Fluid Mechanics & Machinery LabIII SEMESTER CONTENTS S.NO. DESCRIPTION PAGE NO. 01 03 07 10 13 16 18 21 24 27 31 34 38 41 44 1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 STUDY OF FLOW METERS STUDY OF HYDRAULIC PUMPS STUDY OF TURBINES FLOW THROUGH PIPES—ORIFICEMETER FLOW THROUGH PIPES—VENTURIMETER CALIBRATION OF ROTA METER FLOW THROUGH PIPES – MAJOR LOSSES PERFORMANCE TEST ON A SINGLE STAGE CENTRIFUGAL PUMP PERFORMANCE TEST ON A SUBMERSIBLE PUMP PERFORMANCE TEST ON A DOUBLE ACTING RECIPROCATING PUMP PERFORMANCE TEST ON A GEAR OIL PUMP PERFORMANCE TEST ON PELTON WHEEL TURBINE PERFORMANCE TEST ON FRANCIS TURBINE PERFORMANCE TEST ON KAPLAN TURBINE VIVA (SAMPLE QUESTIONS) SYLLABUS FLUID MECHANICS AND MACHINERY LAB (Common to Mechanical & Production) LIST OF EXPERIMENTS 1. Determination of the Coefficient of discharge of given Orifice meter. 2. Determination of the Coefficient of discharge of given Venturi meter. 3. Calculation of the rate of flow using Rota meter. 4. Determination of friction factor for a given set of pipes. 5. Conducting experiments and drawing the characteristic curves of centrifugal pump/ submergible pump 6. Conducting experiments and drawing the characteristic curves of reciprocating pump. 7. Conducting experiments and drawing the characteristic curves of Gear pump. 8. Conducting experiments and drawing the characteristic curves of Pelton wheel. 9. Conducting experiments and drawing the characteristics curves of Francis turbine. 10. Conducting experiments and drawing the characteristic curves of Kaplan turbine. LIST OF EQUIPMENT (For a batch of 30 students) 1. Orifice meter setup 2. Venturi meter setup 3. Rota meter setup 4. Pipe Flow analysis setup 5. Centrifugal pump/submergible pump setup 6. Reciprocating pump setup 7. Gear pump setup 8. Pelton wheel setup 9. Francis turbine setup 10. Kaplan turbine setup 0 0 3 2 FLUID MECHANICS It deals behavior of fluids under rest as well as in motion. Fluid is a substance, which is capable of flowing (both gases and liquids). SIGNIFICANCE OF FLUID MECHANICS Fluid mechanics encompassed a great many fascinating areas like, Design of wide range of hydraulic structures (dams, canals, weirs etc) and machinery (pumps& turbines) Design of a complex network of pumping and pipelines for transporting liquids; flow of water through pipes and its distribution to domestic service lines. Fluidic control devices: both pneumatic & hydraulic. Power generation from conventional methods such as hydroelectric, Steam and gas turbine, to newer ones involving magneto fluid dynamics. Methods and devices or the measurement of various fluids at rest or in motion. Study of man’s environment in subject like oceanography and geology. Human circulatory system, ie, flow of blood in veins and the pumping action of the heart. BUOYANCY BUOY means- lift, buoyancy force means- lifting force Fluid experience an upward thrust due to fluid pressure –force is called buoyancy force. ARCHIMEDES PRINCIPLE. A body immersed in a fluid is buoyed / lifted up by a force equal to the weight of the fluid displaced by the body .The body apparently losses as much of its weight of the fluid displaced by it a floating body displaced the volume of fluid just sufficient to balance its weight BERNOULLI’S EQUATION The sum of the KE (velocity head) the pressure energy (static head) and potential energy (elevation head) of an ideal incompressible fluid is constant along Streamline. A Swiss mathematician Daniel, Bernoulli (1700-1702) Potential energy (or) datum energy – energy possessed by a fluid by virtue of its position Kinetic energy is energy possessed by a fluid by virtue of its motion. Newton second law F= ma. KE = ½ mv 2 Pressure energy is energy possessed by a fluid by virtue of the pressure maintained by it P.E = wgh FLUID CHARACTERISTICS S.no 1 2 3 Characteristics Mass density(or) Density Specific weight(or) Weight density Specific gravity Viscosity / 4 Absolute viscosity / Dynamic viscosity 5 Note: VISCOSITY: • • • It is the property of the fluid, which offers resistance to flow. It is a measure of internal fluid friction, which causes resistance to flow. It’s due to cohesion and molecular momentum exchange between fluid layers. MEASUREMENT SPECIFIC GRAVITY - Pygronometer - Hydrometer (density measurement) VISCOSITY - Capillary tube viscometer - Efflux (say bolt, redwood) - Falling sphere viscometer - Rotating cylinder viscometer, VELOCITY - Pitot tube - Hot wire anemometer - Cup & vane anemometer - Current and turbine meters. Kinematic viscosity ν µ Symbol ρ w S Definition Mass/volume Weight / volume ρ(or) w of liquid ρ(or) w of std.liquid Shear stress (Change of velocity/ change of distance) ν=µ/ρ Units Kg/m3 N/m3 No unit Ns/m2 (Poise) m2/s (Stoke) Kinematic viscosity 1 stoke = cm2 /sec =(1/100) 2 m2/ sec = 1x 10-4 m2/ sec 4. Absolute Viscosity 1 Poise 1 Centi poise = dyne. To convert kg in to N 1kg = 9.81x 10 N/m2 9.81x 103 N/m3 = 10 m .81 N ≅ 10 N W= mg Kg x m/s2 = 1N 2.033 kg/cm2 = 10.sec/cm2 = 1/10 Ns/m2 = 1/100 poise = 1x 10-3 Ns/m2 3. 1 cm2 = 10-4m2) If P is in kg/cm2 H = P/w kg/cm2 / N/m3 4 = 9.33/ 760 mwc (meter of water column) 5.33 m of water 1mm of Hg = 10. Pressure in to pressure head If P is in(N/m2) P = w (or) γ x H H = P/w = N/m2 / N/m3 =m Note: 1 kg/cm2 = 1 bar 1 kg/cm2 = (1x10) (10-4) = 1x105 N m2 N/m2 (1kg = 10N.33 m of water Vacuum Pressure in to Vacuum head 760 mm of Hg = 10.Standard atmospheric pressure.SOME BASIC UNIT CONVERSIONS 1. 1 atm = 760 mm of Hg = 1. Electro magnetic flow meters . Digital tachometer 10-4-0. Piezoelectric pressure picks ups HIGH PRESSURES 1. Mcleod gauges 3. Strain gauge pressure pick ups 2.1 bar 1.non contact type 6. Vertical tube water micro manometer 7. Orifices & mouthpieces 2. Bourdon type (spiral tube) 2.5 bar 0. elbow meters 5.1 m bar up to a minimum of 10-3 m bar up to a minimum of 10 m bar up to a minimum of 5x10-4 m bar up to a minimum of2.1-7.= 1bar STUDY OF FLOW METERS Flow meter is device used to measure the discharge of any liquid flowing through a Pipeline. Ultra sonic flow meter PRESSURE MEASURING DEVICES AND THEIR RANGES LOW PRESSURES 1.1 mbar 0. Inclined tube water manometer 8 Simple vertical tube manometer 9. Rotameter. Diaphragm gauges 4. Open Channel etc.5 bar up to 350 bar up to 75 bar 0.01m bar 0. Strain gauge pressure cells 1.. Low-pressure bourdon gauges 5. Analog tachometer 2. 1. Inclined tube water micro manometers 6. Bourdon type (C-type tube) 4. Weir & notch 3. orifice plates..5x10-3 m bar up to a minimum of 0. nozzles 4. Pirani gauges 10-5-1.tank. Capacitance type transducers 3.1.3 m bar 2.334 mbar . Venturi.05-3. Reservoir. Variable inductance pressure transducers 3.5-3600 bar up to 7000 bar 7000-15000 bar – from a tank /reservoir –open channel – pipelines SPEED MEASUREMENTS . Vertical tube mercury manometer MEDIUM PRESSURES 1.334 bar 0. Stroboscope.3. FLUID PROPERTIES COMPARISION OF FLOW METERS . RECIPROCATING PUMPS Working principle: Movement of the piston or plunger creates a vacuum and atmospheric pressure force the water up through the suction pipe into the cylinder. Application . Reciprocating pumps are generally operates at low speeds and is therefore to be coupled to an electric motor with v-belts.(Reciprocating pumps. or ( centrifugal pumps) A positive displacement pump increases the fluid pressure while a Non positive pump only transfers only the fluid. gear pumps) 2 . It converts mechanical energy into hydraulic energy.STUDY OF HYDRAULIC PUMPS PUMPS Pump is a device used for lifting liquids from a lower level to higher level.: 1. CLASSIFICATION. Positive displacement pumps.Non Positive displacement pumps. Pump can be run at higher speed. when the piston moves from left to right suction is taking place on the left side of the piston. which enables it to rise to a higher level. the discharge of double acting pump is continuous. it is thrown away from the central axis of rotation and a centrifugal head is impressed. Air vessels are fitted with suction and delivery pipes to reduce the acceleration head. this type of pump is very common. while the delivery on the right side. When the crank rotates. In oil drilling operations. FUNCTIONS: Suction Side: Reduces the possibility of separation. which lifts the liquid from lower to higher level by means of centrifugal force. It acts like an intermediate reservoir. called as centrifugal pump. CENTRIFUGAL PUMPS A pump. Pneumatic pressure system. Constant rate of discharge can be ensured. The reciprocating pump is best suited for relatively small capacities and high heads. when the piston moves from right to left vice versa action takes place. near the pump cylinder to reduce the accelerating heads. DOUBLE ACTING RECIPROCATING PUMP The pump is said to be a double acting when the liquid pressure acts on both sides of the piston or plunger. AIR VESSEL: Air vessel is a closed chamber fitted on the suction as well as on the delivery side. the piston or plunger reciprocates inside the cylinder. feeding small boiler condensate returns and light oil pumping. Thus. Main parts. Similarly.Spiral casing made of cast iron having suction and delivery arrangement Impeller having backward curved vanes keyed to the shaft WORKING PRINCIPLE: A centrifugal pump works on the principle that when a certain mass of fluid is rotated by an external source. . Therefore. Length of the suction pipe below the air vessel can be increased. Delivery Side: A large amount of power consumed in supplying accelerating head can be shared. Priming Before starting the centrifugal pump. Further dry running of the pump may result in rubbing and seizing of the Wearing rings and cause serious damage. air pockets inside the impeller may give to vortices and cause-. . to remove any air. suction pipe of the pump is called priming. Semi open impeller used for handling viscous liquids . impeller and suction pipe by filling in the pump with liquid is known as priming. chemicals and acids. CLASSIFICATON OF CENTRIFUGAL PUMP: Based on working head: Low head pumps: Medium head pumps: High head pumps: head up to 15m head between 15 to 40m head above 40m Based on type of casing: Volute casing pump Vortex casing pump Turbine pump or diffusion pump Base on direction of flow: Radial flow Axial flow Mixed flow Based on number of impeller shafts: Single stage pump Multi stage pump Based on the position of shaft: Horizontal pump Vertical pump FUNCTION OF CASING: To convert the kinetic energy of the liquid flowing through the casing into pressure energy PRIMING:Removal of air present in the casing. IMPELLER :Closed impeller used for handling non viscous pure liquid such as water oil. If a pump is not primed before starting.discontinuity of flow. gas or vapour from casing. It can be used to take the muddy water from the excavation trenches. mud and clay. It helps to increase the suction lift beyond the normal limit 6 to 8 m of water head. A jet pimp consists of a conventional radial flow C/F pump with a jet nozzle at the suction end. With the use of jet assembly it is possible to increase the suction lift up to 60m. -these are capable of pumping water against heads up to 350 m and capacities up to 550lps. APPLICATIONS: 1. 2. The pump together with electric motor operates below the liquid surface. -Working as that of multistage c/f pumps -It finds it application in irrigation as well as other deep well sources. WORKING PRINCIPLE: A stream of high-pressure water from the delivery pipe of the pump is allowed to flow through the suction jet nozzle. To lift the water from wells of smaller bores. -Turbine pumps are extensively used for deep well pumping -these pumps are generally multistage pumps with vertical shafts.Open impeller used for handling liquids having coarse debris as in sewage disposal. Advantages: • Simple in design • No lubrication problem . Employed for mining and for pumping oil. 3. JET PUMP It is a combination of centrifugal pump and an ejector. Due to this a partial vacuum is created and water is sucked from the well. which is commonly referred to as the jet. EFFICIENCIES OF CENTRIFUGAL PUMP: Manometric efficiency O/p of pump Work done by the impeller Mechanical efficiency Work done by the impeller Work supplied by the motor Over all efficiency Out put of the pump Work supplied by the motor SUBMERSIBLE PUMP (or) DEEP WELL PUMP The pump is connected to a electric motor. -A pump used for pumping liquids from deep wells is known as deep well pump. The pressure energy is converted in to kinetic energy due to which local pressure drop takes place. Francis turbine and Kaplan turbine) Impulse turbine are those turbines in which the liquid. which convert hydraulic energy into mechanical energy by utilizing the potential and kinetic energies of liquid.685 kpa). Continued rotation of the gears forces the fluid out of the pump discharges. The available head of liquid is converted into kinetic energy before the jet strikes the vanes. APPLICATIONS: Gear pump finds its application in machine tools drive using oil at relatively low pressure for combined lubrication and hydraulic control system of water & steam turbines and other machines. Fluid from an external reservoir is forced by atm pressure into the pump inlet. The shaft is usually connected to the upper gear of the pump. Impulse turbine (Example. Pelton Wheel) 2. Reaction turbine are those turbines in which the liquid when passes over the moving vanes is under pressure (above atmospheric pressure). When the liquid flows out of the turbine . This removal of air from the pump casing produces a partial vacuum on the suction side of the pump. which run the electrical generators in a Power station. CLASSIFICATION OF TURBINES: The major classifications of turbine are: 1. when passes over the vanes of the wheel at atmospheric pressure and falls into the tail race at atmospheric pressure. They are the prime movers. When the pump is first started rotation of the gears forces air out of the casing and in to the discharged pipe. Reaction turbines (Example.• No reciprocating parts GEAR PUMP Gear pump is a constant delivery positive displacement pump CLASSIFICATON OF GEAR PUMP: • External gear pump • Internal gear pump These pumps have two mating spur gears that are turned in a closely fitted casing. STUDY OF TURBINES TURBINES: Turbine is a hydraulic machine. Modern gear pumps used in fluid power system develops up to about 3000 psi (20. Here the fluid is trapped between the teeth of the upper and lower gears and the pump casing. It is an inward mixed flow reaction turbine under medium head with medium discharge. an American Engineer. The guide . The jet of water imp rings on the bucket with a high velocity it after flowing over the vanes leaves with a low velocity.Peltion. It leads water into the tailrace and acts as a safeguard against accidents the casing of reaction turbine leads water into the tailrace. L.into the tailrace the pressure is slightly below atmospheric pressure. which guide the water to enter the wheel at the correct angle without shock. After performing work on the buckets. James Francis. PELTON WHEEL : It is named after its inventor. d) Tailrace It is a water pool into which the water from the turbine ultimately discharge. which rotates the runner. e) Casing The casing of an impulse turbine prevents splashing of water. FRANCIS TURBINE: It is named after its designer. It acts as a safeguard and maintains a difference in pressure. They utilize both pressure and kinetic energies of liquid. When a single jet could not develop the required power more number of jets may be provided by evenly spacing them around the same runner. The pressure of water is atmospheric. PARTS OF TURBINES: a) Guide Blades Blades are provided to guide the water in the proper direction into the runner vanes. In General. 1. The jet of water enters radially at the outer periphery and leaves axially at the centre. The runner of the pelton wheel turbine has a number of hemispherical twin cups called buckets. The water from the guide blades strikes the vanes. c) Penstock It is pipelines that convey the water to the turbine. It is used for high heads of water.A. The flow of water is tangential to the wheel. b) Rotating Wheel or Runner It has vanes on its periphery. English engineer. water is discharged into the tail race. Pelton turbines have only a single jet. with a dividing wall called splitter. 2. The turbine consists of stationary guide blades. The splitter splits the jet into two parts and it glides over the buckets. a Germart Scientist.Victor Kaplan. The runner consists of two annular plates placed parallel with a number of vanes. In this turbine. It is a low head. water is discharged to the tailrace through a closed tube called draft tube. 3. high discharged reaction turbine with axial flow. .blades can be rotated around a pivot at each of its centre. Dr. KAPLAN TURBINE: It is named after its inventor. The force exerted on the vane causes the shaft to rotate. After doing the work. the pressure at the inlet is more than that at the outlet. The water from the scroll casing flows over the guide blades first and then over the vanes. It is very ideal when a large quantity of water is available of low head. The flow of water is parallel to the shaft. The runner resembles the propeller of a ship. Hence it is also called an improved propeller turbine. 16 . Ex. APPARATUS REQUIRED: 1. Orifice meter fitted with the pipeline 2. Meter scale/measuring tape FORMULAE USED: Actual discharge (Qa) Qa = Ah/t m3/s 17 . 3. Stopwatch 4. Collecting tank with piezometer. No: 01 Date: AIM: FLOW THROUGH PIPES—ORIFICEMETER To determine the coefficient of discharge of the orifice meter for a given pipe size. area of throat in orifice meter (m2) a2 =(π d22/4) g-acceleration due to gravity (m/s2) H-head over the orifice meter (m) d1-diameter of the pipe (m) d2-diameter of the orifice(m) 18 .a22 m3/s a1-area of the pipe (m2) a1 =(π d12/4) a2.A h t -Area of the collecting tank (m2) -rise of water level in collecting tank (m) -time for ‘h’ m rise (sec) Head over the orifice meter H = X[(Sm/ Sw)-1] m X—difference in manometer reading (h1-h2)m Sm—Specific gravity of mercury (13.6) Sw—Specific gravity of water(1) Theoretical discharge (Qt) Qt = a1a2 √(2gH) / √ a12. no Readings (h1)cm (h2)cm 1 2 3 4 5 6 X( m) Head Over the Orifice meter H (m) Time for 10cm rise t(sec) Discharge Actual Qa (m3/s) Theoretical Qt (m3/s) Coefficient Of discharge Cd=Qa/Qt 19 .OBSERVATIONS: Diameter of the pipe (d1) mm Diameter of the orifice (d2) mm Area of collecting tank (A) m² Rise of water (h) cm = = = = TABULATION FOR ORIFICEMETER: Manometer S. H 20 . GRAPH: Head (√H) Vs Actual discharge (Qa) RESULT: The coefficient of discharge of an orifice meter for a given pipe size 1) From observation --------2) From graph--------- 21 . 6. Repeat the above procedure for different manometer heads by adjusting the gate valve. Note the manometer readings and note the time for ‘h’ cm rise of water level in collecting tank. The diameter of the pipe and internal cross section area of collecting tank are noted down. Then open the corresponding cocks of a given pipe size. 5.PROCEDURE: 1. 3. 4. Start the motor and adjust the gate valve at exit to maintain steady flow for desired head. 2. Close all the cocks except manometer cocks. area of the pipe (m2) a1 = (π d12/4) a2.acceleration due to gravity (m/s2) H-head over the venturimeter (m) d1. Collecting tank with piezometer 3.a22 m3/s a1.area of throat in venturimeter (m2) a2 = (π d22/4) g.6) Sw—Specific gravity of water (1). Stopwatch 4.Ex.diameter of the pipe (m) d2. No: 02 Date: AIM: FLOW THROUGH PIPES—VENTURIMETER To determine the coefficient of discharge of the venturimeter for a given pipe size APPARATUS REQUIRED: 1. Theoretical discharge (Qt) Qt = a1a2 √(2gH) / √ a12.diameter of the venturi (m) 22 . Venturimeter fitted with the pipeline 2. Meter scale/measuring tape FORMULAE USED: Actual discharge (Qa) Qa = Ah/t A h t m3/s -Area of the collecting tank (m2) -rise if water level in collecting tank (m) -time for ‘h’ m rise (sec) Head over the venturimeter H = X[(Sm/ Sw)-1] m X—difference in manometer reading (h1-h2) Sm—Specific gravity of mercury (13. OBSERVATIONS: Diameter of the pipe (d1) mm Diameter of the venturi (d2) mm Area of collecting tank (A) m² Rise of water (h) cm = = = = TABULATION FOR VENTIRIMETER: S.n o 1 2 3 4 5 6 Manometer Readings (h1)cm (h2)cm X( m) Head Over the Venturi meter H (m) Time for 10cm rise t(sec) Discharge Actual Qa (m3/s) Theoretical Qt (m3/s) Coefficient Of discharge Cd=Qa/Qt 23 . 3. Note the manometer readings and note the time for ‘h’ cm rise of water level in collecting tank. Repeat the above procedure for different manometer heads by adjusting the gate valve. Then open the corresponding cocks of a given pipe size. 5. GRAPH: Head (√H) Vs Actual discharge (Qa) RESULT: The coefficient of discharge of the venturimeter for a given pipe size 1) From observation --------2) From graph--------- 24 . 4. The diameter of the pipe and internal cross section area of collecting tank are noted down 2. Start the motor and adjust the gate valve at exit to maintain steady flow for desired head.PROCEDURE: 1. Close all the cocks except manometer cocks. 6. Rota meter fitted in pipeline 3. No: 03 Date: CALIBRATION OF ROTA METER AIM: To calibrate the given rota meter and to determine the percentage of error. Collecting tank with piezometer 2. Stopwatch 4. Meterscale /measuring tape FORMULAE USED: Actual discharge Qa= Ah/t m3/s A -Area of collecting tank h -rise of water collecting tank (m) t -time for ‘h’m rise of water (sec) Theoretical discharge Qt= (Rota meter reading)/ (1000x60x60) m3/s Calibration error Cerror =[ (Qt-Qa)/Qt ]x100 Where 25 .Ex. APPARATUS REQUIRED: 1. Allow the water to flow through the pipe by switched on pump set 3. Close the gate valves of water meter while you calibrating the Rota meter and vice versa for water meter 4. The internal cross section area of collecting tank is measured.TABULATION FOR ROTAMETER: Rota meter reading (LPH) Time for ‘h’cm rise of water (t) sec Actual Discharge (Qa) m3/s Theoretical Discharge (Qt ) m3/s Calibration of Error (%) [(Qt-Qa)/Qt ] x100 S. Repeat the same procedure for various rotameter readings GRAPH: Actual discharge Vs Theoretical discharge Actual discharge Vs percentage of error RESULT: Thus the given rotameter was calibrated and the percentage of error is ------------26 = = . Adjust the gate valve of rotameter note the reading (lpm) and note the time for ‘h’cm rise of water level in collecting tank 5. 2.no 1 2 3 4 5 6 OBSERVATION: Area of collecting tank (A) m² Rise of water (h) cm PROCEDURE: 1. Ex.6) -Specific gravity of water (1) Darcy’s friction factor (f) hf = flv2 / 2gd f = hf.2.002x10 – 6) 27 a = (π d2)/4 . Collecting tank with piezometer.g. -Specific gravity of mercury (13. Stopwatch 3. 2.d / l v2 d -diameter of pipe (m) l -length of the pipe (m) v -velocity of the liquid (m/s) v=Qa/a g -acceleration due to gravity (m/s2) a -area of the pipe (m2) Reynolds number (Re) Re = (vd)/ν V -velocity of the water (m/s) d -diameter of he pipe (m) ν -kinematic viscosity of water (m2/s) (1. No: 04 Date: FLOW THROUGH PIPES – MAJOR LOSSES AIM: To determine the friction factor for a given pipe size APPARATUS REQUIRED: 1. Meter scale/measuring tape FORMULAE USED: Actual discharge (Qa) Qa = Ah/t m3/s A h t -Area of the collecting tank(m2) -rise if water level in collecting tank (m) -time for ‘h’ m rise (sec) Head loss due to friction (hf) hf = X[(Sm/ Sw)-1] m X Sm Sw -difference in manometer reading (h1-h2) m. no Manometer Readings h1 cm h2 cm x m 1 2 3 4 5 6 Head loss hf (m) Time for 10 cm rise of water (t) sec Reynolds Discharge Q (m3/s) Velocity V (m/s) V2 Friction Factor‘f ’ Number Re = (vd)/ν 28 .OBSERVATION: Length of the pipe (l) -----------m Diameter of the pipe (d) --------m Area of collecting tank (A) -----m2 TABULATION FOR MAJOR LOSS: S. GRAPH: 1. Head loss (hf) Vs square of velocity (v2) RESULT: Friction factor for a given pipe size--------- 29 . 6. Close all the cocks except manometer cocks. Start the motor and adjust the gate valve at exit to maintain steady flow for desired head. Reynolds number (Re) Vs friction factor (f) 2.PROCEDURE: 1. Note the manometer readings and note the time for ‘h’ cm rise of water level in collecting tank. The diameter of the pipe and internal cross section area of collecting tank are noted down 2. 3. Repeat the above procedure for different manometer heads by adjusting the gate valve. Then open the corresponding cocks of a given pipe size. 5. 4. Collecting tank of known cross section with piezometer and stop watch to measure the flow rate. TEST BED REQUIREMENTS: 1.Vacuum (suction) head =(Vx10. Discharge (Q) Q= Ah/t m3/s A -internal cross sectional area of collecting tank (m2) h -rise of water oil level in collecting tank (m) t -time taken for h-m rise.Ex. Bourdon type vacuum gauge for measuring the suction pressure.P. Components: 1) Impeller: Impeller is a rotating element (Rotor) with a series of backward curved blades (vanes). 5) Foot valve: It acting as a non-return valve. 30 . Three phase energy meter for measuring input power.33)/760 -pressure (delivery) head = (Px10) -difference in level of pressure & vacuum gauges. 4. 2) Casing: It is an airtight chamber surrounding the pump impeller it contains a suction and delivery arrangements 3) Suction pipe: The pipe which connects the center / eye of the impeller to the sump from which liquid is to be lifted. 5. Measuring tape or scale to find the difference in height of pressure and vaccum gauges. 3. 2. Total head (H) H = Hs + Hd + X mwc Hs Hd X . which is connected at the outlet of the pump and it. 4) Delivery pipe: The pipe. DESCRIPITION: Centrifugal pump is a device.three phase single stage centrifugal pump. delivers the liquid to required height. FORMULAE USED: 1. which raises the liquid from lower level to higher level by the action of centrifugal force. It allows the water to raise in one direction only. No: 05 Date: PERFORMANCE TEST ON A SINGLE STAGE CENTRIFUGAL PUMP AIM: To conduct and study the performance 2.H. It is mounted on a shaft usually coupled with an electric motor. (Sec) 2. 6) Strainer: It prevents the entry of mud. sediments and other foreign particles in to the suction pipe. Bourdon type pressure gauge for measuring the delivery pressure. of energymeter disc T sec Output power Po (Kw) Input Power Pi (Kw) S .NAME PLATE DETAILS: Pump: Motor: OBSERVATIONS: Area of the collecting tank (A) = Energy meter constant (Ne) = No. no Efficiency η = Po/Pi x100 1 2 3 4 5 6 31 . (X) = = TABULATION FOR SINGLE STAGE CENTRIFUGAL PUMP: Pressure gauge reading P (kg/cm2) Pressure head Hd (mwc) Vacuum gauge reading V mm of Hg Vacuum head Hs (mwc) Total Head H (mwc) Time(t) for ‘h’ m rise of water (sec) Discharge Q m3/s Time for Nr rev.of revolutions of energy meter (Nr) Rise of water level in collecting tank (h) = Difference in level between suction and pressure gauges. 3.time taken for Nr revolution (sec) 5.Specific weight of water (KN/m2) . Discharge (Q) Vs Total head (H) RESULT: Thus the performance test on single stage centrifugal pump is conducted and characteristic curves are plotted. e) Difference in level between pressure & vacuum gauges. .8[(3600xNr)/(NexT)] -KW Nr Ne T . 3. Keep the delivery valve in close condition. Efficiency (η) η = Po/P i x100 Po -Power output (KW) Pi . Output Power (Po) Po = WQaH W Qa H -KW . d) time of Nr revolution in energy meter T-sec.no. of revolutions in energy meter disc. Discharge (Q) Vs Efficiency (η) 2. c) time for h-m rise of water level in collecting tank-t sec. Take minimum 6 set of readings by varying the head from 0 to 2.Total head (mwc) 4.Power input (KW) PROCEDURE: 1. GRAPH: 1. Maximum efficiency (ηmax) = Discharge at best efficiency point (Qbep) = Head at best efficiency point (Hbep) = Input power at best efficiency point (Pi bep) = Output power at best efficiency point (Po bep) = 32 . Strart the motor and adjust the gate valve to required pressure. a) pressure gauge reading P-kg/cm2 b) vacuum gauge reading V-mm of Hg. Power Input (Pi) Pi =0. Discharge (Q) Vs Input power (Pi) 3.Actual Discharge of water (m3/s) . 4.energy meter constant (rev/kwh) . Note the following reading. 2.8 kg/cm2 The above procedure is repeated for different delivery valve openings and tabulated the readings. Prime the pump if necessary. d2-diameter of the throat (m) 2. Output Power (Po) Po = WQH KW W-specific weight of water (KN/m3) Q-discharge of water (m3/s) H-total head (mwc) 33 . Discharge (Q) Qt = a1a2 √(2gH) / √ a12.area of throat (m2) a2 =(π d22/4) g-acceleration due to gravity (m/s2) H-head over the orifice meter (m) d1-diameter of the pipe (m). the stage of the pump may be increased. 3. 2. DESCRIPTION: Submersible pump is one type of deep well pump. The liquid which is to be pumped does not come in contact with electric parts . The motor and pump shafts are supported in water lubricated bearings. A perforated strainer is also provided in the suction housing of the pump. Three phase energy meter for measuring input power. Here the electronic motor and the unit are coupled together and both are submerged in water.Depending upon the head to which the water is to be lifted. FORMULAE USED: 1. Total head (H) H = X[(Sm/ Sw)-1] m X-difference in manometer reading (h1-h2)m Sm-Specific gravity of mercury (13. Measuring tape or scale to find the difference in height of pressure gauge and water surface in the sump. Collecting tank of known cross section with piezometer and stop watch to measure the flow rate. The electric current is conducted through waterproof cable. 4.Ex.a22 m3/s a1-area of the pipe (m2) a1 =(π d12/4) a2. No: 06 Date: PERFORMANCE TEST ON A SUBMERSIBLE PUMP AIM: To conduct and study the performance of submersible pump. TEST BED REQUIREMENTS: 1. Bourdon type pressure gauge for measuring the delivery pressure.6) Sw-Specific gravity of water (1) 3. NAME PLATE DETAILS: Pump: Motor: OBSERVATIONS: Area of the collecting tank(A) Energy meter constant (Ne) No. of revolutions of energy meter (Nr) Diameter of the pipe(d1) Diameter of the throat(d2) Difference in level of water and pressure gauge (Z) = = = = = = TABULATION FOR SUBMERSIBLE PUMP: Pressure head Hd (mwc) Manometer reading h1 h2 (cm) (cm) X (m) Total Head H (mwc) Time for Nr rev.No Pressure gauge reading P (kg/cm2) 1 2 3 4 5 6 34 . Discharge of Q energy (m³/s) meter disc T (sec) Efficiency Output power Po (Kw) Input Power Pi (Kw) η= [Po/Pi]x100 S. 4. Efficiency (η) η = [Po/P i ]x 100 Po-Power output (KW) Pi.energy meter constant (rev/kwh) T-time taken for Nr revolution (sec) 5. Maximum efficiency (ηmax) = Discharge at best efficiency point (Qbep) = Head at best efficiency point (Hbep) = Input power at best efficiency point (Pi bep) = 35 . d) Difference in level between pressure gauge and water. Total head (H) Vs Discharge (Q) RESULT: Thus the performance test on Submersible Pump is conducted and characteristic curves are plotted. Total head (H) Vs Input power (Pi) 3. Ne. GRAPH: 1. Power Input (Pi) Pi = 0. c) Time of Nr revolution in energy meter T-sec. Take minimum 12 set of readings by varying the head from 0 to 5 kg/cm2 The above procedure is repeated for different delivery valve openings and tabulated the readings. a) pressure gauge reading P-kg/cm2 b) Time for h-m rise of water level in collecting tank-t sec.8[(3600xNr)/(NexT)] -KW Nr –no. 3. Note the following reading.Power input (KW) PROCEDURE: 1. Start the motor and adjust the gate valve to required opening. 2. Keep the delivery valve in full open condition. of revolutions in energy meter disc. Total head (H) Vs Efficiency (η) 2. 33)/760 .Ex. Single phase energy meter for measuring input power. Discharge (Q) Q= Ah/t m3/s A -internal cross sectional area of collecting tank (m2) h -rise of water level in collecting tank (m) t -time taken for h-m rise.Vacuum (suction) head = (Vx10. Measuring tape or scale to find the difference in height of pressure and vacuum gauges. Collecting tank of known cross section with piezometer and stop watch to measure the flow rate. Bourdon type pressure gauge for measuring the delivery pressure. TEST BED REQUIREMENTS: 1 Bourdon type vacuum gauge for measuring the suction pressure. 2. 5. Total head (H) H = Hs + Hd + X mwc Hs Hd X . 3. as it sucks and raises the liquid by actually displacing it with a piston or plunger that executes reciprocating motion in a closely fitting cylinder.pressure (delivery) head = (Px10) -difference in level of pressure & vacuum gauges. 3. (Sec) 2. DESCRIPTION: It is an positive displacement pump. 4. FORMULA USED: 1. No: 07 Date: PERFORMANCE TEST ON A DOUBLE ACTING RECIPROCATING PUMP AIM: To conduct and study the performance of double acting reciprocating pump. Output Power (Po) Po = WQaH KW W-specific weight of water (KN/m2) Qa-actual discharge of water (m3/s) H-total head (mwc) 36 . NAME PLATE DETAILS: Pump: OBSERVATIONS Area of the collecting tank (A) = Energy meter constant (Ne) = No.no % of slip Efficienc y η = Po/Pi x100 1 2 3 4 5 6 37 .of revolutions of energy meter (Nr) Motor: Rise of water level in collecting tank (h) = Speed of Crank Wheel (N) = Difference in level of pressure & vaccum gauge (X) = Diameter of piston (d) = Length of stroke (L) = TABULATION FOR DOUBLE ACTING RECIPROCATING PUMP: Pressure gauge reading P kg/cm2 Pressur e head Hd (mwc) Vacuum gauge reading V mm of Hg Vacuum head Hs (mwc) Total Head H (mwc Time(t) Actual for h cm Discharge rise of water Qa sec m3/s Time for Nr rev. of energy meter disc T sec Theoretical discharge Qt m3/s Output power Po (Kw) Input Power Pi (Kw) = S . 38 . a) pressure gauge reading P-kg/cm2 b) vacuum gauge reading V-mm of Hg.Qa)/ Qt Qt -theoretical discharge (m3/s) Qa -actual discharge (m3/s) PROCEDURE: 1.8(3600xNr)/ (NexT) -KW Nr Ne T -no.energy meter constant (rev/kwh) -time taken for Nr revolution (sec) 5. Keep the delivery valve in open condition.Power input (KW) 6. Percentage of slip % of slip = (Qt . Note the following reading. 4.4. 2. Power Input (Pi) Pi = 0. Efficiency (η) η =[ Po/Pi ] X100 Po-Power output (KW) Pi. 3. Theoritical discharge (Qth) (Qth)=2ApLN/60 Ap=area of piston (m2) L=stroke length of piston (m) N=Speed of crank wheel in rpm 7. 39 . c) time for h-m rise of water level in collecting tank-t sec. Prime the pump if necessary. d) time of Nr revolution in energy meter T-sec.of revolutions in energy meter disc. e) Difference in level between pressure & vacuum gauges. Take minimum 6 set of readings by varying the head from 0 to 3 kg/cm2 The above procedure is repeated for different delivery valve openings and tabulated the readings. . Strart the motor and adjust the gate valve to required pressure. RESULT: Thus the performance test on a double acting reciprocating pump is conducted and characteristic curves are plotted. Total Head Vs Discharge. Maximum efficiency (ηmax) Discharge at best efficiency point (Qbep) Head at best efficiency point (Hbep) Input power at best efficiency point (Pi bep) = = = = 40 . Total Head Vs % of slip 3.GRAPH: 1. Total Head Vs Efficiency (η) 2. 41 . Collecting tank of known cross section with piezometer and stop watch to Measure the flow rate. Bourdon type vacuum gauge for measuring the suction pressure. Three phase energy meter for measuring input power. 5. Total head (H) H = Hs +Hd +X moc Hs -vacuum (suction) head= (vx10. it handles viscous or heavy fluids 2.33)/ (760xSp. They run in close contact within the casing and the fluid is trapped between the gears&casing and discharge in to the delivery pipe.gr of oil X . Develops high pressure. Gear pumps cannot be used with outlet valve in fully closed condition. 1. 3.Deference in level of pressure & vacuum gauges. This consists of two spur gears. Measuring tape or scale to find the difference in height of pressure and Vacuum gauges. (Sec) 2. Advantage. TEST BED REQUIREMENTS: 1. In such condition the pressure developed will either stop the pump or cause breakage.Ex. FORMULAE USED: 1. Discharge (Q) Q= Ah/t m3/s A -internal cross sectional area of collecting tank (m2) h -rise of oil level in collecting tank (m) t -time taken for h-m rise. Discharge at uniform rate (without fluctuations) Limitation. 3. No: 08 Date: PERFORMANCE TEST ON A GEAR OIL PUMP AIM: To conduct and study the performance test on a gear pump. 2 Bourdon type pressure gauge for measuring the delivery pressure. DESCRIPTION: It is external gear pump and it comes under the positive displacement category. which are meshed externally with each other.gr of oil) Hd -Pressure (delivery) head= (px10)/Sp. 4. of energy meter disc T sec Output power Po (Kw) Input Power Pi (Kw) 1 2 3 4 5 6 42 .no Time(t) for ‘h’ cm rise of oil sec Discharge Q m3/s Time for Nr rev.of revolutions of energy meter (Nr) Rise of oil level in collecting tank (h) Difference in level between suction and pressure gauges. (X) Vacuum gauge reading v (mm of Hg) = = = = = = Efficienc y η = Po/Pi x100 Motor: TABULATION FOR GEAR OIL PUMP: Pressure gauge reading P (kg/cm2) Deliver y head Hd (moc) Vacuum head Hs (moc) Total head H (moc) S .NAME PLATE DETAILS: Pump: OBSERVATIONS: Area of the collecting tank (A) Energy meter constant (Ne) specific gravity of oil (s) No. 8(3600xNr)/ (NexT) KW Nr -no. Output Power (Po) Po = WQH W -Specific weight of Oil (KN/m3) Q -Discharge of oil (m3/s) H -Total head (moc) 4. c) Time for h-m rise of oil level in collecting tank-t sec. of revolutions in energy meter disc.3. Total Head Vs power input (pi) 3. V-mm of Hg. Ne . Total Head Vs Discharge (Q) RESULT: Thus the performance test on gear pump is conducted and characteristic curves are plotted. Start the motor and adjust the gate valve to required opening. Note the following reading. e) Difference in level between pressure& vacuum gauges. 3. Prime the pump if necessary. Efficiency (η) η= (po /pi )x` 100 po -Power output (KW) Pi -Power input (KW) PROCEDURE: 1. Total Head Vs Efficiency (η) 2. 2. Keep the delivery valve in full open condition. Maximum efficiency (ηmax) = Discharge at best efficiency point (Qbep) = Head at best efficiency point (Hbep) = Input power at best efficiency point (Pi bep) = 43 . 4. Power Input (Pi) Pi = 0. GRAPH: 1. d) Time of Nr revolution in energy meter T-sec. X-m Take minimum 8 set of readings by varying the head from 0 to 4 kg/cm2 The above procedure is repeated for different delivery valve openings and tabulated the readings. a) pressure gauge reading P-kg/cm2 b) Vacuum gauge reading.energy meter constant (rev/kwh) T -time taken for Nr revolution (sec) 5. 3. 5.Ex. The jet of water deflected through more than 160-170 degree causing the change in momentum of jet and hence an impulsive force is supplied to the cups. 2. 44 . Tachometer for measuring the speed of Francis turbine. this jet of water strikes the buckets of the pelton wheel runner these buckets are in shape of double hemispherical cup or bowl jointed at the middle portion by a wall known as splitter. All the available pressure energy is converted in to kinetic energy by means of nozzle and spear arrangement. Spring balance and set of weight for loading the turbine. 4. The specific speed of the pelton wheel varies from 10-100. 6. TEST BED REQUIREMENTS: 1 Pelton wheel turbine coupled with mechanical break drum. Measuring tape to measure the circumference of brake drum. Bourdon type pressure for measuring head over the turbine. Orificemeter fitted with pressure gauge in a pipeline for measuring flow rate. No: 09 Date: AIM: PERFORMANCE TEST ON PELTON WHEEL TURBINE To study the characteristics of Pelton wheel turbine. used to utilize the high heads for generating power. due to which the runner rotates. DESCRIPTION: Pelton wheel turbine is a impulse type turbine. The water leaves the nozzle in the form of jet. (Q) Q = [a1a2 √(2gh) / √ a12.33) /760) mwc P-pressure gauge reading (kg/cm2) V-Vacuum gauge reading (mm of Hg) 3) Pressure difference (h) h = X[(Sm/ Sw)-1] m X—difference in manometer reading (h1-h2)m Sm—Specific gravity of mercury (13. N.Speed of turbine (rpm) 5) Efficiency (η) η = (Po/Pi)x100 45 .FORMULAE USED: 1) Discharge.6) Sw—Specific gravity of water(1) 4) Torque (T) (W1 ﮧW2) xRxg Nm 5) Input Power (Pi) Pi = ρgQH (KW) 1000 ρ.area of throat (m2) a2 =(π d22/4) g-acceleration due to gravity (m/s2) h-pressure difference in (m) 2) Total head (H) H =( Px10)-[(V x 10.Total head (mwc) 4) Output power (Po) Po = 2ΠNT/ (1000x60) KW T –torque (Nm).density of water Q.Discharge (m3/s) H.a22 ] xCd m3/s a1-area of the pipe (m2) a1 =(π d12/4) a2. no Pressure gauge reading P kg/cm2 Vacuum Gauge reading V mm of Hg Total Head H m of water manometer readings (m) h1 cm h2 cm h m Flow rate Q m3/s Speed weight N rpm W1 (kg) W2 (kg) W= W1 ﮧW2 (kg) Torque T (Nm) Output power Po (Kw) Input Power Pi (Kw) Efficiency η = Po/Pi x100 1 2 3 4 5 6 46 .NAME PLATE DETAILS: Pump: OBSERVATIONS: Nozzle opening position Radius of Break drum (R) m Diameter of inlet pipe (d1) m Diameter of throat pipe (d2) m = = = = Turbine: TABULATION FOR PELTON WHEEL TURBINE: S. Close the sluice and start the pump. Load the turbine by adding the weight to the hanger. 3. speed & inlet pressure gauge reading. Speed (N) Vs Efficiency (η) 2. Maximum efficiency (ηmax) Discharge at best efficiency point (Qbep) Head at best efficiency point (Hbep) Input power at best efficiency point (Pi bep) Output power at best efficiency point (Po bep) = = = = = 47 . 4. Keep the nozzle opening at required opening 2. orificemeter pressure gauge reading.PROCEDURE: 1. spring balance load. Note the load on the hanger. Speed (N) Vs Discharge (Q) RESULT: Thus the performance test on a Kaplan turbine is conducted and characteristic curves are plotted. 6. Repeat the experiment for various loads. 8. Speed (N) Vs Input power (Pi) 3. 5. The start button should be kept pressed for 5-10 seconds and then released. Prime the pump if necessary. Open the delivery valve for required pressure. GRAPH: 1. 7. The water from the runner is discharged in to the tailrace. 3. 4. Measuring tape to measure the circumference of brake drum. the kinetic energy is transformed in to mechanical energy i.a22 ] xCd m3/s a1-area of the pipe (m2) a1 =(π d12/4) a2.e. Orifice meter fitted with pressure gauge in a pipeline for measuring flow rate. 6. FORMULAE USED: 1) Discharge.area of throat (m2) a2 =(π d22/4) g-acceleration due to gravity (m/s2) h-pressure difference in (m) 2) Total head (H) H =( Px10)-[(V x 10. 5.33) /760) mwc P-pressure gauge reading (kg/cm2) V-Vacuum gauge reading (mm of Hg) 48 . the water head is converted in to mechanical energy and hence runner rotates. No: 10 Date: PERFORMANCE TEST ON FRANCIS TURBINE AIM: To study the characteristics of Francis turbine. While passing through the spiral casing and guide vanes. Due to then curvature of the vanes. TEST BED REQUIREMENTS: 1 Francis turbine coupled with mechanical break drum. 2..(Q) Q = [a1a2 √(2gh) / √ a12.Ex. the discharge through runner can be regulated by the operating guide vanes also. a portion of pressure energy (potential energy) is converted in to velocity energy (kinetic energy). the remaining potential energy is converted in to kinetic energy. They are best suited for low heads say 50 to 250 m. Bourdon type pressure for measuring head over the turbine. DESCRIPTION: Francis turbine is an inward flow reaction turbine used in dams and reservoirs of low height to convert hydraulic energy in to mechanical energy.Water thus enters the runner at a high velocity and as it passes through the runner vanes. Water under pressure from pump enters through the volute casing and the guide vanes in to the runner. Tachometer for measuring the speed of Francis turbine. Spring balance and set of weight for loading the turbine. Total head (mwc) 4) Output power (Po) Po = 2ΠNT/ (1000x60) KW T –torque (Nm) N.6) Sw—Specific gravity of water(1) 4) Torque (T) (W1 ﮧW2) xRxg Nm 5) Input Power (Pi) Pi = ρgQH (KW) 1000 ρ.density of water Q.Speed of turbine (rpm) 5) Efficiency (η) η = (Po/Pi)x100 49 .Discharge (m3/s) H.3) Pressure difference (h) h = X[(Sm/ Sw)-1] m X—difference in manometer reading (h1-h2)m Sm—Specific gravity of mercury (13. NAME PLATE DETAILS: Pump: OBSERVATIONS: Radius of Break drum (R) m Diameter of inlet pipe (d1) m Diameter of throat pipe (d2) m = = = Turbine: TABULATION FOR FRANCIS TURBINE: S. no Pressure gauge reading P kg/cm2 Vacuum Gauge reading V mm of Hg Total Head H m of water manometer pressure gauge readings (m) h1 cm h2 cm h m Flow rate Q m3/s Speed weight N rpm W1 (kg) W2 (kg) W= W1 ﮧW2 (kg) Torque T (Nm) Output power Po (Kw) Input Power Pi (Kw) Efficiency η = Po/Pi x100 1 2 3 4 5 6 50 . speed & inlet pressure gauge reading. 3) Close the gate valve and start the pump. 8) Repeat the experiment for various loads. 6) Load the turbine by adding the weight to the hanger. orifice meter pressure gauge reading. Discharge (Q) Vs Efficiency (η) 2. 7) Note the load on the hanger.PROCEDURE: 1) Keep the guide vane opening at required opening 2) Prime the pump if necessary. spring balance load. 4) The start button should be kept pressed for 5-10 seconds and then released. GRAPH: 1. Maximum efficiency (ηmax) Discharge at best efficiency point (Qbep) Head at best efficiency point (Hbep) Input power at best efficiency point (Pi bep) Output power at best efficiency point (Po bep) = = = = = 51 . 5) Open the delivery valve for required pressure. Discharge (Q) Vs Speed (N) RESULT: Thus the performance test on a Francis turbine is conducted and characteristic curves are plotted. Discharge (Q) Vs Input power (Pi) 3. 3. a portion of pressure energy(potential energy) is converted in to velocity energy (kinetic energy). While passing through the spiral casing and guide vanes.Water thus enters the runner at a high velocity and as it passes through the runner vanes. TEST BED REQUIREMENTS: 1 Kaplan turbine coupled with mechanical break drum. The specific speed ranges 200 to 1000. Bourdon type pressure for measuring head over the turbine. the discharge through runner can be regulated by the operating guide vanes also.Ex. 6.. 5.(Q) Q = [a1a2 √(2gh) / √ a12.33) /760)] mwc P-pressure gauge reading (kg/cm2) V-Vacuum gauge reading (mm of Hg) 52 . the remaining potential energy is converted in to kinetic energy.area of throat (m2) a2 =(π d22/4) g-acceleration due to gravity (m/s2) h-pressure difference (m) 2) Total head (H) H = (Px10)-[(V x 10. No: 11 Date: PERFORMANCE TEST ON KAPLAN TURBINE AIM: To study the characteristics of Kaplan turbine. Spring balance and set of weight for loading the turbine. They are best suited for low heads say 10 to 50 m. Tachometer for measuring the speed of Kaplan turbine. Measuring tape to measure the circumference of brake drum. 2. The water from the runner is discharged in to the tail race.a22 ] xCd m3/s a1-area of the inlet pipe (m2) a1 =(π d12/4) a2. Orificemeter fitted with manometer in a pipe line for measuring flow rate. Water under pressure from pump enters through the volute casing and the guide vanes in to the runner. the water head is converted in to mechanical energy and hence runner rotates. DESCRIPTION: Kaplan turbine is an axial flow reaction turbine used in dams and reservoirs of low height to convert hydraulic energy in to mechanical energy. Due to then curvature of the vanes.e. 4. FORMULA USED: 1) Discharge. the kinetic energy is transformed in to mechanical energy i. Speed of turbine (rpm) 5) Efficiency (η) η = (Po/Pi)x100 53 .3) Pressure difference (h) h = X[(Sm/ Sw)-1] m X—difference in manometer reading (h1-h2) m Sm—Specific gravity of mercury (13.density of water Q.6) Sw—Specific gravity of water (1) 4) Torque (T) (W1 ﮧW2) xRxg Nm R.radius of brake drum 5) Input Power (Pi) Pi = ρgQH (KW) 1000 ρ.Total head (mwc) 4) Output power (Po) Po = 2ΠNT/ (1000x60) KW T –torque (Nm) N.Discharge (m3/s) H. NAME PLATE DETAILS: Pump: Turbine: OBSERVATIONS: Radius of Break drum (R) m Diameter of inlet pipe (d1) m Diameter of throat pipe (d2) m = = = TABULATION FOR KAPLAN TURBINE: S. no Pressure gauge reading P kg/cm2 Vacuum Gauge reading V mm of Hg Total Head H m of water manometer readings (m) h1 cm h2 cm h m Flow rate Q m3/s Speed weight N rpm W1 (kg) W2 (kg) W= W1 ﮧW2 (kg) Torque T (Nm) Output power Po (Kw) Input Power Pi (Kw) Efficiency η = Po/Pi x100 1 2 3 4 5 6 54 . pressure & vacuum gauge reading. Discharge (Q) Vs Input power (Pi) 3. spring balance load. manometer reading. Discharge (Q) Vs Speed (N) RESULT: Thus the performance test on a Kaplan turbine is conducted and characteristic curves are plotted. Note the load on the hanger. speed. Load the turbine by adding the weight to the hanger. Open the delivery valve for required pressure. Prime the pump if necessary. Close the gate valve and start the pump. GRAPH: 1. Discharge (Q) Vs Efficiency (η) 2. Maximum efficiency (ηmax) Discharge at best efficiency point (Qbep) Head at best efficiency point (Hbep) Input power at best efficiency point (Pi bep) Output power at best efficiency point (Po bep) = = = = = 55 .PROCEDURE: 1) 2) 3) 4) 5) 6) 7) Keep the guide vanes opening at required opening. The start button should be kept pressed for 5-10 seconds and then released. 8) Repeat the experiment for various loads. 2) What are the types of flow meters? 3) What is the principle of orifice meter? 4) What are the advantages of orifice meter over than flow meters? 5) What is vena-contraction? 6) What is the use of rotameter? 7) Write the Bernoulli’s equation between inlet and orifice plate? 8) What is the use of venturimeter? 9) What are the important components of venturimeter? 10) Why is the length of diverging zone greater than that of converging zone in case of venturimeter? 11) Compare the Cd of venturimeter with other flow meters. 20) What is jet pump? 21) What is the specific use of jet pump? 22) Under what circumstances it is very useful? 23) What is the energy conservation that takes place in the case of a pump? 24) What is the working principle of centrifugal pump? 25) Define specific speed of a pump? 26) What is NPSH of a pump? 27) What is the purpose of foot valve? 28) What is meant by priming? 56 . 12) What is meant by diameter ratio in venturimeter and orifice meter? 13) Determination of pipe Friction Factor 14) Losses in pipe flow due to change of section and change of direction.VIVA (SAMPLE QUESTIONS) 1) Define flow meters. 15) Why does pressure along a horizontal pipe go on decreasing? 16) On what factors Darcy’s friction factor depending? 17) What are HGL and TEL? 18) Difference major and minor losses? 19) Define Pump. 39) What is an impulse turbine? 40) In what way is it different from reaction turbine? 41) What is the need for casing in pelton wheel? 42) Define specific speed? 43) Differentiate between impulse and reaction turbine. why does discharge entering the turbine change and how? 45) What is the purpose of a draft tube? 46) Define specific speed of a turbine? 47) State the function of spiral casing. 48) Give the working principle of gear pump & Give its uses. 44) When the load on shaft changes. 49) What are the other rotary pumps? 50) What is the maximum Pressure that can be developed by the gear pump? 57 .29) Give the working principle of reciprocating pump? 30) What is the difference between SARP and DARP? 31) What is the use of air vessel? 32) What is indicator diagram? 33) Which type of pump is used for general day to day purpose? 34) What is multi-stage pump? 35) How many impellers are there in the submersible pump? 36) What is the signifance of specific speed? 37) Mention the importance characteristics of submersible pump? 38) Define turbine. Fundamentals of Compressible Flow . Fluid mechanics and Machinery 7. . 3 Fluid mechanics and Machinery 4.Bansal.S.REFERENCES: 1.D.Kumar.Yahya. 58 . Hydraulics and Fluid Machines . .Ramamirtham 5.M.R. Fluid mechanics and Machinery 2. .Modi and Sethi. . – Jagdish Lal.K.Streeter and Wylie. Fluid Mechanics.K. . Fluid mechanics 9. Introduction to Fluid mechanics 8. Engineering Fluid mechanics .Rajput. . Hydraulic Machines 10.Fox McDonald. Fluid mechanics 6.L.S.S.K.Kumar.R.