system. Q3/1992:116-124. J. Another research project revealed that CLD is a very ef. E F Gad1.D. 2008.W.CTSSNET. Length Optimization that the bonding of the CLD at the foot was not optimal. tal comparison of piezoelectric and constrained layer ement modelling.NET CTSS . 2002. Environmental Testing. a constrained viscoelastic layer. Moreover the TMD should be Conference on Space Constructions. Balmes.S. R. of Steel Construction. J. A D GmbH. landing gear system. Prentice-Hall. Optimization to optimize a TMD. 2008. E.and R. Winters.H. I. E.1996. Fang. To be able [4] H. it was also concluded [2] R. such as mode shape. G. mode of interest for a variable-speed compressors. “Damping in Space Constructions. N. Transfer func- Conclusions and recommendations tion method for frequency response and damping effect The project has shown that a large reduction in vibration of multilayer PCLD on cylindrical shell. 2017 EDITION 209 WWW.S. C. Optimum Design for Passive Tuned Mass niques. TECH BRIEF mode two deviate from the calculated frequencies. An experimen- mance after application of CLD can be made by finite el. Engineering Vibration. J. depending on the Introduction. Kerwin. Noise reduction of a refrigerator com- which an adhesive bonding layer cannot handle very well. Zheng. To design the best TMD. J L Wilson1. Liu. test/analysis correlation on an aircraft engine. 2010. [8] J.” possible. levels of parts of reciprocating compressor systems can [6] I. Zheng. Taulbee. caused for Constrained Viscoelastic Layer Damping. T. Saidi. de Lange. Materials and designed in a way that it can be tuned in the field. J. have shown even a larger reduction factor of 42. The effect of temperature damping. In case [17] Webster. Minimizing in reducing the risk of fatigue failures at low costs. [12] R. such as suction pulsation dampers. Experiments with a U-pipe configuration with CLD have [11] D. Lee. G. S. The prediction and optimization of the damping perfor. They vibration response of cylindrical shells through lay- are also easy to install and are very effective for a large out optimization of passive constrained layer damping frequency range. The and turbo compressor applications where frequencies are School of Engineering. [18] Al-Hulwah. Hollkamp. N Haritos3). Wilson. K. The curvature causes a tensile (peel) stress. bration control of cylindrical shells. Tests with a damped TMD of a three-layer. Passive viscoelastic con- because it is more effective. viscoelastic properties that are measured with a dynamic [9] E. 1958. must be included in the DMA because the viscoelastic prop. clamping of the nozzle end. the dynamic properties of the [14] ANSYS reference manual. R. 2009. 1968. 2005. generally much higher. Dampers Using Viscoelastic Materials. quency and damping ratio. LU. 3. and if Kamphues. Vaicaitis (1992).C. Liu. mechanical natural fre. G. 2006. Mechanical Vibrations. Mead. Moreover. this is caused by the imperfect [1] Hartog. Pau. The forced vibration shown a reduction factor of 20. As References explained for the pipe.M. [19] Optimum Design for Passive Tuned Mass Dampers Acknowledgement Using Viscoelastic Materials Australian Earthquake The authors would like to thank RWE Gasspeicher Engineering Society 2007 Conference (I Saidi1.H. Vibro-acoustic analysis of a thin For larger structures.F. 2nd Edition. R. Gallimore. such as CLD and damped TMDs. Floor Vibration Control Using fective way of mitigating vibrations experienced in screw Three Degree of Freedom Tuned Mass Dampers. 2014.J. the additional damping strained layer damping application for a small aircraft of the TMD reduces the risk of fatigue failures of the TMD. boundary conditions. “Application of of a fixed compressor speed.L. Markus. McGraw-Hill. et al. CTSS Mohammed2. [5] Q. Kevin Menard. Qiu. however. the bearings must during the slow roll of the compressor. tion of a hydrostatic and hydrodynamic journal bearing. Based on the above formula. cannot be compromised at any point of operation. This means the slow be capable of withstanding high journal load with low. roll window is 200 to 400 rpm. Thus. option to use in a system.CTSSNET. with standard rotor bearing design. C = radial clearance. the rotor starts to cool and buoyant convection current leads to development of thermal gradient across the axis of compressor rotor. when starting Nt = (S x PL / µ) (C/Rs) x 60 VSD induction motors. rpm with an operating speed of 11. the motor has to run below 400 rpm frequency drive (VFD) electric motors. Stribeck curve. if the compressor’s first resonant speed is 4000 drives (VSD) to enable slow roll of centrifugal compressors. the lower part of rotor cools faster than the upper segment. With large electric motor driven centrifugal compressors having similar configurations. This paper suggests the type of bearings that may be speed of 150 rpm for a 1450 rpm electric motor. Mantosh Bhattacharya is a rotating equipment technical specialist for In this case. For ex- used in heavy-duty electric motors that use variable-speed ample. One OEM of aeroderivative gas turbines (two shafts GT) has employed this technique [1]. this is not feasible n Figure 1. As the hot gases rise.NET CTSS . PL = bearing unit load. Vogelhoff’s empirical equation can be used for larger than those generated over the remainder of the speed estimation if hydrostatic jacking is needed. hydrodynamic lubrication With this information.TECH BRIEF Slow Rolling Centrifugal Compressors Proper electric motor bearings can mitigate rotor-stator rubs during a hot restart of a centrifugal compressor BY MANTOSH BHATTACHARYA A phenomenon known as “temporary rotor bow” can occur with centrifugal compressors during startup after a short shutdown (known as a hot restart). a different bearing arrangement The hydrodynamic lubrication follows the Stribeck curve is needed. In this case. in which the required operating regime must be hydrody- For VFD drives running between 0 and 10% of maximum namic. On lift off speed speed. in a fixed-speed system since the variable frequency drive is µ = dynamic viscosity. He has 25 years of experi. To fix the slow-roll speed of the driver and surface asperity. which is attained just at lift speed. sliding velocity. most users choose to begin the active The empirical formula for lift off velocity is as follows: operating range at a speed above 10%. The liftoff speed must satisfy Somerfield centrifugal compressor.000 rpm and a gearbox To exercise the slow-roll option in heavy-duty variable. Because of this. the hydrodynamic bearing lubrication number criteria [2]. “hybrid” bearings should be explored as an Petrofac in the United Arab Emirates. range. they behave in the same manner as Where S = Somerfield number. At 2017 EDITION 210 WWW. After the centrifugal compressor stops. the slow roll can start only with a cannot be achieved with a heavy-duty electric motor with low journal speed at high journal loads. A compressor can be slow-rolled to get rid of thermal bow of steam and large gas turbines. The thermal gradient generates over a period of time and causes the rotor to bow due to differ- ences in stress along the two halves. A hybrid bearing is a combina- ence with rotating equipment. Rs = journal kept out of the loop. most produce fluctuating torques that are several times of journals. speed ratio of seven. plored by OEMs to evaluate how they can be incorporated The bottom half shell B is provided with two hydrostatic into the design. 2017 EDITION 211 WWW. driven. If the main lubrication pump is shaft- (slightly above the lift off speed). and Michele Fontana. by M. B. especially to introduce slow roll to mitigate pockets (one on either side of the vertical center line) with high vibration due to possible transient rotor bow. patent 9243644. TECH BRIEF n Figure 2. If the motor is required to be slow rolled. by W. Jacking oil is sup. At higher speed (higher than lift off velocity) hydrody.NET CTSS . the speed parameter value of zero.Lu. by Gianni Bagni.CTSSNET. 1983. with load-carrying capacity based higher speed because the bearing land area encroaches on on the supplied pressure of the lubricant injected as jacking the recess area. Rowe-Butterworths. The duration of slow roll is to be set in such way that it During startup of a slow roll. the journal should be jacked removes the thermally induced bow of the motor rotor as well up using a hydraulic jacking system up to a certain speed as the compressor rotor. plied under the rotor at a pressure sufficient to lift the rotor Slow rolling a heavy-duty electric motor can remove transient off the bearing surface while the machine is slowly rotated. It should connection for the high-pressure jacking system (Figure 3). the bearing operates at unable to generate substantial hydrodynamic lubrication at pure hydrostatic mode. n Figure 3. Leonardo Baldassarre. Adequate protection is also required to protect the driv- ing motor for possible sub synchronous vibration and other instabilities due to the use of hybrid lubrication.S. which has been reported in some cases. heavy-duty rotors. [2] On lift off velocity of Journal Bearing — Tribology Letters. be noted that recessed journal bearings are sometimes The slow-roll speed should be selected in such a way that it has a minimum of 10% separation margin of lateral critical speeds of motor and train torsional critical speeds. Whole entry hybrid bearings may be used oil. Scheme of jacking for a hydrostatic bearing. The operational philosophy is ing. then it is also that large. Khonsari & X. use a jacking oil system. Hybrid bearing. then its capability to pump the required oil pressure Hybrid bearings in heavy duty VSD motors can be ex. ing. like the main steam turbines imperative to ensure that the rotor armature and cooling sys- in power plants.M. with careful consideration of the slow-roll speed selected for the compressor and driver. [3] Hydrostatic and hybrid bearing design. bending of the motor rotor occurring due to differential cool- for instance. on the turning gear. tem is designed to adequately dissipate the generated heat. A separate Campbell diagram for torsional critical speeds should be plotted. CTSS References [1] Method and device for controlling a hot restart of a centrifugal compressor — U. and volume must be ensured during slow roll. for better performance and reduce the cost of manufactur- namic action dominates [3]. Antonio Baldassarre. December 2005. These compressor operation. Colorado. brication rates. without changing the designs or critical areas within the cylinder and packing. so operating costs could be significantly reduced. where he is Design considerations involved with compressor lubrication systems and other related Reciprocating gas compressors are used in a wide projects. range of applications. which accumulates con. where he determine the worst operating case so an oil type and lube specializes in troubleshooting and analyzing field failures. which proportions the oil to livered to each lube point. The first is a recirculating system. The second system is a total-loss system. the worst case is the has more than seven years of experience in troubleshooting operating case having the greatest final-stage discharge and analyzing compressor equipment.. also known as the force- Cost reduction can be achieved with relatively simple steps feed system. thrust plates and crossheads in the take into consideration the associated costs in collection.NET CTSS .000.712 L) annually. most often operate continuously. Compressors A 1000 hp (0. Typically. as well as steps to ensure the lube minute. This paper describes of oil at the critical areas is on the order of drops of oil per the established method. drivetrain. cylinders. bushings. or mixes with the gas flowing thru the compressor cylinder. These additional costs can significantly add to the annual and packing rings. Yance has more than 15 years of experience in design. and gallon for synthetic lubricants. while larger compressors can ap- siderable runtimes on wearing components. which hauling and disposal of oil downstream of the compressor. piston rings. Making efficient use of oil within Abstract the cylinder lubrication system is key when minimizing op- Tens of thousands of reciprocating compressors op. uses a positive displacement plunger pump to ascertain the correct type and quantity of oil being de. In general. Reciprocating proach 6000 gal. to feed oil to a divider valve. pressors is imperative to equipment reliability. to provide long-term reliable overcome gas pressure present at each critical area. Justin Yance is a design engineer for Ariel Corp. This annual cost does not bearings.786 kPa gauge).TECH BRIEF Lube Reduction In Reciprocating Compressors Method designed to ensure proper operation of lubrication systems Editor’s Note: This paper was presented in October at systems is how the oil is used. erating costs while maximizing equipment reliability.CTSSNET. (22. Joe need to be evaluated by the compressor manufacturer to Hagan is a technical service engineer for Ariel Corp. essary. (7570 L) of oil annually. The details for each application manufacturing and troubleshooting compressor equipment. provides oil to the cylinder bore.000 per year in lubricating oil.. pressures typically range from almost atmospheric to 3000 psig (20. the annual oil cost for one packings. Considering oil can compressors rely upon two lubrication systems that deliver cost $7 to $15 per gallon for mineral oils and $20 to $50 per oil to critical components in the drivetrain. A cylinder lube system only uses its oil once before the oil is consumed in BY JUSTIN YANCE AND JOE HAGAN the compression process. The oil type recommended is based on the ex- vibration analysis. field data collection and pressure. He rate can be recommended. which protects compressor can reach $250. The drivetrain reuses its the Gas Machinery Conference in Denver. The flow rate materials of the wearing components. The cylinder lubrication system. The oil must be delivered at sufficient pressure to system is operating correctly. oil many times before this fluid is replaced. This erating in North America each consume as much as paper presents the established method for maintaining the US$250. the oil either migrates to lower pressure regions Maintaining proper lubrication on reciprocating gas com.75 MW) compressor can consume 2000 gal. The major difference between these two oil cost related to compression. pected viscosity loss once the oil is injected to each critical 2017 EDITION 212 WWW. piston rod. Once the oil is injected to the criti- Introduction cal area. most cylinder lubrication system and determining appropriate lu- of these compressors are consuming more oil than nec. pending on severity of service. some amount of lube rate reduction can Compressor original equipment manufacturers (OEMs) usually be expected once the break-in period has ended. made based upon grouping applications into general gas In extreme cases. Lube recommendations are excessive temperatures. hydrocarbon) and oil starvation The recommended cylinder lube rates and oil types are also interfere with oil film quality by decreasing oil viscos.NET CTSS . Two applications may share the same rapid component failure. verity of service. cleanliness. contamination (e. heavier hydrocarbon gases and requires half the “normal” lube rate at rated speed). pressure and operating speeds is reduced proportionally (operating at half-speed temperature. for an independent oil supply if the oil recommendation tion. can’t also be used for the compressor frame. have arrived at their own methods for determining lubri..5 and 3 de. their actual conditions.g.5 pints/day/inch of part diameter. This is the first sheet of cigarette paper and it is soaked completely through with oil. In some cases. In general.3 to 0. this can impact the The lubrication rate is altered via a base rate multiplier divider valve selection. resulting in decreased viscosity and lube rate is recommended which increases the amount thinner oil films protecting components. sized for an estimated set of conditions may arrive at an oil tween 0. which decreases component life. 1 at the beginning of test with normal lube rates. The size type or lube rate that is grossly inadequate or excessive for of compressor frame determines which base rate is used. The calculation determines It is important to note that packings can generate dif- the normal lubrication rate requirement for a component ferent amounts of heat depending upon the compressor 2017 EDITION 213 WWW. Ariel starts with a base rate that ranges be. category but differ in how aggressive the conditions actu- Lubrication rates determine how often oil needs to be ally are toward the lubricating oil. and need depending on the discharge pressure and gas composi. To avoid losing too of oil to 150 to 200% of the normal rate. throw No.CTSSNET. a break-in come more diluted. Compressors that had their cylinder lubrication systems cation rates. force-feed pump sizing. Poor lubrication results in unknown or upset conditions. Depending on the se- added to critical areas in the cylinder lubrication system. The additional much viscosity. Oil viscosity is affected operating at the frame rated speed. in most cases conservative to account for some level of ity and/or removing the oil film. Liquid debris as components conform to each other. a thermal runaway condition can lead to stream categories. Base rate multipliers range between 0. area of the cylinder lube system. For higher discharge pressures cause the cylinder oil to be. TECH BRIEF n This sample was taken from the third stage. water. the first 200 hours of compressor operation. heavier ISO grade mineral oils or synthetic break-in oil helps cool components and flushes away wear lubricants resistant to dilution are recommended. Operation at slower by gas composition. The cylinder lube system setup needs Lube rate factors: to be correct and deemed in good working condition (reli- • Gas composition and quality able) prior to reducing the lubrication rates. This is an example of over-lubrication. TECH BRIEF n This is the second sheet of paper from the sample in from the third stage. 1. fittings. • Heat tracing to improve oil flow • Filtration to improve oil quality Considerations for lube reduction • Faulty check valve Many factors can influence the lubrication rate require.CTSSNET. Systems should • Compressor operating speed already exhibit satisfactory component service lives and • Oil type and viscosity grade for cylinder lube system performance prior to reducing lube rates. This paper is marked with oil that soaked through the first sheet. • Correct lube line arrangement to/from divider valves Lube rate reductions must be done methodically to 2017 EDITION 214 WWW. The current compressor setup needs to be reviewed be- ment and how reliably oil is delivered to critical areas in the fore pursuing a lube rate reduction.. Factors may be found cylinder lube system. the cylinder lubrication system may no longer be op- • Frequent start/stop operation erating correctly or be sized for the compressor application. throw No. Oil delivery factors: The cylinder lube system hardware and lube sheets may • Force-feed pump and divider valve bore/piston wear need to be updated to achieve an appropriate starting lube • Installation and sizing of balance valves rate for the current operation. tubing. The system needs to tolerate the most diffi- • Force-feed pump and divider valve sizing cult application the compressor will see while in service. damaged connections.g. Large • Lubed component wear and geometry changes amounts of heat generation will require the packing to be • Oil supply (day tank) feed line arrangement cooled with water — or in some cases oil — in order to • Line sizing to improve oil flow maintain a reasonable operating temperature.NET CTSS . Below are the most common factors that developed or were not considered in initially sizing the that need consideration prior to modifying lube rates: cylinder lube system.. application. • Part geometry (e. cylinder bore sizes) The cylinder lubrication system is typically sized for a • Cylinder discharge pressure particular worst-case compressor operating condition or • Operating temperature application.g. may warrant increasing the recommended oil viscosity to O-rings) offset the viscosity lost at the increased temperature. • Recycling gas saturated with lubricating oil Depending on the age of the equipment or how the unit was • Deactivating cylinder operation sized. The additional heat generated by the packing • Leaks (e. the lubri- ture can be monitored to note changes in operating condition. in good operation. For these com. Parameters to be recorded: • Measured packing leakage/vent temperature prior to shutdown • Piston rod diameters • Piston ring /wear band groove widths / depths • Cylinder bore inside diameters • Packing case dimensions with regards to packing cup depth n This paper is from the third stage. inspections at regular the break-in rate to the normal lube rate. • Cigarette paper tests showing lubrication quality in cyl- ly lubricated cylinder. cation reduction procedure can be instituted and followed.NET CTSS . This verifies the amount of oil and quality on components. the vent line leakage and/or tubing contact tempera. A consistent tubing location (nearest the packing case) and method for verifying contact temperature is required. Related issues on wear components may lead to further investigation into what the failure mode is and may result in any lube reduction being suspended until fur- ther investigation is performed. Tools required for inspections: nificant costs depending on their severity: • Gas flowmeter to measure packing leakage • Labor (overtime) = $2000/day • Thermometer to monitor packing vent/drain temperatures • Packing and piston ring replacement = $3000 • Vernier calipers • Expedited shipping = $4000 • OD micrometers for all piston groove diameters • Cylinder replacement = $25. age components due to increased operating temperatures. procedures must be instituted to en- New ring components are fed additional oil as they break. To determine in period. Field lubrication reduction procedure Once an application is determined to be a good candidate Break-in lube rates for lubrication reduction. along with other major components like piston rods and cylinder bores to fail. inder bores on all stages • Force-feed lubrication system should be reviewed to be avoid under-lubricated conditions that accidentally dam. Some equipment may inadvertently operate for ex- tended periods at the break-in rate because the lube rates were never reduced after the break-in interval. It is difficult to inspect oil films inside the further lube reduction. a thorough inspection should be performed. 1 after 7022 hours • Piston ring radial thicknesses. After the break. the ap- Evidence of marginal lubrication indicates when lube rates plication can then be reviewed to be a good candidate for need to be increased. These inspections include: 2017 EDITION 215 WWW. This indicates an adequate.000 • ID micrometers or dial bore gauges for cylinder bore • Lost production = $40. wear bands and packing. good quality lubrication on all wear components. widths running at 50% lubrication reduction. nents and six parameters are monitored closely. Inspection prior to lube reduction It is important to identify any history related to acceler- ated wear on components such as piston rings. To aid in recognizing any accelerated wear on compo- nents lubricated by the force-feed lubrication system. lubrication rates must be manually reduced from proper lubrication to all components. This inspection should include a pressure test of di- Excessive temperatures can cause piston/packing rings vider valves. TECH BRIEF normal lube rate typically reduces oil consumption by 33% to 50%. Component failures can accrue sig. throw No.CTSSNET. widths sheet and lightly marked the second sheet. has not experienced excessive wear and shows to have ponents. sure proper application of lubrication to all force-feed compo- in during their first 200 hours of operation. If all inspections reveal that the unit packing due to how the cases are constructed. • Unwaxed cigarette papers tion. Changing to the time intervals must be done. Once all information is gathered prior to testing.000/day diameters The reduction process requires slowly decreasing the lube • Depth micrometer rates and performing periodic inspections after each reduc. Oil soaked through the first • Wear band radial thicknesses. Lubrication reduction time intervals. mensions should be compared to original measurements at the start of the test to identify any considerable wear. Reduce lube an additional 10% 1 month 2 months 20 Shut down for inspection. wear bands.0625 in. Ideally. Reduce lube an additional 10% 1 month 5 months 50 Shut down for inspection. Reduce lube an additional 10% 1 month 4 months 40 Shut down for inspection. ers of regular unwaxed cigarette paper together. If satisfactory. The test compartments and piston rods is carried out by the following steps: Worn sliding surfaces can accelerate ring wear and in- • Using light pressure. Piston rods should be visually cumference. be sure to saturate one layer of cigarette paper. surface.CTSSNET. If satisfactory. If satisfactory. Begin A visual inspection of cylinder bores and crosshead guide at the top and wipe downward about 20° (between 0. Continue operation at 50% 6 months 8000 hrs 50 Shut down for complete inspection. crosshead guide representation of cylinder oil film during operation. to specific points based upon paper test results. both papers stained through rings. removed from components. The paper test should be per- formed within one hour of stopping the unit to get the best Visual inspection of cylinder bores. rings seal and whether sealing surfaces are worn or damaged. using two clean papers for each side. TECH BRIEF Cylinder lubrication paper test take into account emissivity and area of the measurement This test estimates the amount of oil present on the cyl. with the inspections outlined above. of unwaxed cigarette paper. If cylinders • Measure packing leakage from packing vent/drain to appear under lubricated. the divider valve arrangement may be able to be • Measure packing vent temperature as close as possible reconfigured by the compressor OEM to tailor oil delivery to crosshead guide. Using an infrared thermometer. move to next step. Reduce lube an additional 10% 1 month 3 months 30 Shut down for inspection. along from the top. crease leakage rates. All di- may indicate over-lubrication. but the second paper should Inspections should be conducted at the time intervals not be soaked through. move to next step. move to next step. lubrication should be increased in monitor increased gas leakage due to wear occurring in 10% increments until proper lubrication is restored on cylin- the packing case. If satisfactory. If satisfactory. • Repeat the test at both sides of the bore at about 90° At the conclusion of the test at the 8000 hour mark. The paper against the bore surface should inspected for scoring or signs of excess heat. Packing leakage inspection If at any point in the test packing leakage/temperatures in- Packing leakage flow rate is an indicator of how well packing crease or lubrication quality is marginal on any cylinder bore. cylinder lube points will have enough oil on the bore to only age is occurring. all This measurement will indicate if increased packing leak. depending on bore size) along the bore cir. wipe the cylinder bore with two lay. piston indicate under-lubrication. If specific lube points appear to have marginal permanent gas flow meter. piston assemblies Paper against the bore surface not stained through may should be removed to inspect piston ring grooves. be stained (wetted with oil). 2017 EDITION 216 WWW. CTSS Elapsed Time Total Run Total Lube Reduction Interval Time From Normal Rate (%) Startup at break-in lube rates 0 0 Break-in rates are 150-200% of normal Set system to normal lube rates 200 hrs 200 hrs 0 Review conditions Reduce lube 10% from normal rate 1 month 1 month 10 Shut down for inspection. piston rods and cylinder bores. n Table 1.35 compartments to identify any wear materials that have been to 4. This can be done with a portable or der surfaces. A baseline temperature measurement with new inder bore by transferring oil from the bore to thin layers packing is required to identify any increase in leakage. outlined in Table 1. move to next step.NET CTSS . move to next step. lubrication. the lubrication reduction should not continue. Purchasers And Training Providers CTSSnet.net COMPRESSION TECHNOLOGY SOURCING SUPPLEMENT COMPRESSOR Dedicated To Gas Compression Products & Applications . COMPRESSION SOURCING TECHNOLOGY SUPPLEMENT SYSTEM REPAIRS The Industry’s Leading Reference Tool For Packagers. Purchasers And Training Providers CTSSnet.net COMPRESSION TECHNOLOGY SOURCING SUPPLEMENT COMPRESSOR Dedicated To Gas Compression Products & Applications . COMPRESSION SOURCING TECHNOLOGY SUPPLEMENT SYSTEM REPAIR The Industry’s Leading Reference Tool For Packagers. . As Atmos Energy investigated the causes of packing fail- ure. Environmental Protection composed of 11 compressor stations and 5 gas storages totaling approximately 102. He has been in the industry for nine years with a focus on • 24 separable high-speed compressors improving field operations. Atmos Energy built a system to measure the gas leakage rate from each individual cylinder packing case. The system provides a visual indication of the rate relative to new packing. The rod attached to the piston has a W. The direct relation. 2012. small to the EPA. As an extension of this.S. Subpart pressed by a piston. The original packing vent Agency (EPA) in response to the federal “Climate Action monitor (PVM) and subsequent iterations have been imple. Typical reciprocating compressor rod packing system The system keeps a numerical measurement of the (U. it designed a monitoring system to indicate the condi- tion of the packing material.000 hp (76 MW).” stated that mented at several Atmos facilities. gas enters the suction chanical components that leak as they degrade over time.000 metric ship between running hours and packing degradation results tons per year of CO2 to report fugitive emissions annually in an increase in gas leakage over time.S. manifold. • 5 integral low-speed compressors 2017 EDITION 218 WWW. EPA. transmission. and requires facilities producing over 25. Colorado. n Figure1. and leaks per cylinder among the thousands of compressors facilities are expected to use Best Available Monitoring throughout the oil and gas sector (processing. the growth in the oil and gas sector has the potential to in- crease air emissions. In addition. which also helps keep track of fugitive emissions. Plan: a Strategy to Reduce Methane Emissions. The objectives were to reduce unscheduled outages for packing case replacements and to reduce gas losses. The EPA provides calculation methods. 2006a) quantity of gas vented to atmosphere. Green House Gas Monitoring 40 CFR Part 98. is the primary regulation that affects fugitive emissions series of flexible rings in machined metal cups (“packing”) to measuring and reporting. Compression overview Regulation Atmos Energy has 16 facilities throughout their system A 2014 report by the U.TECH BRIEF Case Study: Packing Vent Monitoring Atmos Energy uncovers the root cause of a compressor cylinder packing case failure Editor’s Note: This paper was presented in October at the Gas Machinery Conference in Denver. BY DANNY ATHAR Abstract Atmos Energy investigated the root cause of compressor cylinder packing case failure. and storage) add up to significant methane emissions. flows into compressor cylinder and is then com. These include: Danny Athar is an engineer for Atmos Energy Storage & Compression • 8 turbines with centrifugal compressors Group.CTSSNET. create a seal that limits the amount of natural gas that may The Greenhouse Gas Reporting Program started in escape along the piston rod (Figure 1).NET CTSS . A significant source of these emissions Packing case is from gas compressors — specifically the seals around me- In a reciprocating compressor. Methods (BAMM). .577 95 127.417 83 112.300 63 85..761 39 52... as PTC 17.328 The derived SI unit for torque (or moment of force) 7 9. grade) scale..607 47 63. The Newton is that force which..097 76 101. meter m second squared.502 42 56.000145 lbf/in2 or 0.540 44 59....774 34 45..233 lbf ft LUBRICATING-OIL POUNDS FORCE FEET (lbf ft) TO NEWTON METERS (Nm) PRESSURE AND STRESS CONSUMPTION (1 lbf ft = 1.710 69 92....Kelvin K Fuel consumption measurements will be based on the currently accepted unit.. and one meter is equal to kilo.138 38 50.0000102 kgf/cm2...208 47 63....212 91 122.387 27 36.546 liters/h 7 9.. 0...102 1 Nm = 0.. PS.779 78 104...161 41 54..360 metric hp HEAT RATE kW hp kW hp kW hp kW hp kW hp 1 hp = 0... energy and type... PK.. 1 kW being equal to 1.570 75 101.. gives it an acceleration of one meter per Electric current .820 40 53. 13 17.918 96 128.NET CTSS ...... this code is intended for tests of all WEIGHTS AND LINEAR for which the abbreviation SI is being used in all types of reciprocating internal combustion engines DIMENSIONS languages. and the “Weight” in itself will no longer apply..423 24 32.715 seems to be favored to indicate barometric pres.116 40 54..738 lbf ft = 0. In its Section 2.828 42 56..549 48 64.... this being based on the For Liquid Fuel 8 10.687 65 87.067 23 31.mole mol Kilowatt Hour (kWh).005 64 85.746 g/hph = 0.435 69 93.941 99 132.959 58 77.646 (sfc) specific fuel consumption (measured in lb/hph TORQUE or g/kWh). one bar being 100. The American Society of Mechanical Engineers 1°C = 273 K Surry.491 27 36.074 73 97.259 97 130. One Watt is a kilometer is a meter x 103.802 81 108.848 87 116. character is used without the degree symbol (°) nor. lbf ft Nm lbf ft Nm lbf ft Nm lbf ft Nm lbf ft Nm unit for pressure and stress should be the Pascal (Pa)... this is a very small unit.669 is the Newton meter (Nm).000 Pascal (100 1 Imp gal/h = 4.807 Nm = 7..746 kW = 1.751 31 41..282 77 104. ampere A SPECIFIC CONSUMPTION second squared.890 49 65.623 1 metric hp = 0.....871 90 120.184 43 58. it will continue to be common parlance to internal combustion engine referred to net power use the word “weight” when referring to the mass of an object.. kilogram kg when applied to a body having a mass of one Time. or 0.. and equal to 0. but it is important to note that the kilogram these being: both the FPS and corresponding SI units of meas. Known System of Units (Systeme International d’ Unites).. and 1 hp being the equivalent of 0. the gram (g)...165 57 77. so being virtually the same as the 9 12. this unit being one thousandth of a bar.521 58 78..).. there is a school that favors the kiloNewton 15 20.023 23 30.145 lbf/in2 or 0...664 63 84.014 metric 1 g/metric hph = 1.....22 Imp gal/h 5 6.589 61 82..641 60 80. will no longer apply for force.675 42. for which the SI unit urements are given.069 29 38.735 kW = 0.001 sure.36 g/kWh horsepower (CV.601 of pressure.020 kgf/cm2....245 6 8.012 65 88.282 100 134...870 kgf/cm2.840 87 117.34102 hp) 1 kW = 1.270 32 43.055 = kJ/kWh 1 lbf ft = 1.454 55 74... gram (kg) will continue to be used as the unit of versally used.504 lbf/in2 or 8 10... Description and Definition of Terms.810 56 75.CTSSNET..001644 lb/hph = millimeter is a meter x 10-3.438 77 103.189 88 118.226 to the Celsius unit.466 100 135....346 61.705 81 109.254 53 71. One Newton (1 N) is 11 14...110 99 134.956 kPa)....414 = kJ/kWh 18 24...742 53 71. 1 1.014 metric hp Heat Rate is a product of Lower Heating Value 1 1..420 Or 19 25...098 54 73....138 kgf m 1 kgf m = 9... with a wide range of multiples and sub- quantity of heat – the Joule (J).433 33 44. Use of Celsius 1 lbf/in2 = 0. The 1 g/hph = 1.341 hp 1 lb/hph = 608. being equivalent to just 1 g/kWh = 0.010 SI unit of force — the Newton (N) – and the SI unit 9 12... Btu/hph X 1.. mechanical.530 89 119.847 28 37..410 30 40...715 gram force (kgf) and one member is equal to Heat Rate (Btu/hph) = LVH (Btu/ft3) 14 18...... for engine performance purposes...472 41 55.184 44 59...405 38 51.. KT6 6HA England..687 95 128.761 20 26.964 3 4...889 European engine designers favor the bar as the unit 1 liter/h = 0.28084 feet (ft).159 per square meter (kN/m2).263 90 91 122..867 45 46 60.392 71 95.233 60 81....693 36 48..214 74 100...061 82 111.. so direct conversions can be 20 27.0102 a temperature of -273.305 fuel and Btu/ft3 or kJ/m3 for gas fuel) multiplied times 4 5.. which is ment of lube-oil consumption will be quoted in liters 3 4.349 80 108. the tables below give examples.98 bar “Vehicle Metrics” published by Transport and 0 K = 273°C.056 3....364 24 32..033 (lb/hph) equivalent to 0.595 54 72..341 hp = 1..582 1 bar = 14..196 88 119.797 37 49.323 62 83....600 98 131. which is becoming uni.926 76 103.... The Kelvin unit is identical in interval 19 25. so the kilogram in effect should Amount of substance.398 97 131.733 72 96...638 78 105..712 22 29.300 59 79.507 85 86 113.101972 To convert these units to SI units: 17 22.791 69..503 72 97.3 g/kWh to SI units. A 14 18.092 32 42.... These tables are reproduced from the booklet 1 kgf/cm2 = 0.987 115.877 59 79.963 48 65.558 11 14.35582 Nm) Although it has been decided that the SI derived Although the metric liter is not officially an SI unit.479 39 52...619 92 124.341 21 28.533 only 0....894 93 124..341 k/kWh British unit of horsepower is equal to 1. One Watt (1 W) is cific energy consumption is expressed: g/kWh.147 70 94. KILLOWATTS (kW) TO HORSEPOWER (hp) (1 Kw = 1..803 temperature of zero degree Kelvin is equivalent to 16 21....515 18 24.. mass.......177 one Newton per square meter (1 N/m2).135 26 35. Then mally employed with other scales of temperature..374 kilogram-force (kgf).356 Nm = 0. Undoubtedly..572 51 68. so for engine ratings the 0.981 34 46.369 68 91. units/power units so that energy consumption of an though.447 again.. is founded on seven base units.772 84 113..166 66 88. this being the same as a kilopascal.. For Gaseous Fuel 13 17..456 36 48.386 52 70..552 89 120... so one Newton meter (1 N m) is X sfc (ft3/hph) 15 20..553 92 123..102 kgf m Btu/kWh X 1.668 currently accepted metric equivalent.461 80 107.526 34.896 45 61.046 25 26 33..993 79 107.986 hp (LHV) of Fuel (measured in Btu/lb or kJ/g for liquid 2 2. is based on low unsaturated The derived SI unit for power is the Watt (W)...331 94 127.079 kilogram-force meter (kgf m). while a very small unit of power. Also adopted is heat only be used as the unit of mass...737562 pound-force (lbf ft)..484 86 116.779 25 33.028 67 89. being the same as its use will continue to be permitted.....738 equal to 0..051 70 93.705 8.277 56 75.356 21 28.15°C on the Celsius (centi.. Surbiton.656 64 86.825 84 112.. for example.. So many per hour (liters/h). 17 23.5 lbf/in2 = 1.0197 kgf/cm2 made by adding or subtracting 273..724 67 90. etc. 4 5..808 73 98..10197 12 16...351 Heat Rate (Btu/hph) = LVH (Btu/lb) X sfc 10 13. Thus the SI unit of measurement for net spe.128 85 115..368 66 89..7457 kW.069 bar is still permitted.975 93 126.913 52 69.312 1.. meter. Thermodynamic temperature .....626 33 44. 5 6 6. second s kilogram.. which is a kilogram meter per Length.754 98 132.... is the Newton (N)..024 123.936 55 73...235 94 126. SI UNITS… THE INTERNATIONAL STANDARDS SYSTEM The system outlined here is the International Reciprocating Internal Combustion engines.. 118 Ewell Road.. multiples ranging from exa (1018) to atto (10-18): A equal to one Joule per second (1 J/s).692 of length – the meter (m).231 50 67.756 75 100.380 hand. Mass ... candela cd ambiguous term..944 62 84.914 30 31 40. and the 12 16...728 28 37. since this is an Luminous intensity.682 22 29....843 43 57.415 74 99.484 83 111.. For indications of “weight” the original metric kilo- for determining power output and fuel consumption.....319 49 66.982 61 81. the millibar The SI unit of temperature is Kelvin (K)..042 96 130. The SI system.... absolute zero K Distribution Press Ltd.202 29 39..... so measure. in 1973 published its Performance Test Codes for 2017 EDITION 219 WWW.907 71 96.397 16 21...00134102 horsepower..618 57 76.049 37 50.2248 pound-force (lbf) or 0.115 35 46...079 68 92. which is the equivalent of 14.736 g/metric hph To give an idea of how currently used units convert kilowatt (kW) is used. POWER output.030 50 51 67.337 35 47.821 2 2..120 79 105.251 46 62. On the other TEMPERATURES 10 13. this heat value of the fuel whether liquid or gaseous The base SI unit for linear dimensions will be the being based on the SI unit of work.143 82 109... Operations could then alert parts. this operation was frequently inter. n Figure 2. could cause the meter to lock and create backpressure geted. a communication cable connected to a remote mounted viding direct measurement of the flow.” This technique was effective.” When the whistle sor station that runs continuously and is critical to system sounded. Functionality is simple with no moving cases required maintenance. unscheduled outages became an unacceptable system supply problem. The configuration (Figure 3) has vented to atmosphere. cost and deliv- The first iteration of the PVM design included adding a ery. A second design improved on the original by utilizing a rotary meter (Figure 2) to measure the flow of vent Pilot installation gas at a common line. Texas. Initial setup of flow switch and test valve. for the project. Differentiating between normal and excessive A single LED represents new packing with the nominal venting required the operator to test a new set of packing leak rate of 5 to 10 scfh (0. meter and a switch are available by FCI. test vent. which can be calibrated in the field. as it would be a good inexpensive start the operator tested each cylinder for excessive venting. During 2011. This indicated that particular cylinder had rupted by unscheduled downtime due to packing cases worn out packing. and schedule the work. purchase materials emissions studies. Monitoring ter to directly measure the flow of packing vent gas. the rotary meter became very audi- South of Denton. Rotary meter n Figure 3. Atmos opted for mon line and flow through a test vent. Packing material was being replaced meter are quite small. noise stopped. Operations initially relied on visual displays 2017 EDITION 220 WWW. This required some finesse on the operator’s part. To save on space. During daily checks. Atmos Energy has a compres.14 to 0. Though a flow- allowed the operator to isolate the vent gas from the com. TECH BRIEF Background an excessive leak. Frequent downtime cost of materials and operator in all of the packing vent lines. When there was display unit. Atmos Energy’s solution for the Mass flowmeter unscheduled outages was to monitor the flow of vent gas A third design was proposed that utilized a mass flowme- that blows by as the cylinder packing wears out. and similar devices are used by the EPA in its fugitive system supply of an upcoming outage. since all of the compressor cylin. ble and produced a distinct “whistle. the cylinder. call-outs. Rotary meter installed on common packing vent line. communications. albeit rudi. Atmos each compressor cylinder individually allowed operations selected a mass flowmeter that was relatively inexpensive to detect excessive leaks and determine which packing and easy to install. Atmos ordered the remote mount der’s packing vent lines connected at that point and then kit for each flow switch. additional LED represents an increment in leak rate for mentary and possibly inconsistent.NET CTSS . as they Each flow switch has a 10 LED display as a visual indi- had to physically feel the passing gas venting through the cator of the flow rate. while considering Three-way valve size. oil build up or debris in the line every two months instead of every two years as bud. which by Fluid Component International (FCI). Atmos investigated several companies that could pro- vide flowmeters for this application. only the switch.CTSSNET. A device that fit the specifications was a flow switch three-way valve in-line with each packing vent line. the operator isolated each cylinder until the supply. because the tolerances in a rotary failing at a high rate. mounting options. The rotary meter worked well in a flow sensor in-line with the packing vent line and has conjunction with the previous valve technique by pro.3 Nm³/hr) and each as a “control. 204 pages US$24.95 Plus Shipping .4322
[email protected] “FAN LAWS” have nothing to do with spectator rules-of-conduct at sporting events.. The Illustrated Dictionary Of Because ..co/dictionary 1. Essential Process Machinery Terms Why struggle through useless Internet search results for technical terms? Order your copy today: http://dieselpub.800.558. Paperback. being that calibration utilized the LED lights with a flow- meter to get an accurate number. there was a PVM system quantify flow. Calibrating the flow switch in the field. displayed in Figures 5 and 6. The range used was based on packing leak rates published by Ariel: 5 scfh to a maximum of 120 scfh (0. ity located in north Texas. only.CTSSNET.NET CTSS . Refining calibration n Figure 7. Prior to installation. The flow switch installation was well received by opera- tions. Flowmeter on common line with isolation valves. another PVM system pressure (DP) gauge on the common packing vent line was installed at a different mainline compressor station displayed a reading in the control room and was con- that has identical compressor units.14 to 3. A secondary meter for verification was used to calibrate each flow switch. Flow sensor and test vent installed. PLC implementation plays together and as time went by. In addition. the operator noted that The next installation (Figure 7) was at a storage facil- the number of LEDs increased as the packing wore out. Each flowmeter had to be calibrated individually in the manner n Figure 4. previously installed by the skid packager. The facility has smaller com- The main criticism of the design was the need for an im.58 Nm³/hr). The installation was figured such that a high DP would alert the operators to nearly identical to the first station. Each flow switch was then set to zero and air was cycled through the flow switch and the second meter. the general rate was opted for rather than a quantitative display. the only difference an excessive leak in one or more of the packing cases. TECH BRIEF n Figures 5 and 6. pressors with less room to work with around the com- proved calibration method for the flow switches and way to pressor cylinders. This was resolved by mounting the flow sensor vertically and utilizing the three-way valve as a test vent (Figure 4). A differential After a successful pilot study. There was concern that oil and debris build up in the flow switch could cause false readings or produce back- pressure. with no signals going to the plant control system. Similar to prior attempts. each flow switch was calibrated in order to provide a relatively consistent display for leaks. 2017 EDITION 222 WWW. Daily checks allowed the operator to see all the dis. NET CTSS .CTSSNET.2016 EDITION XX WWW. Future considerations inder. operations can run the compressors and note their packing case conditions to establish a base case condition. Atmos took a slightly different approach to this de. Flowmeter with isolation valves plumbed together. There timately the PVMs serve the same purpose and provide was no method to isolate each cylinder when a high DP resolution to common problem. alarm was displayed. CTSS . This system is analog output was tied to the PLC and programmed to something Atmos would like to include in the specifications show the leak rate. benefitting Atmos operations by preventing unscheduled outages and monitoring fugitive emissions. alerting the operators to isolate each cylinder to find the leaking packing. ul- jump around on the screen and confuse operators. operations plumbed the tubing so each cylinder isolation valve is next to the flowmeter. mated system. An alarm would display if there were for all new compressor packages. Summary Atmos started with a quick solution to a problem that was both time consuming and costly. allowing a single operator to check for individual cylinder leaks. For this installation. Atmos installed the latest design (Figure 8) at another storage facility in east Texas with five compressors. This method was inaccurate because the numbers would Though each facility had different design preferences. Atmos will be looking at the possibility to log leak rates for sign by replacing the DP device with a flowmeter and each compressor and trend the data so they can determine adding isolation valves to each cylinder. The flowmeter’s what conditions reduce the life of packing. The PVM system evolved from a makeshift hands-on device to an auto- n Figure 8. Because of the lack of room to work around each cyl. Prior to storage in- jection season. TECH BRIEF an excessive leak. . www.com 2017 EDITION 226 WWW. With 3. 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[email protected] 2017 EDITION 227 WWW.NET CTSS . ZOLLERN North America T +1 713 673-7902 ZOLLERN BHW Gleitlager GmbH & Co. integrally geared compressor used in the pro- duction of oxygen for industrial processes. a natural frequency mode with a forcing function. the inlet guide vane (IGV) position had been set fatigue. His primary areas of expertise are fluid the original (baseline) impeller using ANSYS software: dynamics.TECH BRIEF Creating The Perfect Impeller Shape By Scalloping Sulzer study shows designs. Failure analysis of the original impeller Engineers at Sulzer’s service center performed a failure analysis to identify the reasons for the crack initiation. The cover plate the impeller with external excitation forces.5 to 464 psi(g) (5 to 32 bar[g]). He has 10 years of experience in design and re. of the impeller showed cracks Because of the lower supply needs of the plant. structural and modal analysis and test. This change may have increased them to propagate. induced down. (FEA). It compresses air from 72. other loads applied) to determine the impeller natural 2017 EDITION 228 WWW. which led Sulzer to the conclusion that the failure had been caused by fatigue mechanisms related to the interaction of n Figure 1. To run the compressor at turn. It is likely that these events. flow instability. its propagation and the liberation of the cover plate material. No material or workmanship defects were found. combined The impeller was ring tested to determine its natural fre- with a near-resonant situation caused by the proximity of quencies.NET CTSS . which initiated cracks in the impeller and caused close to design limits. BY KIRILL GREBINNYK A n Australian industrial gas company contracted Sulzer to perform an engineering study to analyze a recent impeller failure. Characteristic marks on the sur- face (so-called “beach” marks) indicated high-cycle fatigue failure. The compres- sor works as a booster compressor and is located after the main air compressor. The impeller is part of a multistage. The following numerical studies were performed for pairs of turbomachinery. Four sections of the cover plate showed cracks with missing pieces of material (Figure 1). failure analysis.CTSSNET. These natural frequencies were later used to validate the numerical model by comparing them with the Kirill Grebinnyk is an aerodynamics engineer at Sulzer (Houston frequencies obtained from a 3-D finite element analysis Service Center). operations can lead to impeller failure Editor’s Note: This article was originally published in the third issue of the Sulzer Technical Review 2015.000 operating hours. • “Free-free” modal analysis (with no rotational speed or ing of the rotating equipment. The impeller failed during operation after being in service for almost 40. Metallography was performed by collecting a replica of the fracture surface and inspecting it under a scanning elec- tron microscope (SEM). compressor operating regime had been changed from the rated point to a turndown mode over the last few months prior to the failure. the with missing pieces of material. Ft. Compressor Horsepower Selection Chart (Brake Horsepower Per Million Cu.NET CTSS .CTSSNET.26 WWW.) 2017 EDITION DISCHARGE PRESSURE (PSIG) 25 50 75 100 125 150 175 200 250 300 350 400 450 500 550 600 650 700 750 800 850 900 950 1000 1050 1100 1150 1200 0 65 99 128 144 156 168 178 187 203 218 233 233 241 248 254 260 266 272 277 282 286 291 295 299 303 307 311 315 3 10 35 63 85 104 121 131 140 149 163 175 186 196 205 214 223 231 228 233 237 242 245 250 253 257 260 264 267 270 20 43 62 78 92 106 118 126 139 151 160 170 178 186 193 199 206 212 218 225 231 226 229 232 236 239 242 245 STAGE 30 29 47 62 74 85 96 107 123 133 143 152 159 167 173 179 185 191 196 201 206 211 216 221 226 230 224 227 40 36 50 61 72 81 90 107 121 130 138 145 152 158 164 170 175 180 185 190 194 198 202 206 210 214 218 50 26 41 52 61 70 78 93 106 119 127 134 141 147 153 158 163 168 173 177 181 185 189 193 196 200 203 60 32 44 53 61 69 83 95 108 118 125 131 137 143 148 153 158 162 166 170 174 178 182 185 188 192 70 25 37 46 54 61 74 86 97 109 117 123 129 135 140 145 149 153 157 161 165 169 172 176 179 182 80 30 40 47 54 67 78 89 98 109 117 122 127 132 137 142 146 150 153 157 161 164 167 171 174 2 90 24 34 42 49 61 72 81 91 100 109 116 121 126 131 135 139 143 147 150 154 157 160 163 166 100 28 37 44 55 66 75 84 92 100 109 116 120 125 129 133 137 141 144 148 151 154 157 160 STAGE 125 25 32 44 54 63 71 78 85 92 99 106 113 117 121 124 128 131 134 137 140 143 146 229 150 22 35 45 53 60 67 74 80 86 92 98 103 110 114 118 121 124 127 130 133 135 175 27 37 45 52 57 60 71 76 82 87 92 97 102 107 112 115 118 121 123 126 200 30 38 45 52 58 63 68 73 78 83 88 92 96 101 105 110 113 116 119 250 26 33 40 46 51 56 60 65 69 73 77 81 85 88 92 95 99 102 SUCTION PRESSURE 300 23 30 36 41 46 50 54 58 62 66 69 73 76 79 83 86 89 350 21 27 33 38 42 46 50 53 57 60 63 67 70 73 75 78 400 25 30 35 39 43 46 50 53 56 59 60 64 67 70 450 23 28 32 36 40 43 46 49 52 55 58 60 63 1 500 22 26 30 34 38 41 44 46 49 52 54 57 550 20 25 20 32 36 39 41 44 46 49 51 STAGE 600 23 27 30 34 37 39 42 44 46 650 22 26 29 32 35 38 40 42 700 22 25 28 30 33 36 38 750 20 24 27 29 32 34 NOTE: 1 MMSCFD MEASURED 14.7 AND 60°F 3 SUCTION TEMPERATURE 100°F NOT CORRECTED FOR COMPRESSIBILITY 4 NATURAL GAS 2 “N”=1. speed line. in turndown mode. frequencies and validate them against the frequencies obtained from the ring test. The steady-state structural analysis revealed that there was a high stress concentration located at the fillet between the vane and the cover plate at the outside of the impeller diam- eter. This interference did not guide vanes. back- current case study is shown in Figure 2. Increased alternat- shapes corresponding to the sixth nodal diameter were iden. accounting for the effects of stiffness change due to rotation. For a fracture to initiate. There is an impeller natural as a SAFE diagram. the impeller mode which is unexpected at other regimes.NET CTSS . This is a graphical analytical tool pro. • Steady-state structural analysis to determine impeller stresses from steady loads at operating speed. • Pre-stressed modal analysis to determine the impeller natural frequencies at operating speed. flow effects from the diffuser might have appeared because Based on the diffuser and impeller vane counts and the of the low flow and they may have caused resonance. It aids in determining natural fre. However. but it was very localized and could not be deemed high enough to initiate a crack by itself. frequency closely resembles the failure pattern observed. TECH BRIEF n Figure 2. to be possible. 2017 EDITION 230 WWW. For resonance stress amplitude to increase and initiate the crack. This location matched the suspected site of the crack initiation. The interference diagram created for the rated operating point. which lies within 5% of the running posed by Murari Singh to identify resonance in turboma.CTSSNET. also known as a potential excitation source. possible interactions between them. The stress was close to the material yield strength limit. Because the mode shape associated with this chinery components. the impeller frequency on the diagram must there had to be an additional source of stress related to the coincide with both the compressor operating speed line impeller interference with the diffuser vane passing frequency. quencies that can potentially be excited depending on the this was identified as the frequency that was excited and running speed and number of stationary components (inlet that caused the failure (Figure 2). diffusers) and rotating vanes interacting in the cause any issues when the compressor was running near particular stage. and the exciting force mode shape (harmonics) identified The engineers used an interference diagram. The mode shape of the resonance frequency identified (right) resembles the crack shape. ing stresses due to the resonance caused the dynamic tified as potentially excitable mode shapes. The interference diagram (above) revealed a reso- nance frequency that caused the fracture. frequency at 4884 Hz. 4536 kg 0.394 30 1.850 67 2.6 343 650 1202 6.482 81 178.069 35 77. 1 kg/metric hp = 2.7 71 159.023 25 55.347 95 209.44 40 104.44 15 59.339 54 2.378 55 2.228 26 57.89 16 60.459 76 167. = 0.11 43 109.8 254 490 914 493 920 1688 L liter mph km/hr 1.961 98 216.370 100 220.252 -12.7 2 35.709 38 1.5939 -13.0716 -7.260 52 2.455 32 70.61 0.9 75 167.890 68 2.4 58 136.825 13 28.865 34 74.307 which is desired to convert into the other scale.621 12 26.660 33 72.0176 100 to 1000 571 1060 1940 849 1560 2840 C F C F 577 1070 1958 854 1570 2858 38 100 212 77 170 338 582 1080 1976 860 1580 2876 MILLIMETERS (mm) TO INCHES (in) 43 110 230 82 180 356 588 1090 1994 866 1590 2894 49 120 248 88 190 374 593 1100 2012 871 1600 2912 (1 millimeter = 0.6 11.906 43 1.3 83 181.8 100 212.8 143 290 554 382 720 1328 cm2 square centimeter lbf/ft N/m 14.640 72 158.093 40 88.039 21 0.2 23.6 204 400 752 443 830 1526 in.7457 -8.I.4 266 510 950 504 940 1724 cu.299 53 2.706 43 94.1 61 141.7 89 192.0 18.1 52 125.914 m 0.6 30.779 17 0.0 50 122.8 13.208 65 143. in.687 82 180.9 57 134.776 58 127.354 29 1.6093 -2.937 KILOGRAMS (kg) TO POUNDS (lb) (1 kilogram = 2.439 16 35.78 37 98.6 51 123.480 83 3.78 18 64.9 13.0283 m3 0.0185 -15.528 91 200.189 66 150 302 100 212 413 610 1130 2066 888 1630 2966 2 0.323 79 3.733 92 202.0 35.984 4 8.953 95 3.2931 kcal/hr 0. cubic foot Btu/hr W 0.957 54 119.205 76 2.795 91 3.8948 kg/cm2 0.008 71 2.3 74 165.6093 km/hr 1.56 22 71.433 31 1.571 57 125.8 227 440 824 466 870 1598 in.732 64 2.8 73 163.0283 m3/min 0.6 60 140. = 0.913 94 3.7854 L 3.2 54 129.945 44 1.617 67 147.3 56 132.710 87 191.436 71 156.2 31.0929 -16.102 48 1. 7.67 44 111.0 166 330 626 404 760 1400 Btu/scf kJ/mm3 37.277 80 176.6 232 450 842 471 880 1616 kJ kilojoule -5.2 216 420 788 454 850 1562 psig kPa gage 6.548 52 114.409 22 48.2 28.819 18 0.6 316 600 1112 N/m2 Pascal From Metric By 3.8 55 131.3558 N•m 1.551 34 1.835 92 3.827 41 1.204 21 46.CTSSNET.2 243 470 878 482 900 1652 kPa kilopascal °F (Interval) °C (Interval) 5/9 °C (Interval) 5/9 -3.7457 kW 0. 7 0.007 9 19.3048 -2.7854 -0.583 VOLUME PISTON SPEED WEIGHT/HORSEPOWER 12 0.502 42 92.8 35.1 10 50.779 3 6.33 17 62.8 282 540 1004 521 970 1778 m3 cubic meter cfm m3/min 0.6 69 156.181 50 1.89 48 118.126 74 2.402 81 3.150 100 3.6 22.984 45 1.079 22 0.4482 -14.848 18 39.8 116 240 464 354 670 1238 Btu/hr British thermal unit/hour -16.535 59 2.8 18.0283 -1.4 76 168.346 the equivalent temperatures will be found in the left column./hp 15 0.637 28 61.4 22.819 24 52.822 68 149.4 11.0 249 480 896 488 910 1670 kW kilowatt ft-lb N•m 1.046 30 66.6 19.2 327 620 1148 psi pound/square inch 4.2 12.614 61 2.2 554 1030 1886 832 1530 2786 Pascals cm Hg kPa 1.0 32.8 538 1000 1832 816 1500 2732 bars kPa 100.4 scf standard* cubic foot kcal/hr W 1.614 23 50.343 51 112.802 8 17.4 154 310 590 393 740 1364 cu.0 332 630 1166 psia pound/square inch absolute cm2 mm2 100.543 11 0.8 21.6 121 250 482 360 680 1256 °C Celsius sq.677 88 3.0551 kcal 0.251 31 66.02 cu.598 7 15. m3 0.4 210 410 770 449 840 1544 in.0929 m2 0.0 193 380 716 432 810 1490 hp horsepower -8.8 338 640 1184 psig pound/square inch gage kcal kJ 4.297 41 90.73 psia cm H2O kPa 9.7 11 51.78 27 80.0268 nm3/hr 1.540 -5.630 36 1.56 33 91.7 98 208.4516 sq.22 45 113. ft. while if converting from degrees Centigrade to 6 0.2 72 161. ft.8 30.67 20 68.116 45 99. H2O kPa 0.22 28 82.185 60 132.2 17.4 14.753 53 116.425 8 0.6 177 350 662 416 780 1436 ft-lb foot-pound ft m 0.6 149 300 572 388 730 1346 cm3 cubic centimeter Btu kJ 1. Multiply 2. H2O inch water psia kPa abs 6.559 85 3.NET CTSS .7 62 143.220 51 2.0665 7.1 88 190.244 77 3.00 23 73.6 288 550 1022 527 980 1796 m3/min cubic meter/minute scfm nm3/min 0.0 21. kg/m3 16.4 127 260 500 366 690 1274 cfm cubic foot/minute -15. in.6 78 172.390 61 134.9 84 183.6 25.67 29 84.574 2 4.462 2017 EDITION 231 WWW.2 90 194.003 64 141.2 20.0 277 530 986 516 960 1760 m2 square meter gas (US) L 3.03937 inch) 54 130 266 93 200 392 599 1110 2030 877 1610 2930 mm in mm in mm in mm in mm in 60 140 284 99 210 410 604 1120 2048 882 1620 2948 1 0.4 85 185. If converting from Fahrenheit degrees to Centigrade degrees.8 27.164 L 100 ft.669 37 1.22 36 96.8 82 179. m2 0.258 20 44.283 78 3.2 99 210.540 kg kilogram in.416 11 24.11 21 69.748 39 1.362 80 3.235 15 33.0 304 580 1076 N Newton 2.6 33.4 321 610 1130 Nm3/hr normal* cubic meter/hour Old Metric 3.142 94 207.4 67 152.3048 m 0.325 8.1 70 158. CONVERSION FACTORS SI — METRIC/DECIMAL SYSTEM TEMPERATURE CONVERSION TABLES* ABBREVIATIONS CONVERSION FACTORS By Albert Sauveur abs absolute To Convert To S.0 12.8 16.4 31.644 17 37.274 36 79.ft.1 79 174.717 89 3.772 65 2.811 66 2.479 37 81.6 36.366 56 123.16 cm2 6. ata atmosphere absolute From Metric By Metric By C F C F C F C F Btu British thermal unit English -17.ft.417 56 2.0283 0 32 89.661 14 0.0 14 57.030 14 30.0 560 1040 1904 838 1540 2804 *“Standard” = 59°F and 14. Hg inch mercury psi kPa 6.032 97 3.9 ft.6 260 500 932 499 930 1706 m meter ft/sec m/sec 0.504 10 0.4 20.118 23 0.252 -13.868 78 171.8 199 390 734 438 820 1508 in inch hp kW 0.0 23.300 85 187.663 77 169. kg/metric hp lb/hp 19 0.622 CONVERSION FACTORS CONVERSION FACTORS CONVERSION FACTORS 13 0.441 82 3./min.073 79 174.386 degrees Fahrenheit.8 310 590 1094 To Convert To S.858 L cu.096 84 185.799 63 138.063 47 1./min.053 19 41.276 27 1.047 72 2.8 91 195.8 64 147.2 81 177.6 16.598 86 3.980 59 130.540 -11.520 84 3.0 59 138.320 46 101.9 66 150.4 6 42.937 93 205./min.2 63 145.432 27 59.2 1000 to 1630 scfm standard* cubic foot/minute cm mm 10.8 24.4 549 1020 1868 827 1520 2768 *“Normal” = 0°C and 1.1868 5.0 138 280 536 377 710 1310 cm centimeter lbf N 4.119 89 196.4 238 460 860 477 890 1634 °F °C = (°F -32) 5/9 °C = (°F -32) 5/9 -4.683 38 83.866 42 1.3 92 197.142 49 1.6 13 55.2488 cm H2O 2.324 90 198.413 66 145.472 32 1.898 20 0.0 95 203.2 34.4 28.00 41 105.934 49 108.8064 566 1050 1922 843 1550 2822 nm3/hr nm3/min 0.188 5 11.162 55 121.0185 kg/m3 16.0 221 430 806 460 860 1580 kcal kilocalorie -6.512 33 1.8 0 32 10.1 3 37.4536 -9.33 47 116. 1 m/s = 196.400 cm 2.087 73 2.89 25 77.8948 ata 0.496 58 2.4 17.575 60 2.0 15.0 C F C F sq square kg/cm2 kPa 98.070 -7.2 132 270 518 371 700 1292 lb/cu.0 77 170.56 42 107.235 lb.8 9 48.2 1 33.6 543 1010 1850 821 1510 2750 atm kPa 101.3558 -3.4 182 360 680 421 790 1454 gal gallon yd m 0.0 86 186.6 87 188.78 46 114.2 188 370 698 427 800 1472 lb kg 0.11 34 93.236 26 1.2 299 570 1058 538 1000 1832 mph mile per hour 1.929 69 2.197 25 0.0 110 230 446 349 660 1220 -17.5939 N/m 14.729 48 105.638 87 3.20462 pounds) kg lb kg lb kg lb kg lb kg lb 1 2.071 98 3.8 10.0 68 154.1565 -11.4 94 201.465 9 0.3048 -10.4 36.16279 6.211 10 22. mm2 645.6 96 204. 5.3332 37.992 96 3.11 30 86.254 75 165.4 293 560 1040 532 990 1814 1.0 37.8 171 340 644 410 770 1418 ft/sec foot/second in mm 25.0 26.89 39 102.3 8 46.7 53 127.165 75 2.654 62 2.I.2590 kcal/nm3 0.231 70 154.026 69 152.3769 cm Hg 2.6 27.594 62 136.843 29 63.2 160 320 608 399 750 1382 °F Fahrenheit -12.3 65 149.8948 bars abs 0.228 71 160 320 104 220 428 3 0.888 39 85.701 1 L = 61.67 35 95.56 31 87.33 38 100.756 90 3.591 35 1.51 m/s 1 lb/hp = .787 40 1.268 Note: The numbers in bold face type refer to the temperature either in degrees Centigrade or Fahrenheit 4 0.2 271 520 968 510 950 1742 mm millimeter -1.693 63 2.968 70 2.914 88 194.1 97 206.4 33.44 24 75.9 7 44.6 4 39.4474 kg/metric hp 16 0.2 26.165 99 218.393 6 13. Multiply To Old Multiply 0 to 100 100 to 1000 – cont. in.1 12 53. 5 0. in.740 10 cu.911 44 97.845 73 160.070 -6.110 99 3. the answer will be found in the column on the right.22 19 66.4 25.874 93 3.4482 N 4.891 83 182.0 29.01325x105 9.33 26 78.9 93 199.0 5 41.8 32.457 57 2.024 46 1.3048 m/sec 0.2 15.756 97 213.914 -10.525 47 103.315 28 1.139 50 110. m/s ft.551 96 211.7 80 176.050 74 163.44 49 120.157 24 0. Hg kPa 3. 8.505 86 189. 8% and minor flow imperfections caused by the scalloped redesign. the redesigned impeller was tested performance of the scalloped impeller. it would eventually have resulted in ex. identified as one of the factors contributing to the failure. CTSS decided to scallop a new impeller to achieve the redesign targets. TECH BRIEF showed an efficiency reduction of about 0. The engineers hoped to avoid future resonance prob. tion of external factors can change depending on unit oper- cies.NET CTSS . Sulzer analyzed and compared various scallop designs to determine the optimal scallop shape based on the fol- lowing criteria: reduced stress levels. or changes in impeller performance. Sulzer in Switzerland manufactured the impeller. all the characteristics of the redesigned impeller remained nearly unchanged from the original design and would not affect the perfor- mance of the unit (Figure 3). After fabrication. was completed in 14 weeks. The impeller would have needed multiple Such drastic changes can lead to necessary changes in design iterations. causing the equipment to fail in a specific lems regardless of the operating mode. was significantly reduced with the cover plate scalloping. A complete redesign of an impeller to mitigate some of the impeller could have been performed. making use of their experience and their proprietary technologies n Figure 3.. for brazing joints of a complex curvature.g. shaft). CFD analysis confirmed the performance of the rede. scalloped impeller design was approved for manufacturing. The contribu- impeller natural frequencies and excitation force frequen. Based on the results of the redesign. A complete redesign mode. ating conditions. was nondestructively tested after fabrication and after spin testing at 15% above the maximum operating speed. Scalloping can provide tended delivery time to the customer and higher modification an effective solution to alter the impeller modal character- expenses. time and labor.CTSSNET. Sulzer engineers shape is chosen. but it would have of the problems identified by the root failure cause analy- ended up being highly expensive in terms of engineering sis can be a very resource-consuming engineering project. the new. 3-D computational fluid dynamics (CFD) verified the n Figure 4. stationary stationary components modifications as well as performance diffuser vanes. The cover plate fillet stress concentration. which confirmed the ac- with the diffuser passing frequency. scalloping both the cover plate and back plate provid- ed significantly better results in terms of natural frequency separation margins obtained. The new impeller signed impeller. which affect process requirements. engineering studies and redesign. Fabrication and testing of the redesigned impeller The redesigned impeller was fabricated and tested within a 20-week period after all studies had been completed. and minimum scallop depth to maintain per- formance levels. In addition. Scalloping is a machining procedure that removes material from the impeller periphery. revision. To accelerate the redesign process and return the istics without affecting performance if the optimal scallop impeller to service as quickly as possible. Also. including root cause failure analysis. 2017 EDITION 232 WWW. The entire project. curacy of the numerical studies and analysis. Ring Impeller redesign procedure testing was performed on the new impeller stacked on the Two main factors contributed to the impeller failure: stress shaft to confirm modal characteristics (Figure 4). In general. It would have involved stage housing and other components of the machine (e. which were both deemed acceptable by the Sulzer engi- neers and the customer. The CFD analysis and fulfilled all requirements. The goals of the rede. sign were to reduce the stresses in the cover plate fillet area The study shows that multiple design and operational fac- and to achieve at least 5% separation margin between the tors can be responsible for an impeller failure. housing. separation between the impeller frequencies and the frequencies of the exci- tation forces. Measured concentration at the cover plate fillet and resonance caused natural frequencies of the impeller appeared to be within by the interference of one of the impeller natural frequencies 3% of the predicted frequencies. . . COMPRESSOR Dedicated To Gas Compression Products & Applications PACKAGER GUIDE 2017 www.com. 2017 EDITION 233 WWW. types of compressors offered and the capacity range of the packages they produce.compressortech2. please contact
[email protected] A listing of global compressor packagers. A PDF of this listing is available on our website. along with primary contact information.NET CTSS .CTSSNET. If your company is missing from this listing. Oil & Gas igomez@abc-compressors. Jeannette Pennsylvania USA x 10. Sales
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[email protected]@ngsgi. Sales
[email protected] SES International Sales Manager. Inc. anbarasan.com Palmero San Luis Buenos Aires Buenos Aires Argentina x x 100 6700 75 5000 Matias Maggi Compression Manager
[email protected] Safe San Giovanni Persiceto Italy x 67 4700 50 5000 Dario Salvadori Sales Manager. unloaders. or fully oil-free to meet highest purity demands • Multi-stage design for reduced power consumption Screw compressor Gas turbines package • Cost savings at turbine part-load operation through flow dedicated 20 MW and smaller control methods (slide valve.oil injected Reciprocating compressor packages . Oil-injected screw compressor package with inlet filtration unit Tailor-made. flexible solutions via three different technologies Screw compressor packages .integrally geared Advantages TECHNOLOGIES VS. IGV) according to High-pressure screw Gas turbines or reciprocating compressor type 20 .60 MW compressor package • Special fast-acting recycle valve and correct volume selection for Gas turbines quick response to turbine dynamics 60 MW and larger Centrifugal compressor package • Availability and maintainability oriented design • Compliant to the highest standard health and safety directives and international standards (noise control and fire-fighting) .horizontally opposed Centrifugal compressor packages . TURBINE SIZE • Turbine protection: minimized oil carryover with enhanced oil separation. baseplate or skid. To minimize fugitive emissions from toxic and flammable gases.W. • A Unit of IDEX Corporation 3805 N. Off-The-Shelf Compression Packages • 103 Mounting: Consists of a compressor. When this happens Corken will start from scratch and build a custom compression package from the floor up.CTSSNET.com • E-mail: cocsalesdept@idexcorp.. 36th St. Custom Engineered Compression Packages When working with toxic and flammable gases. • 109 Mounting: Has all of the 103 items listed above plus a liquid trap and interconnecting piping. Phone (405) 946-5576 • FAX (405) 948-7343 Website: www. and process gas markets for more than 70 years.Custom Compression Packages for Small Horsepower Reciprocating Compressors A Global Leader in Small Horsepower (HP) Compression Corken has been manufacturing compression solutions for the LPG. Oklahoma City. We offer a full line of small horsepower (7.5 to 75 hp) reciprocating compressors in vertical and horizontal designs. Oil & Gas. and interconnecting piping. flywheel.. and an optional driver. INC. often times there are no off-the-shelf gas handling solutions. • 107 Mounting: Has all of the 103 items listed above plus a liquid trap. each compressor is available in a double or triple packed configuration.corken. four-way valve.NET CTSS . OK 73112 U.com @CorkenInc CP547A 2017 EDITION 238 WWW. belt and belt guard. CORKEN. adjustable driver slide base.A.S.. Send your specifications and see what Corken can do for you! Solutions beyond products. . Gas Terminals 2017 EDITION 239 WWW.8 bar g) • Single.com for more information Operating Specifications: • Horsepower/(kW): 7.5 to 75 (5.CTSSNET.6 to 55. Liquid and Liquefied evacuation situations.and Two-Stage Compression • Air and Water Cooled Models • Double or Triple Packed Configurations • Lubricated and Oil-Free Models Applications: • Gas Boosting • Gas Gathering • Landfill Gas Recovery • Liquid Transfer • Tank Car Unloading • Vapor Recovery • And many more.9) • Working Pressure: Up to 1.. See corken. and methyl chloride.NET CTSS . butadiene. Industries Served: Process: Chemical and Petrochemical Processing Energy: Oil and Natural Gas Production Alternative Fuels Refined Petroleum Products Liquefied Gases 291-107 Compressor Package Unit FT491-109F Compressor Package Unit Electric Power Model 291 single-stage compressor Model FT491 single-stage. flanged Generation packaged with a gas engine drive compressor packaged with an electric designed for tank maintenance motor drive designed for liquefied gas Transport: evacuation and emergency transfer applications using vinyl chloride.650 psi (113. ......at C M COMOTI .......de/zm L Burckhardt Compression AG ...138. Ing.com Solar Turbines Incorporated ...Romanian Research & Development MAN Diesel & Turbo SE .......125...com/bhs G Voith Turbo Inc.........................kobelcocompressors...........com www.... KG ................cumminsengines.136.134........com/oil-and-gas PSE Engineering GmbH Compression Systems ......... Prime Movers Tab www.....com 2017 EDITION 240 WWW........ Mitsubishi Heavy Industries A Unit of IDEX Corporation .... 115........Gas Processors Association ZOLLERN BHW Gleitlager GmbH & Co.............123 www........... KG .................mandieselturbo.. 192 www. Mario Cozzani Srl ................ 129 Voith Turbo BHS Getriebe GmbH ..com S SIAD Macchine Impianti S..pse-eng.org/ www..127.............com www.com/compressors www......borsig..........117 Elliott Group . Dott.....burckhardtcompression............flsmidth........... 239 Compressor International .corken....cozzani... 135 www...............atlascopco-gap.......................Packagers Tab D www.NET CTSS ...........119 www........ 141 www........................comoti.. ......LMF...........com Cummins Inc....113 www.............144 Leobersdorfer Maschinenfabrik (LMF) ... E Compressors Division ..com Corken Inc..113 info@voithusa............ Ing Mario Cozzani Srl . 143 www.......... V Pneumatic Transport ..............140..............cozzani.... .237 http://gea.............ro www.p.............mhicompressor......A..........................neuman-esser..com/en Cozzani..... Components Tab Plain Bearing Technology .......com F FLSmidth Inc. 137 www......hoerbiger....arielcorp.... 139 Institute for Gas Turbines....Third Cover.217 www.....238..com BORSIG ZM Compression GmbH .....226..Fourth Cover B www....solarturbines.................217 NEUMAN & ESSER GmbH & Co......................... Compressors Tab HOERBIGER ........... DIRECTORY OF ADVERTISERS A H Ariel Corporation ......zollern..de Dott.......................com K Kobelco Compressors America Inc.....142...com www.................................... Oil & Gas Markets ...com www......... 227 https://gpsa.elliott-turbo....com www....................... 201 www........gpaglobal......voith................siadmi......CTSSNET................................... Second Cover P www.....com Z GPA/GPSA .com GEA Refrigeration Italy Oil & Gas .................com Atlas Copco Gas and Process .. Elliott’s global sourcing capabilities provide world-scale producers with unmatched reliability. efficiency.elliott-turbo.com . They turned to Elliott for unparalled experience in olefins compression. www. and value over the life of their investment. Who will you turn to? C O M P R E S S O R S n T U R B I N E S n G L O B A L S E R V I C E The world turns to Elliott. n Challenge: Ensure the success of the enterprise’s first PDH project. n Result: Elliott Group is selected as the world’s most entrusted PDH compressor supplier.n Customer: World-scale propylene producer. China. Elliott Group has decades of experience in high volume flow olefins compression that meets the most exacting standards. U. Houston Office: sales@kobelco-kca. (713) 982-8450 • Tokyo. Germany • Jurong. Inc. Singapore • Dubai. Kobelco Compressors America. Providing our clients with the best possible solution and service is our top priority. KOBELCO has been curing gas compressor headaches for almost 100 years. Kobelco will manufacture a custom engineered compressor package that can be delivered and serviced anywhere in the world. (713) 655-0015 f.com p. we know compressors. After consulting with you on the required specifications.TEMPORARY RELIEF Take a couple of aspirin and call KOBELCO. . FOR THE CURE Call KOBELCO first and avoid pain relievers altogether. Japan • Houston. E. in the morning. Simply stated. A. Texas • Munich. 2 150 10.0 5 75 55 725 1850 CC40-40H X X OI 131 334 3.3 6 75 55 500 1250 CC80 X X OI 244 611 6.8 150 10.7 150 10.2 62.2 81.9 27.3 6 350 250 325 750 CC225 X X OI 724 1672 20.3 6 150 111 400 925 CC135 X X OI 419 968 11.3 150 10.7 150 10.5 300 20.NET CTSS .8 34.3 53.3 6 75 55 500 1250 CC70 X X OI 206 516 5.4 11.4 150 10.3 5 500 375 300 520 C450 X X OI 1534 2659 43.4 150 10.6 150 10.0 7.5 150 10.3 150 10.7 9.5 24.CTSSNET.6 66. CC30 X X OI 106 271 3.3 6 500 375 325 750 CC300 X X OI 943 2176 26.4 150 10.6 150 10.0 7.3 6 500 375 325 750 C350 X X OI 1102 2203 31.3 5 500 375 300 520 C400 X X OI 1364 2364 38.3 6 350 250 325 750 CC200 X X OI 614 1416 17. FUL-VANE 125.9 17.4 11.3 6 150 111 400 925 CC120 X X OI 369 854 10.3 6 125 90 500 1250 CC100 X X OI 291 729 8.2 150 10.7 300 20.7 61.0 5 75 55 725 1850 (Continues) CC50-50H X X OI 156 398 4.3 5 650 485 300 520 C608 X X OI 1943 3368 55. ADDENDUM SPECS FOR 2017 CTSS RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max FLSMIDTH INC.3 150 10.6 150 10.3 6 75 55 725 1850 CC60 X X OI 172 430 4.3 5 500 375 300 520 C508 X X OI 1667 2889 47.3 5 650 485 300 520 CC30-30H X X OI 106 271 3.3 6 150 111 400 925 CC150 X X OI 471 1090 13.7 9.5 47.7 150 10.4 30.3 20.3 6 75 55 725 1850 CC50 X X OI 156 398 4.8 14.3 6 75 55 725 1850 129 CC40 X X OI 131 334 3.2 150 10.9 12.4 40.3 6 150 111 400 925 CC175 X X OI 523 1208 14.3 150 10.1 150 10.3 6 125 90 500 1250 CC110 X X OI 325 752 9.0 95.2 62.9 150 10.2 21.3 6 350 250 325 750 CC250 X X OI 822 1897 23.0 5 75 55 725 1850 WWW.4 75.3 6 500 375 325 650 C375 X X OI 1278 2215 36.9 150 10.3 150 10.3 300 20. 6 8.0 7 75 55 725 1850 CB40 X X OI 45 116 1.7 300 20.0 7 150 111 400 925 CB135 X X OI 144 333 4.3 53.6 300 20.2 300 20.8 34.1 2.4 300 20.4 30.3 300 20.NET CTSS (Continues) CB250 X X OI 277 638 7.9 27.0 7 350 250 325 750 CB225 X X OI 243 561 6.3 5.0 7 150 111 400 925 CB150 X X OI 162 375 4.6 10.CTSSNET.0 5 150 111 400 925 CC120-120H X X OI 369 854 10.2 62.6 300 20.0 7 125 90 500 1250 CB100 X X OI 99 247 2.1 9.1 300 20.0 5 500 375 325 750 C350-350H X X OI 1102 2203 31.8 7.4 300 20.0 5 500 375 325 650 CB30 X X OI 38 97 1.9 300 20.7 61.8 300 20. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max FLSMIDTH INC.0 7 500 375 325 750 .4 300 20.0 300 20.4 40.0 5 350 250 325 750 CC225-225H X X OI 724 1672 20.0 7 75 55 500 1250 CB80 X X OI 83 207 2.0 5 150 111 400 925 CC135-135H X X OI 419 968 11.5 300 20.3 300 20.0 7 75 55 500 1250 CB70 X X OI 74 185 2.2 300 20.0 7 75 55 725 1850 CB60 X X OI 64 161 1.0 5 75 55 500 1250 129 CC70-70H X X OI 206 516 5. CC60-60H X X OI 172 430 4.1 300 20.6 300 20. FUL-VANE 125.0 7 75 55 725 1850 CB50 X X OI 55 140 1.8 4.0 5 150 111 400 925 CC150-150H X X OI 471 1090 13.6 300 20.9 12.9 300 20.4 300 20.5 4.0 5 125 90 500 1250 CC110-110H X X OI 325 752 9.1 5.9 300 20.9 17.0 7 350 250 325 750 WWW.8 13.9 15.9 11.4 300 20.0 5 500 375 325 750 CC300-300H X X OI 943 2176 26.0 5 150 111 400 925 CC175-175H X X OI 523 1208 14.4 300 20.2 300 20.2 21.0 7 150 111 400 925 CB175 X X OI 174 402 4.8 14.3 300 20.0 7 150 111 400 925 CB120 X X OI 128 297 3.3 20.2 300 20.0 7 125 90 500 1250 CB110 X X OI 113 262 3.0 300 20.5 300 20.5 24.0 5 75 55 500 1250 CC80-80H X X OI 244 611 6.0 5 350 250 325 750 CC200-200H X X OI 614 1416 17.3 3.2 7.0 7 350 250 325 750 CB200 X X OI 207 477 5.5 47.0 5 350 250 325 750 CC250-550H X X OI 822 1897 23.0 5 125 90 500 1250 CC100-100H X X OI 291 729 8.3 300 20.8 18. 2 -0.2 -0.91 125 90 500 1000 V100 X X OI 291 729 8.6 -13.0 125 90 500 1000 V100-100H X X OI 291 729 8.2 -0.9 -13.6 -1.4 30.5 -14.3 53. CB300 X X OI 315 726 8.91 150 111 400 800 V150 X X OI 471 1090 13.2 -0.2 -0.0 150 111 400 800 WWW.6 -1.7 9.8 34.2 -14.6 -14.6 -1.6 -13.1 -13.91 500 375 325 650 V300 X X OI 943 2176 26.4 -13. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max FLSMIDTH INC.91 350 250 325 650 V200 X X OI 614 1416 17.6 -1.2 -0.2 -13.6 -1.7 -14.6 -1.3 -14.2 -0.2 -0.7 61.2 -14.6 300 20.0 125 90 500 1000 V110-110H X X OI 325 752 9.0 75 55 725 1500 V50-50H X X OI 156 398 4.0 7.2 -0.91 150 111 400 800 V135 X X OI 419 968 11.0 150 111 400 800 .5 47.6 -1.9 27.0 75 55 725 1500 V40-40H X X OI 131 334 3.91 75 55 725 1500 V60 X X OI 172 430 4.0 7 500 375 325 650 V30 X X OI 106 271 3.2 -0.9 27.5 24.91 75 55 500 1000 V70 X X OI 206 516 5.5 24.7 9.8 300 20.3 -14.2 -13.4 20.4 11.3 -13.2 -0.9 17.3 -14.5 -13.2 -0.0 75 55 725 1500 V60-60H X X OI 172 430 4.91 150 111 400 800 V120 X X OI 369 854 10.4 -14.6 -1.6 -13.2 21.91 350 250 325 650 V225 X X OI 724 1672 20.0 7.2 -0. FUL-VANE 125.91 350 250 325 650 V250 X X OI 822 1897 23.9 12.7 -13.91 75 55 500 1000 V80 X X OI 244 611 6.3 20.2 -0.91 125 90 500 1000 V110 X X OI 325 752 9.2 -0.91 75 55 725 1500 V40 X X OI 131 334 3.0 75 55 500 1000 V70-70H X X OI 206 516 5.2 62.3 -13.8 14.3 20.4 11.3 -13.6 -1.NET CTSS (Continues) V135-135H X X OI 419 968 11.0 75 55 500 1000 V80-80H X X OI 244 611 6.0 150 111 400 800 V120-120H X X OI 369 854 10.91 500 375 325 650 V350 X X OI 1102 2203 31.2 -13.9 12.91 75 55 725 1500 V50 X X OI 156 398 4.4 -13.2 21.CTSSNET.8 14.4 40.9 17.7 -13.91 150 111 400 800 V175 X X OI 523 1208 14.91 500 375 325 650 V30-30H X X OI 106 271 3.0 7 500 375 325 750 129 B350 X X OI 368 736 10.6 -1.3 -13.2 -0.6 -14.2 -0.9 20. 3 53.000 9800 7300 1200 300 X X X X OF/OI 9800 700 12.6 -1.0 350 250 325 650 V250-250H X X OI 822 1897 23.000 40.000 1600 1200 1000 250hs X X X X OF/OI 9800 700 56.300 860.000 6700 5000 650 560hs X X X X OF/OI 9800 700 12.700 150.000 1340 1000 1200 130 X X X X OF/OI 9800 700 56.6 -1.000 80.6 -1.200 1.000 6700 5000 1200 320 X X X X OF/OI 9800 700 193.000 1340 1000 1200 150hs X X X X OF/OI 9940 700 33.7 -14.0 150 111 400 800 129 V175-175H X X OI 523 1208 14.200 250.0 500 375 325 650 NEUMAN & ESSER GROUP 142.0 350 250 325 650 V225-225H X X OI 724 1672 20.700 470.700 150.600 560.CTSSNET.000 540 400 1200 V1 X X X OF/OI 3550 250 24. FUL-VANE 125.200 1.000 30.000 540 400 1200 80hs X X X X OF/OI 4540 320 18.2 -14.700 110.2 62.000 135 100 700 143 BV35 X X X OF/OI 710 50 8540 38. RECIPROCATING AND ROTARY COMPRESSORS 2017 Basic Specifications Reciprocating Rotary Inlet Flow Range 2017 EDITION Manufacturer Speed Range (rpm) Maximum Allowable Working Pressure Maximum Input Power Maximum Allowable Rod Load acfm m3/min Catalog Page Reference Compression Ratio (Per Stage) Model Designation Straight Lobe Helical Lobe (Screw) Single Screw Sliding Vane Liquid-Ring Trochoidal Scroll OF = Oil Free OI = Oil Injected Single Stage Multiple Stages Integral Engine Driven Separable Balanced/Opposed Diaphragm min max min max psig bar lb Newtons hp kW min max FLSMIDTH INC.600 560.NET CTSS .6 -1.6 -1.6 -1.000 1200 WWW.3 -14.0 500 375 325 650 V350-350H X X OI 1102 2203 31.6 -14.4 -14.0 500 375 325 650 V300-300H X X OI 943 2176 26.000 1600 1200 1000 190 X X X X OF/OI 9800 700 85.000 135 100 1000 30 X X X X OF/OI 4540 320 18.4 30.000 80.000 6700 5000 1200 500 X X X X OF/OI 9800 700 382.300 860.700.0 350 250 325 650 V200-200H X X OI 614 1416 17.000 6700 5000 600 700hs X X X X OF/OI 9800 700 193.4 40.9 -14.8 34.000 40.700.000 30.400 380.1 -14.200 250.7 61.000 3400 2500 1000 320hs X X X X OF/OI 9800 700 105. 25 X X X OF/OI 710 50 5620 25.6 -1.000 600 1200hs X X X X OF/OI 9800 700 382.5 47. V150-150H X X OI 471 1090 13.000 335 250 1200 63 X X X X OF/OI 9940 700 33.