Date : ____________

EXPERIMENT NO :

Name of the Experiment : Performance charecteristics of Pelton turbine

Apparatus :
The apparatus consists of the main sump tank to which the centrifugal pump is
connected working in close circuit. The suction and delivery pipes are connected to the pump with
the bypass delivery valve. The discharge is collected in main tank for all the flows the constant flow
is maintained with the 5 HP centrifugal pump connected to a 5 HP motor working in a close circuit
with flow control valves for each application, a venturi meter connected to mercury manometer and
pressure gauges to measure the pressure at the inlet. A pressure reducing by pass valve is directly
connected to the main sump to avoid excess pressure build up in the system. The readings for
different speeds of the pelton wheel are obtained by controlling the Bypass flow rate suitably; a
steady state will be reached after a few minutes. The control panel consists of three phase motor
starter of 15 amperes to start and stop the pump.

Formula :

Where, Q = Discharge
Cd = Coeff. Of Discharge.
A1 = Area of inlet
A1 = Area of outlet

Diagram :

Theory : The hydraulic machines are defined as those which convert the hydraulic energy
(energy possessed by water) into mechanical energy which is further converted into electrical
energy or the mechanical energy into hydraulic energy. The hydraulic machines which convert
the hydraulic energy (energy possessed by water) into mechanical energy are called turbines.
This converted mechanical energy is used in running an electric generator which is directly
coupled to the shaft of the turbine. Thus mechanical energy is converted into electrical energy
the electrical power which is obtained from the hydraulic energy (energy of water) is known as
hydro electric power.
The Pelton wheel or Pelton turbine is a tangential flow impulse turbine. The
water strikes the bucket along the tangent of the runner. The energy available at the inlet of the
turbine is only kinetic energy. The pressure at the inlet and out let of the turbine is atmospheric.
This turbine is used for high heads and is named after L.A. Pelton, an American Engineer.
The main parts of the pelton turbine are:
Nozzle and flow regulating arrangement (sphere) Runner
with buckets
Casing
Breaking jet
Nozzle and flow regulating arrangement (sphere):- The amount of water striking the buckets (vanes) of
the runner is controlled by providing a sphere in the nozzle the sphere is a conical needle which is
operated either by hand wheel or automatically in an axial direction depending upon the size of the unit.
When the sphere is pushed forward into the nozzle the amount of water striking the runner is reduced.
On the other hand, if the sphere is pushed back, the amount of water striking the runner increases.

Runner with buckets:- it consists of a circular disc on the periphery of which a number of
buckets evenly spaced are fixed. The shape of buckets is of a double hemispherical cup or bowl.
Each bucket is divided into two symmetrical parts by a dividing wall which is known as a
splitter. The jet of water strikes on the splitter. The splitter divides the jet into two equal parts
and the jet comes out at the outer edge of the bucket. The buckets are shaped in such a way that
the jet gets deflected through160 0 or 170 0 . The buckets are made of cast iron, cast steel
bronze or stainless steel depending upon the head at the inlet of the turbine.

Casing:-The function of the casing is to prevent the splashing of water and to discharge water
to tail race. It also acts as safeguard against accidents. It is made of cast iron or fabricated steel
plates. The casing of the Pelton wheel does not perform any hydraulic function

Breaking jet:-when the nozzle is completely closed by moving the sphere in the forward
direction, the amount of water striking the runner reduces to zero. But the runner due to inertia
goes on revolving for a long time. To stop the runner in short time, a small nozzle is provided
which directs the jet of water on the back of the vanes. This jet of water is called breaking jet

Specifications :
1. Sump/Main Tank: 4x2x2
2. Capacity:453 liters
3. Centrifugal Pump::5 HP manual priming with foot valve
a. Suction Pipe diameter:65mm 2.5”
b. Delivery pipe diameter:55 mm (2”)
c. Piping:55 mm GI
d. Type:Single Stage e.
e.RPM:2880
f. Max Output pressure:(4Kgf/cm 2 )
g. Head:38 m h
Discharge:7L/sec
4. Control Valves: 2” ball valves made of brass
5. Material:Cr powder coated MS stand
6. Mounting: On MS C channel stand
7. Supply:415v AC 3ф
8. Delivery Pressure gauge:(0 - 4Kgf/cm 2 )
9. No. Buckets: 18
10. Dynamometer: :Rope Brake type
11.Spring Balance/Electronic Weight Balance:: 10 Kg 1 Nos Or 10 Kg load Cell
 Procedure :
1. Make all the necessary water and electrical connections.
2. Close all the application valves and completely open the by pass delivery valve of the
centrifugal pump this avoids the development of sudden pressure in the system.
3. Start the pump and allow the water to flow through the system wait for 2-3 minutes.
4. Adjust the discharge by operating the by pass delivery valve.
5. Always keep open the delivery valve, do not close it completely.
6. Remove the air bubbles from the U tube differential manometer.
7. Slowly close the bypass delivery valve and allow the water to flow through the nozzle and
strike the buckets
8. Note the reading on the pressure gauge
9. Note the reading of the right and left column of the manometer
10. Adjust the nozzle opening by operating the sphere so as to achieve the jet of water of
required velocity to strike on the buckets.
11. Set the dynamometer speed to some desired value.
12. Apply loads on the dynamometer by revolving the hand wheel and take corresponding
readings of spring balance and measure the speed of the turbine by tachometer.
13. Change the position of regulating valve so as to increase flow rate towards the buckets
14. Repeat the procedure for 4 to 5 set of readings
15. Switch off the pump.
16. Plot the graph for :-
Efficiency Vs Power,
Efficiency Vs Speed,
Power Vs Speed

Observations:-

Suction Pipe diameter, D1= 65 mm (2.5”)

Diameter of brake drum = 210mm
Circumference of brake drum =Pi x D
Diameter of rope ds= 12mm
Equivalent drum diameter, D= Diameter of brake drum + 2 x Diameter of rope = 240mm
Diameter of throat of Venturimeter = 31.5mm
inlet pipe diameter of Venturimeter = 63mm
Coefficient of discharge of Venturimeter Cd = 0.96 (assumed) Electric
motor efficiency ηe = 90%
Mass density of water = 1000 Kg/m
 Observation Table :

Sr. Deflection of the Differential Load

No. Pressure mercury columns of head in Meters applied on Speed
gauge the manometer of Water turbine of
reading Left Right Pressure Turbine
(P) H 1= h( Dead/Spring Dead/Spring
limb limb head N
h1 h2 h2-h1 h 2 – h1/ s) weight W 1 weight W 2
unit Kg/cm2 m m m m kg kg rpm
1
2
3
1. Manometer Readings:
Differential head in Meters of Water H = X [(s 2 - s 1 ) / s 1 ] (in meter) Where, s 1 =
Specific Gravity of Liquid Flowing in Pipe (Water) = 1.0
s 2 = Specific Gravity of Manometric Fluid (mercury) = 13.6 Pressure
Intensity P = W x H (N/m)
Where, W = Specific weight of water (9810 N/m)

2. Discharge of pump is to be calculated by Venturimeter:-

The diameter of the inlet pipe, d 1 = 65 mm
Area of pipe =  xd12

=  x 65 2
= 0.004225 mm 2
The diameter of the throat, d 2 = 31.5mm Area
of the throat a 2 =  xd22

=  x31.25 2
= 0.00077934 mm 2
Cd = 0.96 (assumed) Actual
discharge,

Where C d = Co-efficient of Discharge for Venturimeter and its value is less than1. Cd = 0.96
Q act = _____ m 3 /sec

3. Pressure Gauge reading, P = _____ Kg/cm 2

4. Net head on turbine H = P/H = 3.998 m of water
5. W=ρg
6. ρ = 1000 kg/m 3
7. g = 9.81 m/s 2
8. Input power (Pi)
P i = WQH watt
 P i = WQH / 1000 kW
Where,
W = Specific weight of water Q
= Discharge m 3 /sec.
9. Resultant load on turbine:
W r = ( W 1 - W 2 ) kg x 9.81N (for double rope wound, dynamometer Condition)

10. Torque on turbine,

(w 1 - w 2 ) (D ds)
T= ................................. Nm
2
11. Out put Power (P o )
P0=2ΠNT / 60 watt

N = Speed of the turbine in r.p.m.

12. Overall Efficiency ( )
o = (P o /P i ) x 100.
= ___________%
Result :

Discharge Input Speed of Resultant Output Efficiency

Obs Q Manometric Power Turbine N load on Power (%)
No. (m /sec)
3
Head Pi RPM turbine Po
(watts) (watts)

1
2
3
4

Result :-
The average efficiency of Pelton wheel turbine is found to be _____________ %.
 Date : ____________
EXPERIMENT NO :

Name of the Experiment : Performance charecteristics of Francis turbine

Apparatus :1) Francis Turbine, (2) A supply pump unit to supply water to the above Francis Turbine,
(3) Flow measuring unit consisting of an Orifice meter and pressure gauge and (4) Piping system. (5)
Suitable capacity sump tank is provided.

Formula :-

1. Input Power =  QH in kW

Where  = Specific weight of water = 9.81 kN/m3

Q = Discharge in m3/sec.

H = Supply head in meters.

2 NReW x 9.81
2. Brake Power =------------------- kW
60000

Output
3. Efficiency = ------------- x 100%

Input
Diagram :
 Theory :

SPIRAL CASING: is of close grained cast iron with integral legs and 150mm. Flanged inlet.

RUNNER: is of bronze, designed for efficient operation accurately machined and smoothly finished.

GUIDE VANE MECHANISM: Consists of bronze guide vanes, operated by a hand wheel through a link
mechanism. External dummy guide vanes are provided to indicate the position the actual guide vanes
working inside the turbine.

SHAFT: is of chrome plated EN8 steel accurately machined and provided with a bronze sleeve at the
stuffing box.

BALL BEARINGS: is of double row deep groove rigid type in the casing and double row self-aligning
type in the bearing pedestal both of liberal size.

DRAUGHT BEND: is provided at the exit of the runner. To the bend is connected, a straight conical
draught tube of mild steel fabrication of 500 length.

BRAKE ARRANGEMENT: Consisting of a machined and polished cast iron brake drum, cooling water
pipes, internal water scoop, discharge pipe, standard cast iron dead weights, spring balance, rope brake etc.,
arranged for loading the turbine.

BASE PLATE: is of cast iron box type ribbed construction.

FINISH: is of high standard suitable for laboratory use in technical institutions.

SUMP TANK: a suitable size of sump tank is provided for closed circuit operation.

TECHNICAL SPECIFICATION

FRANCIS TURBINE:

1. Rated Supply Head : 10 meters

2. Discharge : 1000 LPM

3. Rated Speed : 1250 rpm

4. Power Output : 1 kW

5. Runaway Speed : 1750RPM

6. Runner diameter : 160mm

7. No. of guide vanes : 10

8. P.C.D. guide vanes : 230 mm

9. Brake Drum Diameter : 230mm

10. Rope Brake Diameter : 15mm

SUPPLY PUMP SET:

1. Rated Head : 10 meters

2. Discharge : 1200LPM

3. Normal Speed : 1440 RPM

4. Power Required : 5 HP

5. Size of pump : 100mm x 75mm

6. Type : Centrifugal medium speed,

single suction volute

FLOW MEASURING UNIT:

1. Inlet diameter of Orifice meter : 80mm

2. Orifice meter diameter : 60 mm

3. Pressure Gauges : 0-2Kg/cm2 – 2 Nos.

4. Meter constant for Orifice meter : K=9.11 x10-3 h (h in m of water)

BALL BEARING USED:

1. in the casing : 6308 (or its equivalent) –1

2. in the bearing pedestal : 1308 (or its equivalent) -1

OIL SEALES USED (OMCO BRAND):

1. Shaft sealing : OM 457510 – 2Nos.

2. Guide Vane Seal : OM 153510 – 10Nos.

Experimental procedure :-

Make sure before starting that the pipelines are free foreign matter. Also note whether all the joints are
watertight and a leak proof. Prime the pump and start it with closed gate valve. The guide vanes in the
turbine should also be in the closed position while starting the pump. See that all the ball bearing and bush
bearings in the units are properly lubricated. Then slowly open the gate valve situated above the turbine
and open the valve fitted to the pressure gauge and see the pump develops the rated head. If the pump
develops the required head, slowly open the turbine guide vanes by rotating the hand (which operates the
guide vanes through suitable link mechanism) until the turbine attains the normal speed for about for ten
minutes and carefully note the following:

• Operation of the bearings, temperature rise, etc.

• Vibration of the unit.

• Steady constant speed & speed fluctuation if any.

The addition to this, on the pump side, notes the operation of the stuffing box. (the stuffing box should
show an occasional drip of water. If the gland is over tightened, the leakage stops but the packing will heat
up, burn and damage the shaft).
 If the operation of the above parts is normal, load the turbine slowly and take readings. To load the
turbine standard dead weight are provided with figures stamped on them to indicator their weights. Open
the water inlet valve and allow some cooling water through the brake drum when the turbine runs under
load, so that the heat generated by the brake drum is carried away by the cooling water. Do not suddenly
load the turbine. Load the turbine gradually and at the same time open the guide vanes to run the turbine at
the normal speed.

Observations :

Brake drum diameter D=0.230m

Input total head H in m of water = Pressure gauge reading in kg/cm2x 10

Rope Diameter t = 0.015m

Orifice meter Head h in m of water h=(p1-p2)x 10m of water

Effective Radius of = (D/2 + t)

Discharge Q = K h (h in m of water)

Input power IP = x H x Q kW (H in m of water)

Brake drum Re = 0.13m

Brake Drum net load W = (W1 + weight of rope & hanger) – W2 kg Weight of rope & hanger = 0.916kg

Turbine output OP = (2 NWRe x 9.81)/60000 KW

Guide Vane opening = 0.5

Efficiency = (output / Input) x 100% “K” value: 9.11 x10-3

Observation Table :-

Sr Pressu Vacuu Total Mano Actual Spee Net Load Input Outpu Efficienc
. re m Head meter Equival Dischar d (W) t y
N gauge Gauge (H)x readi ent ge (N)
o. readin Readin 10 ng water
g g (V) head
(G)
H=G W W
x h=12.6x Qa W
+V 1 2
Kg/cm K K
Kg/cm2 m m m3/sec rpm kg KW KW %
2
g g
1.
2.
3.
4.

Result :-
The average efficiency of Francis turbine is found to be _____________ %.
 Date : ____________
EXPERIMENT NO :

Name of the Experiment : Performance charecteristics of Kaplan turbine

Apparatus :
The test rig consists essentially of (1) Kaplan Turbine (2) A supply pump unit to supply water to the above Kaplan
turbine. (3)A flow measuring unit consisting of a Orifice meter and Pressure gauge and (4)Piping system (5) A
pressure and vacuum gauge are provided to find out the supply head of the turbine. (6)Sump tank.

Formula :
(C) Input Power =  QH in kW
Where  = Specific weight of water = 9.81 kN/m3
Q = Discharge in m3/sec.
H = Supply head in meters.
2 Π NT x 9.81
(D) Brake Power = ------------------- kW
60000
Output
(E) Efficiency = ----------- x 100%
Input

Where, N = Turbine speed in RPM.

T = Torque in Kg-m, (effective radius of the brake drum in meters (R) x the net brake load in kg.
(W)
Re = 0.165m

Theory : The turbine consists of a spiral casing, a rotor assembly, shaft and brake drum all mounted on
a sturdy support pedestal. A straight conical draught tube is provided vertically after the runner. A
Transparent hollow Perspex cylinder is provided in between the casing and the draught tube. Rope brake
arrangement with suitable pulleys is provided for loading the turbine. The input into the turbine is
controlled by a set of guide vanes .The net supply head is measured by means of a pressure and vacuum
gauge. For the measurement of speed tachometer is to be used.

SPIRAL CASING: Is of close grained cast iron with flanges inlet, designed for constant velocity water
distribution.

RUNNER: Is of Stainless steel with four aero – foil blades, designed to the latest hydro – dynamic
principles. All parts coming in contact with water are made either of bronze or of stainless steel to prevent
corrosion.

GUIDE VANE MECHANISM: Consists of bronze vanes cast integral with their spindles. By suitable
external link mechanism these can be set at different relative positions, and two external dummy guide
vanes are provided to indicate the exact position in the actual guide vanes working inside the turbine, thus
showing the relative water passages through the guide apparatus for the different position of the guide
vanes.

SHAFT: Is of Chrome plated EN 8 Steel.

BALL BEARINGS: Are of heavy duty type designed for long life. One double row deep groove rigid ball
bearing to take care of radial loads and a thrust ball bearing to take the axial thrust and self weight of the
rotor assembly are provided in the bearing bracket. A Self aligning type ball bearing is used in the bearing
pedestal for trouble free operation.
OBSERVATION WINDOW: A transparent Perspex hollow cylinder window for observation of flow past
the runner is provided in between the casing and draught tube.

SUPPORT PEDESTAL: Is of mild steel, robust in construction.

DRAUGHT TUBE: Of mild steel fabricated construction and length 500mm is provided at the exist of the
runner.

TECHNICAL SPECIFICATION

KAPLAN TURBINE:

1. Rated Supply Head : 5 to 8 meters

2. Discharge : 1500 LPM

3. Rated Speed : 1000 rpm

4. Power Input : 1 kW

5. Runaway Speed : 1750RPM

6. Runner outside dia : 150mm

7. Hub diameter : 78mm

8. No. of runner blades : 4

9. No. of guide vanes : 10

10. P.C.D. guide vanes : 230 mm

11. Brake Drum Diameter : 300mm

12. Rope Brake Diameter : 15mm

SUPPLY PUMPSET:

1. Rated Head : 9 meters

2. Discharge : 1500LPM

3. Normal Speed : 1440 RPM

4. Power Required : 7.5 HP

5. Size of pump : 150mm x 150mm

6. Type : Medium speed, Centrifugal, single suction volute

FLOW MEASURING UNIT:

1. Size of Orifice meter : 150mm

2. Area Ratio : 0.45

3. Orifice Diameter : 100.62mm

4. Pressure Gauge : Double column differential type

5. Orifice meter Constant : Q = 2.3652 x 10-2  p (Q = K p ) p in m of water

BALL BEARING USED:

1. In the casing : 6308 –1 No

2. In the casing thrust bearing : C 209 - 1 No.

3. In the bearing pedestal : 1308 -1 No.

OIL SEALES USED

1. Shaft sealing : 45-75-10 – 2Nos.

2. Guide Vane Seal : 16-35-10 – 10Nos.

Experimental Procedure :

The suction pipe with foot valve should be adequately submerged on the water. The flow measuring
unit, 150mm Orifice meter and the pressure gauges are so arranged and mounted that the readings can be
conveniently taken. Make sure before starting that the pipelines are free from foreign matter also note
whether all the joints are water tight and leak proof. Prime the pump and start it. While starting the main
150mm butterfly valve near the turbine should be closed. The guide vanes in the turbine shall be in the
closed position. See that all the ball bearing and bush bearing in the unit are properly lubricated. Then
slowly open the valve near the turbine. A pressure and vacuum gauge is used to measure the supply head
on the turbine. If the pump develop the rated head slowly open the turbine guide vanes by rotating the hand
wheel (which operates the guide vane through suitable mechanism) until the turbine attains the normal
speed of 1000RPM. Run the turbine at the rated speed for about 15 minutes and carefully note the
following:-

1. Operation of the bearings, temperature rise, noise etc.,

2. Vibration of the unit.
3. Steady constant speed and fluctuation, if any.

In addition to this, on the pump side note operation of the stuffing box. (The stuffing box should on
occasional drip of water. If the gland is over tightened, the leakage stops, but the package will heat up and
burn damages the shaft).

If the operations of the above parts are normal, load the turbine slowly and take readings. To load the
turbine, rotate the hand wheel of circular balance. Open the water inlet valve and allow some cooling water
through the brake drum when the turbine runs under load, so that the heat generated by the brake drum is
carried by the cooling water. Don’t suddenly load the turbine. Load the turbine gradually and at the same
time open the guide vanes to run the turbine at normal speed.

Observations :

Brake drum diameter D=0.3m

Input total head H in m of water=Pressure gauge reading in kg/cm2x10 m

Rope Diameter t = 0.015m Orifice meter Head p in m of water = (p1-p2) x 10

 Effective Radius of = (D/2 + t) = 0.165m

Weight of rope & Hanger = 0.76 kg

Discharge Q = Kp (h in m of water)

Guide Vane opening = 0.8

Input Power IP =  x Q x H kW (H in m of water)

Run away speed = 1750 RPM Brake Drum net load W = (W1 + Weight of rope &hanger)-W2 kg

‘K’ Value = 2.3652 x 10-2

Turbine output OP = (2NWRe x 9.81)/60,000 kW

Efficiency  = (output / Input) x 100%

Observation Table :-

Pressur Spring
Sr Weig
e (H) Orifice meter balanc Net
. Discharge ht on Spee Outp Efficien
Gauge head Pressure e Weig Input
N hange d ut cy
Readin Gauge Reading readin ht
o. r
g g
P P1 P2 P Q W1 W2 W N OP IP 
kg/cm2 kg/cm2 m3/sec kg kg kg rpm kW kW %

1.

2.

3.

4.

The average efficiency of Kaplan turbine is found to be _____________ %.

 Date : ____________
EXPERIMENT NO :

Name of the Experiment : Performance characteristic of Variable Centrifugal speed pump

Diagram :

Theory :
Main Parts of a Centrifugal Pump:The following are the main parts of a centrifugal pump
1. Impeller
2. Casing
3. Suction pipe with a foot valve and strainer
4. Delivery pipe

Impeller: - The rotating part of a centrifugal pump is called ‘impeller’. It consists of a series of backward
curved vanes. The impeller is mounted on a shaft which is connected to the shaft of an electric motor.
Casing: - The casing of a centrifugal pump is similar to the casing of a reaction turbine. It is an air tight
passage surrounding the impeller and is designed a way that the kinetic energy of the water discharged at
the outlet of the impeller is converted into pressure energy before the water leaves the casing and enters the
delivery pipe. The following three types of casing are commonly adopted.
(A) Volute Casing
(B) Vortex casing
(C) Casing with guide blades.
Suction pipe with a foot valve and strainer: - A pipe whose one end is connected to the inlet of the pump
and other end dips into water in a sump is known as suction pipe. A foot valve which is a non -return valve
or one-way type of valve is fitted at the lower end of the suction pipe. The foot valve opens only in the
upward direction. A strainer is also fitted at the lower end of the suction pipe.
Delivery pipe: - A pipe whose one end is connected to the outlet of the pump and other end delivers water
at a required height is known as delivery pipe.

Definition of Heads and Efficiencies of a Centrifugal Pump:-

Suction head (hs):- it is the vertical height of the centre line of the centrifugal pump above the water
surface in the tank or pump from which water is to be lifted this height is also called suction lift and is
denoted by (hs).
Delivery head (hd):- the vertical distance between the centre line of the pump and the water surface in the tank to which
water is delivered is known as delivery head. This is denoted by (hd)
Static head (Hs):- the sum of suction head and delivery head is known as static head. This denoted by (Hs)
and is written as
Hs=hs+hd

Manometric head: - it is defined as the head against which a centrifugal pump has to work. It is denoted
by Hm.

Hm= hs + hd + hfs + hfd

Where,
hs = Suction head
hd = Delivery head
hfs = frictional head loss in suction pipe
hfd = frictional head loss in delivery pipe
Vd = velocity of water in delivery pipe

Efficiencies of a centrifugal pump: - in case of a centrifugal pump, the power is transmitted from the
shaft of the electric motor to the shaft of the pump and then to the impeller. From impeller, the power is
given to the water. Thus power is decreasing from the shaft of the pump to the impeller and then to the
water. The following are the important efficiencies of a centrifugal pump.

a. Manometric efficiency

b. Mechanical efficiency

c. Overall efficiency

• Manometric efficiency the ratio of the Manometric head to the head imparted by the impeller to the
Water is known Manometric efficiency

Manometric Head
ηman = ..........................................................................................
Head imparted by impeller to water

b) Mechanical efficiency the ratio of power available at the impeller to the power at the shaft of the
centrifugal pump is known as mechanical efficiency and is given as:

Power at the impeller

η m = ............................................................................
Power at the Shaft

c) Overall efficiency it is defined as the ratio of power output of the Pump to the p
ower input to the pump.
The power output of the pump in

ηo = W Hm / S * 1000

Specification :

1. Sump/Main Tank : 1.5’x4’x1’

2. Capacity : 170 liters
3. Measuring Tank : 305 x 305 x 305 mm
 4. Capacity : 28.32 liters
5. Centrifugal Pump : 1 HP manual priming with foot valve
a. Suction Pipe diameter : 25.4 mm (1”)
b. Delivery pipe diameter : 25.4 mm (1”)
c. Piping : 25.4 mm GI
d. Type : Single Stage
e. RPM : 2800
f. Max Output pressure :(1Kgf/cm2)
6. Control Valves : 1” ball valves made of brass
7. Material : Cr powder coated MS stand
8. Mounting : On castor wheels
9. Motor : 1 HP 3000 RPM DC with dimmer
speed controller for steeples speed
regulation
10. Supply : 230v AC 1ф
11. Energy meter constant : 3200
12. Delivery Pressure gauge :( 0 – 10Kgf/cm2)
13. Suction pressure gauge : 0- -750 mm/hg
14. Belt adjustment : Screw type

Experimental Procedure :

1. Make all the necessary water and electrical connections.

2. Close all the application valves and completely open the bypass delivery valve of the centrifugal
pump this avoids the development of sudden pressure in the system.
3. Start the pump and allow the water to flow through the system wait for 2-3 minutes.
4. Adjust the discharge by operating the delivery valve.
5. Always keep open the delivery valve, do not close it.
6. Allow water to flow in the main tank.
7. Measure the distance between the gauges this is called as the difference between potential heads i.e. Δz.
8. Note the diameters of suction and delivery pipes D1 and D2
9. Set the motor speed to some desired value.
10. Note and measure the area of the measuring tank.
11. Measure the time required for 5 to 10 revolutions of electric disc for calculation of input power.
12. Close the discharge valve of the main tank collect water in the measuring tank to measure the actual
discharge i.e. the volume of the water collected in the measuring tank for ‘T’ seconds use the stop
watch to measure the time. Measure the time required for rise in the height of water level (say 20 cm).
13. Measure the RPM of the main shaft of the pump by tachometer.
14. Note the suction and delivery pressures.
15. Select different speed of the motor from the controller and repeat steps 11 to 15.
16. The water collected in the measuring tank should be drained in the main tank after taking the readings.
17. Vary the discharge by changing the position of delivery valve for different delivery and suction
pressure and repeat the steps 11 to 15 for different set of readings.
18. Plot the graph for

1) Discharge Vs head
2) Discharge Vs power
3) Discharge Vs overall efficiency (plot discharge on x- axis)
 Observation Table :-
Time for 20 Time for rise in RPM of the
Revolution of 10 cms height of crank shaft N
Delivery
Sr. No. Suction pressure disc of energy water level in
pressure
meter in container in
seconds seconds

M of Kg/ M of
Mm of Hg
water cm^2 water

01.
02.
03
04
05

Calculation :-

NO. Of disc revolution x 3600 x  t x   x 1000

1. Input Power = ...................................................................................................................
Constant of electric motor x Time for no. Of Revolution of disc

2. Volume of water collected in the tank = area of the tank x rise in level of water in tank

3. Specific weight of water, w=9810 N/m 2

Volume of water collected

4. Discharge (Q) = ................................................
Time of water collected

m 3 /sec

5. Manometric head (Hm)

Hm= Suction head + Delivery Head

Hm= Hs + Hd = 1.36 + 3.0 = 4.36m

6. Output power of the pump = WQHm watt

7. Overall efficiency Output power

   x 100
Input Power

Result: Efficiency of the centrifugal pump is found to be_________

 Date : ____________
EXPERIMENT NO :

Name of the Experiment : Performance characteristic of Reciprocating pump

Formula :
Q = Discharge in one revolution x No. of revolution per second

ALN
Q = ............
60

PgALN
W = .................
60
PgALN
Work done / sec = ...................... ( HS + Ha )
60

PgALN x ( HS + Ha )
Power required to drive the pump, in kW = ....................................
60 x 1000
Diagram :

Theory :-
Figure shows a single acting reciprocating pump, which consists of a piston which moves
forward and backward in a close fitting cylinder. The movement of the piston is obtained by
connecting the piston rod to the crank by means of a connecting rod. The crank is rotated by
means of an electric motor. Suction and delivery pipes with suction valves and delivery
valves are connected to the cylinder. The suction and delivery valves are one way valves or
non-return valves, which allow the water to flow in one direction only. Suction allow water
form suction pipe to the cylinder which delivery valve allows water from cylinder to delivery
pipe only. When crank starts rotating, the piston moves to and fro in the cylinder. When crank
is at A, the piston is at extreme left position in the cylinder. As the crank is rotating from A to
C, (i.e. from θ=0 to θ =180 o ), the piston is moving towards right in the cylinder. The
movement of the piston towards right creates a partial vacuum in the cylinder. When crank is
rotating from C to A (i.e. from θ=180 to θ =360 o ), the piston from its extreme right position
starts moving towards left in the cylinder. The movement of the piston towards left increases
the pressure of the liquid inside the cylinder more than atmospheric pressure. Hence suction valve closes
and delivery valve opens. The liquid is forced into the delivery pipe and is raised to a required height.
 Experimental Procedure :-

1. Make all the necessary water and electrical connections.

2. Close all the application valves and completely open the by pass delivery valve of
the reciprocating pump this avoids the development of sudden pressure in the system.
3. Start the pump and allow the water to flow through the system.
4. Adjust the discharge by operating the delivery valve.
5. Always keep open the delivery valve, do not close it.
6. Allow water to flow in the main tank.
7. Measure the distance between the gauges this is called as the difference between potential
heads i.e. ∆z.
8. Note the diameters of suction and delivery pipes D1 and D2.
9. Set the motor speed to some desired value.
10. Note and measure the area of the measuring tank.
11.Start the pump and wait for 2-3 minutes. Measure the time required for 10 to 20
revolutions of electric disc for calculation of input power.
12. Close the discharge valve of the main tank collect water in the measuring tank to
measure the actual discharge i.e. the volume of the water collected in the measuring tank
for ‘T’ seconds use the stop watch to measure the time. Measure the time required for rise
in the height of water level (say 10 cm).
13. Measure the RPM of the main shaft of the pump by tachometer.
14. Note the suction and delivery pressures.
15. Select different speed of the motor from the controller and repeat steps 11 to 15.
16. The water collected in the measuring tank should be drained in the main tank after
taking the readings.
17. Vary the discharge by changing the position of delivery valve for different delivery and
suction pressure and repeat the steps 11 to 15 for different set of readings.

Observation:-
1. Suction Pipe diameter, D 1 = 25.4 mm

2. Cross section area of suction pipe, A s = (л/4) d12

= (3.14/4) x 0.0254 x 0.0254
= 0.000506 m 2
3. Delivery pipe diameter,D 2 = 12.7mm

4. Cross section area of delivery pipe, A d = (л/4) d22

= (3.14/4) x 0.0127 x0.0127
= 0.0001267m 2
5. difference between heights of pressure gauge points i.e. Z 2 and Z 1 from datum, ∆Z
 =Z2-Z1
= 0.335 m
6. Diameter of cylinder bore, D =0.0254 m
7. Length of stroke, L =0.01905 m
8. Area of Measuring Tank, A = 0.02837 m 2
9. Transmission efficiency η t = 60%
10. Electric motor efficiency η e = 70%
11. Energy meter constant = 3200
Observation Table :

Time for 20 Time for rise RPM of the

Revolution of in 10 cms crank shaft N
Delivery disc of energyheight of water
Sr. No. Suction pressure
pressure meter in level in
seconds container in
seconds

M of
Mm of Hg M of water Kg/ cm2
water

01.
02.
03.
04.
05.

NO. of Energy meter blink x 3600 x  t x   x 1000

1. Input Power = ...................................................................................................................
Constant of electric motor x Time for no. of blink

(л/4) d22
2. Qth = ......................

60

Area of measuring tank x 0.1

3. Qact = ...............................................................................
Time of rise

Q act
4. Velocity of water in suction pipe = ..............................
Area suction pipe

Q act
5. Velocity of water in Delivery pipe = ..............................
Area delivery pipe

6. Out put power = w Q act H

Actual discharge

7. Coefficient of discharge, C d = ...................................

Theoretical discharge
 Qth

= ...............

Q act
8. Slip = (Q th – Q act )

(Q th – Q act )
Percentage slip = ........................ x 100
Q act

= (1 – Q act / Q th ) x 100

9. Efficiency ,
Output power
   x 100
Input Power

Result: Efficiency of the reciprocating pump is found to be_________