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DEPARTMENT OF MECHANICAL ENGINEERING
HYDRAULIC MACHINES AND SYSTEMS LAB (ME3127)
II B. Tech – I Semester
(Mechanical Engineering)
GURU NANAK ENGINEERING COLLEGE
Ibrahimpatnam, Ranga Reddy District – 501 506 (A. P.)

IMPACT OF FREE JETS
Objective: - To determine the coefficient of impact of Jet on different vanes by comparing
actual force with theoretical force for different types of vanes.
Apparatus: -1.Sstop clock,
2.meter scale,
3.Impact of jet on vane setup
Theory: - When the jet of water is directed to hit the vane of any particular shape, the force is
exerted by the fluid in the opposite direction of the jet. The amount of force exerted depends
on the diameter of the jet, shape of the vane, fluid density and velocity of the jet. It also
depends on whether the vane is moving or stationary. At this present set up we are
concerned about the force exerted on the stationary vanes. The theoretical value of the force
is different for different types of vanes.
Formulae for Calculations: -
1). Basic data contents
(i). 1kg/cm2
= 760 mm of Hg (10m of water)
(ii). Density of water, ‘ρ’ = 1000 kg/m3
(iii). Diameters of the jet, 8mm, 5mm and 3.5mm
2). Velocity of the Jet, in m/s
V = Q / [1000x 60xA]
Where Q → Discharge rate, liters/min
A→ Area of the jet, m2
3). Theoretical, Tangential force acting on vane in N
a) For Hemispherical vane
Fthe = 2ρAV2
/g
b) For Flat plate
Fthe = ρAV2
/g
c) For inclined plate
Fthe = 2ρAV2
/g Sinθ, Where, θ → Angle of jet deflection in ‘degrees’
ρ → Density of water, 1000 kg/m3
; A→ Area of the jet, m2

V→ Velocity of the jet in m/s; g→ Acceleration due to gravity, m2
/s
4). Actual, Tangential force acting on vane in N
Fact = F x g
Where, F→ Force indicator reading in kgf
g→ Acceleration due to gravity, m2
/s
5). Jet Impact co-efficient
Cd = Fact / Fthe
Procedure:- 1. Fill up the sump tank with clean water,
2. Keep the pump delivery valve closed,
3. Keep the Force indicator reading at minimum (zero),
4. Press the green button of the supply pump starter. The pump picks up full speed
and become operational,
5. Now open the delivery valve slowly
6. At one particular velocity of the jet, note down the pressure gauge reading, force
indicator reading, flow rate/ Discharge of the jet and tabulate the readings
7. Repeat the step no. 6 at different jet velocities and at different diameter jets.
8. After the experiment is over keep delivery valve closed, and switch-OFF the
pump.
Fig: Impact free water jet on a curved vane at the center

Sample Calculations: -
Precautions: - 1.Do not start the pump if the supply voltage is less than 250V,
2. The water in the sump tank should be clean.
3. It is recommended to close delivery valve before starting.
Graphs: -To study Impact force and jet co-efficient plot the following graphs,
i). Theoretical Tangential force, Fthe on X-axis Vs actual Tangential force,
Fact on Y-axis
ii). Theoretical Tangential force, Fthe on X-axis Vs Jet co-efficient, Cd on
Y- axis
Expected Graphs: -
Fthe Vs
Cd
Fthe Vs Fact
Fthe

Result: - 1). The value of the actual force is approximately equal to the value of theoretical force.
2). Value of the average Cd =
Table for Observations and Calculations: -
Table:
Sl.
No.
Diameter
of the Jet
in ‘mm’
Type of
Pressure
gauge
reading, in
Kgf/cm2
Force
indicator
reading,
F in Kgf
Fact
in N
Fthe
in N
Cd= Fact
/Fthe

PELTON WHEEL TURBINE
Objective: - To study the characteristic curves of a Pelton wheel turbine at constant
head condition.
Apparatus:-
1. Stop clock,
2. meter scale,
3. Pelton wheel turbine setup,
4. 3-phase power supply.
Theory: - Pelton wheel is a tangential flow high head impulse turbine. Water from the nozzle
strikes the buckets tangentially to the runner wheel. Total energy of the water at the outlet of
the nozzle is in the form of kinetic energy. The pressure at the inlet and outlet of the Turbine
is atmospheric pressure.
1). Head on Turbine in meters of water, H
H = 10P, Where P → is the pressure gauge reading in kg/cm2
2). Flow rate of water through Turbine
Qact = 8/15 x Cd√ 2g tan (θ/2) h5/2
Assuming, Cd = 0.6, g= 9.81m/sec2
, θ= 60 and
h→ Head over the notch in meters
3). Hydraulic input to the Turbine
H.Ppump = wQH/75
Where, w→ 1000kg/m3
;
H→ Head over the Turbine in meters of water.

4). Brake Horse Power (BHP) of Turbine
B.H.P = [2ΠN(F1-F2)r] / 4500
Where, F1 and F2→ Spring balance readings in kgf
r→ Radius of the brake drum in meters (r = 0.15m)
5). Turbine Efficiency
ηtur = (B.H.P / H.Phyd) x 100
6). Unit quantities under unit head
(a). Unit Speed; Nu = N / √ H
(b). Unit Power; Pu = P / H3/2
( c). Unit discharge; Qu = Q / √ H
7). Specific Speed
Ns = N √ P / H5/4
Procedure:-
1. Fill up the sump tank with clean water,
2. Keep the butterfly valve and sphere valve closed,
3. Keep the brake drum loading at minimum (zero),
4. Press the green button of the supply pump starter. The pump picks up full speed and
become operational,
5. Now keep the butterfly valve opening at minimum,
6. Slowly open the sphere valve so that the Turbine runner picks up the speed and attains the
maximum at full opening of the valve,
7. At one particular head on the Turbine note down the speed, head over notch, brake loads
and tabulate the readings
8. Repeat the step no. 7 at different brake loads and note down the readings of speed
9. After the experiment is over keep sphere valve and butterfly valve closed, and switch-OFF
the pump.

Sample Calculation: -
Precautions:
1.The water in the sump tank should be clean.
2. To start and stop supply pump, keep gate valve closed.
3. It is recommended to close sphere valve before starting.
Graphs:
To study constant head characteristic curves of a Pelton wheel Turbine plot
the following graphs,

i). Unit Speed, Nu on X-axis Vs Unit Power, Pu on Y-axis
ii). Unit Speed, Nu on X-axis Vs Unit discharge, Qu on Y-axis
iii). Unit Speed, Nu on X-axis Vs ηoverall on Y-axis
Result: - 1. The constant head characteristic curves have been obtained
2. The maximum efficiency of the Pelton wheel is =
Table for Observations: -
Sl. No.
Runner speed, ‘N’
in RPM
Head over the Turbine,
‘P’ in kgf/cm2
Head over the notch,
‘h’ in meters
Spring balance reading in kgf
F1 F2
Tables for Calculations:
Sl. No.
Net Head, H
in
m
et
er
s
Flow rate , Q
in
m
3
/s
ec
H.Phyd
B.H
.P
ηturbine
Unit
Speed,
Nu
Unit
Power,
Pu
Unit
Discharge
, Qu

Expected Graphs:
Qu Vs Nu
Pu Vs Nu
ηpumpVs Nu
Nu
FRANCIS TURBINE at Constant head condition
Objective: To study the characteristic curves of a Francis turbine at constant head condition.
Apparatus:
1. Stop clock,
2. Meter scale,
3. Francis turbine setup,
4. 3-phase power supply.
Theory: Francis turbine is a reaction turbine operated at medium head. It consists of guide vanes,
runner, scroll casing and draft tube at the exit. Water turns through right angles and guided
through the runner and thus rotating the runner shaft. By varying the guide vane angles, high
efficiency can be maintained over a wide range of operating conditions. After passing
through the turbine, water enters into the collecting tank through draft tube. Loading of the
turbine can be done by brake drum arrangement.
H = 10(P + Pv / 760)

Where P → pressure gauge reading in kg/cm2
Pv→ Vacuum pressure gauge reading in mm of Hg
Q = 2/3 x b x Cd√ 2g h3/2
, b = 0.5m
H.Phyd = wQH/75
;
Q→ Flow rate of water, in m3
/s
B.H.P = [2ΠN(F1-F2)r] / 4500
Procedure:-
1. Keep the butterfly valve and gate valve closed,
become operational,
5. Slowly open the gate valve so that the Turbine runner picks up the speed and attains the

7. Repeat the step no. 6 at different brake loads and note down the readings.
8. After the experiment is over keep sphere valve and butterfly valve closed, and switch-
OFF the pump.
Sample Calculation:
Precautions:
3. It is recommended to close guide vanes before starting.

Graphs:
To study constant head characteristic curves of a Francis Turbine plot the
following graphs,
i). Unit Speed, Nu on X- axis Vs Unit Power, Pu, on Y- axis
ii). Unit Speed, Nu on X- axis Vs Unit discharge, Qu on Y- axis
iii). Unit Speed, Nu on X- axis Vs ηoverall on Y- axis
Result:
1. The constant head characteristic curves have been obtained
2. The maximum efficiency of the Francis Turbine is =
Sl. No.
Runner
speed, ‘N’ in
RPM
Head over the Turbine Head over the
notch, ‘h’ in
meters
Spring balance reading in kgf
‘P’ in kgf/cm2
Pv in mm of Hg F1 F2

Tables for Calculations: -
Sl. No.
Net Head,
H
i
n
m
et
er
s
Flow rate,
Q
in
m3
/se
c
H.Phyd B.H.P
ηtu
rbin
e
Unit
Speed
, Nu
Unit
Pow
er, Pu
Unit
Discha
rge, Qu
Expected Graphs: -
Qu Vs Nu
Pu Vs Nu
ηpumpVs Nu
Nu
04. KAPLAN TURBINE at Constant head condition

Objective: - To study the characteristic curves of a Kaplan turbine at constant head condition.
Apparatus: - stop clock, meter scale, Kaplan turbine setup, 3-phase power supply.
Theory: - Kaplan turbine is a reaction turbine operated at low head. It consists of guide vanes,
through the runner and thus rotating the runner shaft. The runner has four blades, which can
be turned about their own axis so that the angle of inclination may be adjusted while the
turbine is in operation. By varying the guide vane angles, high efficiency can be maintained
over a wide range of operating conditions. After passing through the turbine, water enters
into the collecting tank through draft tube. Loading of the turbine can be done by electrical
switches arrangement. (Electrical loading)
H = 10(P + Pv / 760)
Q = 2.95 x L x h3/2
Where, L → Crest width in meters (L= 0.5m)
H.Phyd = wQH/75
;
/s
4). Electric power as indicated by the energy meter
H.Pelec = (5/1500) x (1000/736) x (60x60)/t = 16.3 / t
Where, t→ it is the time taken for 5 revolutions of the energy meter in sec.
B.H.P = H.Pelec / ηgenerator
Where, ηgenerator→ Generator Efficiency (ηgenerator =75%)

Procedure:- 1. Keep the butterfly valve and gate valve closed,
become operational,
5. Slowly open the gate valve so that the Turbine runner picks up the speed and attains the
6. At one particular head on the Turbine note down the speed, head over notch, wattage of
electrical load bulbs in action, load on generator, energy meter reading and tabulate the
readings
7. Repeat the step no. 6 at different electrical bulb loads and note down the readings.
OFF the pump.

Fig: Sectional arrangement of Kaplan Turbine
Precautions: -1. The water in the sump tank should be clean.

Graphs: -To study constant head characteristic curves of a Francis Turbine plot the following
graphs,
i). Unit Speed, Nu on X- axis Vs Unit Power, Pu, on Y- axis
ii). Unit Speed, Nu on X- axis Vs Unit discharge, Qu on Y- axis
iii). Unit Speed, Nu on X- axis Vs ηoverall on Y- axis
Result: - 1. The constant head characteristic curves have been obtained
2. The maximum efficiency of the Kaplan Turbine is =
Table: 1
Table: 2
Sl. No.
Net Head,
H
i
n
m
et
er
s
Flow rate,
Q
in
m3
/se
c
H.Phyd B.H.P
ηtu
rbin
e
Unit
Speed
, Nu
Unit
Pow
er, Pu
Unit
Discha
rge, Qu
Sl.
No.
Runner
speed, ‘N’
in RPM
Head over the Turbine
Head
over the
notch, ‘h’
in meters
Load on
generator
Wattage
of bulbs
in action
Time taken for 5
rev. of Energy
meter reading, ‘t’
sec.
‘P’ in
kgf/cm2
Pv in mm of
Hg
V in
Volts
I in
Amps

Expected Graphs: -
Qu Vs Nu
Pu Vs Nu
ηpumpVs Nu
Nu
05. MULTISPEED SINGLESTAGE CENTRIFUGAL PUMP TEST RIG
Objective: - To plat the operational characteristic curves of a Multi-speed single stage centrifugal
pump.
Apparatus:-Multi-speed single stage centrifugal pump test set-up, stop clock, steel rule etc.
Theory:-In general a pump may be defined as a mechanical device which when interposed in a
pipe-line converts mechanical energy supplied to it from some internal source in to
hydraulic energy thus resulting in the flow of liquid from the lower potential/head to the
higher potential/head. Multi-speed Single stage centrifugal pump falls in to the category of
Roto-dynamic pumps. In these pumps the liquid is made to rotate in a closed chamber/casing
thus creating the centrifugal action, which gradually builds the pressure gradient towards
outlet, thus resulting in the continuous flow. Hydraulic head developed by the centrifugal
pump is low hence; it is not suitable for high heads as compared to the reciprocating pumps
of same capacity and stage

(i). 1kg/cm2
(ii). Density of water, ‘w’ = 1000 kg/m3
(iii). Energy meter constant = 1500rev/1kWh
(iv). Area of collecting tank, ‘A’ = 0.25m2
2). Discharge rate ‘Q’ in m3
/sec
Q=(A x h) / (1000 x T) = 0.25h/1000T
Where, A→ 0.25m2
, is the area of collecting tank,
h→ Height of water collected in the collecting tank., in mm
T→ Time taken in seconds for water collection in sec.
3). Total head ‘H’ in meters
H = 10 x (Delivery pressure + Vacuum head)
H = 10(P + Pv/760)
Where, P→ Pressure (at stage 4)in kg/cm3
,
Pv→ Vacuum pressure in mm of Hg.
H.Pelec = (10 /1500) x (1000/736) x (60x60)/t = 32.61/
Where, t→ It is the time taken for 10 revolutions of the energy meter in sec.
5). Hydraulic H.P (Delivered by the pump)
H.Ppump = wQH/75
;
H→ Total/ Manometric head in meters.
6). Pump Efficiency
ηpump = H.Ppump / (H.Pelec x ηmotor) x 100
Where, ηmotor→ Assumed as 70%;
ηoverall = H.Ppump/H.Pelec x 100
Procedure:-1. Fill the sump tank with clean water,
2. Keep the delivery and suction valves open,
3. Switch on the mains, so that the mains-ON indicator glows. Now switch-ON the pump,
4. Close the delivery valve slightly so that the delivery pressure is readable.

5. Operate the delivery valve to note down the collecting tank reading against the known
time, keep it open when the readings are not taken. Also note down the delivery pressure
and other readings,
6. Repeat the steps 5 for different openings of delivery valve.
7. After the experiment is over keep all the delivery and suction valves open and switch-
OFF the pump.

Precautions: -1.Do not start the pump if the supply voltage is less than 300V,
3. Accurate readings must be taken to get the good results.
Graphs: -To analysis the operating characteristic curves of a multi stage centrifugal pump, plot the
following graphs,
i). Discharge, ‘Q’ Vs Manometric Head, ‘H’
ii). Discharge, ‘Q’ Vs Input power,
iii). Discharge, ‘Q’ Vs ηoverall
Result: -1. The operational characteristic curves have been obtained
2. The maximum efficiency of the multi speed single stage centrifugal pump is=______
Table: 1
Sl.
No.
Speed,
N in
RPM
Delivery head
pressure, P in
kg/cm2
Suction head
(Vacuu
m), Pv
in mm
of Hg
Time taken for 10
rev. of
Energy
meter
reading,
‘t’ sec.
Height of
water
collected,
h in mm
Disch
arge
time
in sec
Table for Calculations: -
Table: 2
Sl.
No.
Head, H in
meters
Rate of discharge in
m3
/s
H.Pelec (No
load)
H.Ppump
H.Po
verall
ηpump

Expected Graphs: -
H Vs Q
P Vs Q
ηpumpVsQ
Q
06. MULTISTAGE CENTRIFUGAL PUMP TEST RIG.
Objective: - To plat the operational characteristic curves of a multistage centrifugal pump.
Apparatus:-Multistage (4-stage) centrifugal pump test set-up, stop clock, steel rule etc.
higher potential/head.
Multistage centrifugal pump falls in to the category of Roto-dynamic pumps. In these
pumps the liquid is made to rotate in a closed chamber/casing thus creating the centrifugal
action, which gradually builds the pressure gradient towards outlet, thus resulting in the
continuous flow. Hydraulic head developed by the centrifugal pump is low hence; it is not
suitable for high heads as compared to the reciprocating pumps of same capacity and stage.
But if the pump is of multistage construction the pressure gradually builds up in successive
stages all most equally in a stage.
(i). 1kg/cm2
/sec

Q=(A x h) / (1000 x T) = 0.25h / 1000T
Where, A→ Area of collecting tank, 0.25 m2
H = 10(P + Pv/760)
,
H.Pelec = (10/150) x (1000/736) x (60x60)/t = 32.61 x 10/t
H.Ppump = wQH/75
;
6). Pump Efficiency
time, keep it open when the readings are not taken.
6. Note down the pressure at each stage and also other readings,
7. Repeat the experiment for different openings of delivery valve.
OFF the pump.

following graphs,
i). Discharge, ‘Q’ on X-axis Vs Manometric Head, ‘H’ on Y-axis
ii). Discharge, ‘Q’ on X-axis Vs Input power on Y-axis
iii). Discharge, ‘Q’ on X-axis Vs ηoverall on Y-axis

Result: - 1. The operational characteristic curves of centrifugal pump have been obtained
2. The maximum efficiency of the Centrifugal pump is = _________
Table: 1
Sl.
No.
Delivery head pressure,
kg/cm2
Suction
he
ad
(V
ac
uu
m),
Pv
in
m
m
of
Hg
Time taken for 10
rev. of
Energy
meter
reading,
‘t’ sec.
Height of
water
collected,
h in mm
Disch
arge
time
in sec
Stage
-I
Stage-
II
Stage-
III
Stage-IV
( P )

Table: 2
Sl.
No.
Head, H in
meters
m3
/s
H.Pelec (No
load)
H.Ppump ηpump
H.Poveral
l
Expected Graphs: -
H Vs Q
P Vs Q
ηpumpVsQ

Q
07. RECIPROCATING PUMP TEST RIG.
Objective: - To obtain the operational characteristic curves of a Reciprocating pump.
Apparatus:-Reciprocating pump test set-up, stop clock, meter scale etc.
pipe-line converts mechanical energy supplied to it from some internal source in to hydraulic
energy thus resulting in the flow of liquid from the lower potential/head to the higher
potential/head.
Reciprocating pump is a positive displacement pump, which is having a plunger
(piston) moves to and fro in a closed cylinder. The cylinder is connected to suction and
delivery pipes and are lifted with non-return valves to admit the liquid in one direction only.
The non-return valve at the suction side, allows the liquid only to enter the cylinder and the
delivery non-return valve allows the liquid only to escape out from the cylinder to the delivery
pipe.
For more uniform flow, an air vessel is fitted before the suction valve, and after
delivery valve. This contributes for more uniform flow of liquid also saves energy input to the
pump from the prime mover.
(i). 1kg/cm2
H.Pelec = (5/1500) x (1000/736) x (60x60)/t = 16.3 / t
3). Shaft Horse Power as indicated by swinging field dynamometer
H. Pshaft = H.Pelec x ηmotor
Where, ηpump → Motor efficiency, 75%
/sec

Q = (A x h) / (1000 x T) = 0.125h/1000T
where, A→ 0.125m2
H = 10(P + Pv/760)
,
H.Ppump = wQH/75
;
7). Pump Efficiency
ηpump = H.Ppump / H.Pshaft x 100
8). Overall Efficiency
ηoverall = H.Ppump/ H.Pelec x 100
Procedure: - 1. Fill the sump tank with clean water,
3. Set the required speed using the stepped pulley. Switch on the mains, so that the mains-
ON indicator glows.
4. Note down the pressure gauge, vacuum gauge and time for number of revolutions of
energy meter disc at full opening of delivery and suction valves,
5. Operate the butterfly valve to note down the collecting tank reading against the known
6. Repeat the experiment for different openings of the delivery valve.
OFF the pump.

Fig Schematic
diagram of
Reciprocating pump
2. Initially the suction and delivery valves should be kept fully open,
Graphs: -To study the operating characteristic curves of a Reciprocating pump, plot the following
graphs,
i). Total head, ‘H’ on X-axis Vs Discharge, ‘Q’ on Y-axis
ii). Total head, ‘H’ on X-axis Vs Shaft Input power, on Y-axis
iii). Total head, ‘H’ on X-axis Vs ηpump on Y-axis
Result: - 1. The operational characteristic curves of Reciprocating pump have been obtained

2. The maximum efficiency of the Reciprocating pump is =
Table: 1
Sl.
No.
Pump
Speed,
‘N’ in
RPM
Delivery
head
pressure, P in
kg/cm2
Suction head
(Vacuum), Pv
in mm of Hg
Time taken for 5
rev. of Energy
in sec.
Height of
water
collected,
‘h’ in mm
Discharge
time. ‘T’ in
sec
Table: 2
Sl.
No.
Pump
Speed, ‘N’
in RPM
Total
Head, H in
meters
Rate of
discha
rge,
‘Q’ in
m3
/sec
H.Ppum
H.Pshaft
H.
Pel
ec
ηp
um
p
ηover
all

Expected Graphs: -
Q Vs H
P Vs H
ηpumpVsH
H
08. CALIBRATION OF VENTURI METER
Objective: - - To calibrate venturimeter and to determine the co-efficient of discharge of the given
venturimeter.
Apparatus: -Venturi meter fixed in a pipeline, manometer, collecting tank, stop watch.
Theory: -Venturi meter is a device which is used to measuring the rate of flow of fluid through a
pipeline. The basic principle on which a Venturi meter works is that by reducing the cross
sectional area of the flow passage, a pressure difference is created between the inlet and
throat and the measurement of pressure difference enables the determination of the
discharge through the pipe.

A Venturi meter consists of i). An inlet section followed by a convergent cone
section, ii). A cylindrical throat and iii). A gradually divergent cone section. At the inlet
section and at the throat of the Venturi meter pressure taps are provided through the
pressure rings.
1. Basic data contents
(i). Area of the collecting tank, 0.12 m2
(ii). Diameter of the pipeline, d1 = 25mm,
(iii). Diameter of the throat, d2 = 12.5mm,
2. Theoretical discharge through the pipe line
QThel = A1A2√ 2gH) / √ (A1
2
– A2
2
)
Where, H→ Difference in manometer limb levels, in meters of water;
A1→ Cross sectional area of the inlet section of the Venturi, in m2
;
A2→ Cross sectional area of the Outlet section of the Venturi, in m2
;
g→ Acceleration due to gravity in m/sec2
3. Actual discharge through Venturi meter
Qact= A Lr / T
Where, A→ Area of the collecting tank in meters;
Lr→ Height of water collected in the collecting tank., in meters
T→ Time taken in seconds for water collection in sec
3. Co efficient of discharge, Cd
Cd = Qact / QThe
4. To determine k and n (from calibration curve)
Qact = k (H) n
where k is a const and k = Cd A1 A2√ 2g) / √ (A1
2
– A2
2
)
log (Qact)= n log (H) + log (k) ( i.e y = mx +c form)
Procedure: -1. Switch on the pump and open the delivery valve
2. Open the corresponding ball valve of the venturimeter pipes
3. Note down the differential head reading in the manometer (expel if any air is trapped by
opening the drain cocks provided with the manometer.)

4. From the known pressure head difference, the ideal discharge is calculated using the
basic formula. The actual discharge is determined by finding time taken for specific
volume of water collection in the collecting tank.
5. Repeat the steps 2 to 4 for different flow rates and note down the readings.
6. After the experiment is over keep supply valve closed, and switch-OFF the pump.
2. The water in the tank should be clean.
3. See that there should be no water leakage from the Venturi meter connections
Graphs: -To find, co efficient of discharge through graph plot the following graphs
1. Theoretical discharge, Qthe on X-axis Vs Actual discharge, Qact on Y-axis
2. log (Qact) on Y-axis Vs log (H)on X-axis
Result: - 1).Cd from graph, Qthe Vs Qact = _______

2). Cd from graph, log (Qact) Vs log(H)= _______
3). Arithmetic mean value of the Cd = _________
Table for observations: -
Table: 1
Sl.
No.
Difference in manometer
Limb levels, ’h’ in cm
Rise of water level in collecting
tank
Time taken for
rise Lr, ’T’ in sec
h 1 h 2 h = h 1- h 2 From To Rise Lr , in mm
Table for calculations : -
Table: 2
Sl.
N
o
Qact= ALr/
(1000T) in
m3
/ sec
Mean
Velocity,
V=Qact/a in
m/sec
Head difference,
in m of
water ,
H =
0.126 x
h
log
(H)
QThe = A1A2√
2gH)/ √ (A1
2
–
A2
2
)
in m3
/ sec
log
(Qact)
Co efficient
of discharge
Cd = Qact /
QThe
Expected Graphs: -
log (Qact) n=Δy/Δx Qact
Cd = slope

log (k)
log (H) Qthe
09. CALIBRATION OF ORIFICE METER
Objective: - To calibrate Orifice meter and to determine the co-efficient of discharge of the given
Orifice meter.
Apparatus: - Orifice meter fixed in a pipeline, manometer, collecting tank, and stopwatch.
Theory: - Orifice meter is a device, which is used to measuring the rate of flow of fluid through a
pipeline. The basic principle on which a Orifice meter works is that by reducing the cross
vena-contracta and the measurement of pressure difference enables the determination of
the discharge through the pipe.
An Orifice meter consists of an inlet section followed by a suddenly reduced cross
section in form of orifice. At the inlet section and at the vena-contracta of the Orifice
meter pressure taps are provided through the pressure rings.
(i). Area of the collecting tank, 0.12 m2
(ii). Diameter of the inlet pipeline, d1 = 25mm,
(iii). Diameter of the orifice, d2 = 12.5mm,
QThel = A1A2√ 2gH) / √ (A1
2
– A2
2
)
A1→ Cross sectional area of the inlet section of the Orifice, in m2
;
A2→ Cross sectional area of the Orifice, in m2
;
3. Actual discharge through Orifice meter
Qact= A Lr / T

Cd = Qact / QThe
Qact = k (H) n
2
– A2
2
)
7. Open the corresponding ball valve of the Orifice meter pipe

1) Theoretical discharge, Qthe on X-axis Vs Actual discharge, Qact on Y-axis
2) log (Qact) on Y-axis Vs log (H)on X-axis
Table: 1
Sl.
No.
Difference in manometer. Limb levels,
’h’ in cm
Rise of water level in collecting tank Time taken
for rise Lr, ’T’
in sec

Table: 2
Sl.
N
o
Qact= ALr/
(1000T) in
m3
/ sec
Mean
Velocity,
V=Qact/a in
m/sec
Head difference,
in m of
water ,
H =
0.126 x
h
log
(H)
QThe = A1A2√
2gH)/ √ (A1
2
–
A2
2
)
in m3
/ sec
log
(Qact)
Co efficient
of discharge
Cd = Qact /
QThe
Expected Graphs: -
Cd = slope
log (k)
log (H) Qthe
10. FRICTION FACTOR OF A PIPE LINE
Objective: - To determine the co efficient of friction for a given pipeline.

Apparatus: -One given length of pipeline, Manometer, collecting tank and stopwatch etc.
Theory: - When a fluid flows through a pipe, certain resistance is offered to the flowing fluid,
which result in causing of loss of energy. The various energy losses in pipe may be classified
as a). Major losses b). Minor losses. The major loss of energy as a fluid flows through a pipe,
is caused by friction of the pipe walls. The loss of energy due to friction is classified as a
major loss because in case of long pipelines it is usually much more than the loss of energy
incurred by other causes.
(i). Dimensions of the collecting tank, length = 600mm and width = 600mm
(iii). Length of the pipeline, L = 3450mm,
2. Basic equation
Head loss due to flow over a length L, hf = fLV2
/ (2gD)
Where,
D Diameter of pipe in cm, V Mean Velocity in cm/s
f Friction factor of pipe and k f L / (2gD)
Procedure:
1. Switch on the pump and open the delivery valve
2. Open the corresponding ball valve of the pipe
3. Note down the differential head reading in the manometer (expel if any air is trapped
by opening the drain cocks provided with the manometer).
4. The actual discharge is determined by finding time taken for specific volume of water
collection in the collecting tank.
Precautions: -1). Do not start the pump if the supply voltage is less than rating voltage.
2). The water in the tank should be clean.
Graphs: - a). A graph between V2
on X-axis and hf on Y-axis is drawn.
b). A graph between log10V on X-axis and log10hf on Y-axis is plotted.

Result: - 1). Friction factor from V2
Vs hf curve = _____________________
2). Friction factor from log10V Vs log10 hf curve = ______________
3). Arithmetic mean value of the friction factor = ______________
Table: 1
Sl.
No.
tank
Time taken for
Table: 2
Sl.
No
Actual discharge,
Qact= ALr/(1000T) in
m3
/sec
Mean Velocity,
V=Qact/a in
m/sec
Head difference,
in m of
water hf =
0.136 x h
C = (2gD) /
L
Friction
factor,
f = C hf / V2
Expected Graphs: -
log10 hf n=Δy/Δx hf

log10 (k)
log10 V V2
11. BERNOULLI’S EXPERIMENT
Objective: - To verify the validity of the Bernoulli’s equation for an incompressible flow.
Apparatus: - Duct of variable cross section with supply and discharge chambers, collecting tank
and stop watch etc.
Theory: - P/w + V2
/ (2g) + Z= const. is called Bernoulli’s equation. Each term in this equation
represents the energy possessed by the fluid. Each term in the equation represents the energy
per unit weight of the flowing fluid. The term ‘P/w’ is known as pressure head or static head;
‘V2
/ (2g)’ is known as velocity head or kinetic head and ‘Z’ is known as potential head or
datum head. The sum of P/w, V2
/ (2g) & Z is known as ‘Total head’ or the total energy per
unit weight of the fluid. The Bernoulli’s equation thus states that in a steady, irrotational flow
of an incompressible fluid the total energy at any point is constant. In other words, if the
Bernoulli’s equation is applied between any two points in a steady irrotational flow of an
incompressible fluid then, we get
P1/w + V1
2
/ (2g) + Z1 = P2/w + V2
2
/ (2g) + Z2
Where the different terms with subscripts 1 and 2 correspond to the two points considered.
1) Basic data
Cross sectional area of the pipe at different duct points, in mm2
a1= 491 a2= 377, a3= 245, a4= 153, a5= 123
a6= 153, a7= 202, a8= 279, a9= 369, a10= 491
2) Basic equation
Total Head, H = P/w + V2
/ (2g) + Z
Where, P/w Pressure head, V2
/ (2g) Pressure head
Z Elevation head above any arbitrary datum.
Procedure: - 1). The inflow valve is opened so that water flows into the supply chamber and heads
up.
2). Flow through the duct is controlled by the outlet valve located at down stream.

3). At steady flow, all the readings should be noted down simultaneously.
4). The discharge is measured in the collecting tank.
5). Repeat the steps no. 3 and 4 for different flow patterns
6). After the experiment is over keep supply valve closed, and switch-OFF the pump.
Precautions: -1.Do not start the pump if the supply voltage is less than the rating voltage.
Graphs: -Duct points on X-axis Vs Pressure head, velocity head, elevation head and Total head on
Y-axis and on the same graph.
Result: - Bernoulli’s equation is verified by conducting an experiment.
Table for calculations Table-1
Sl.
No.
Height of water
collected ‘h’ in
mm
Time taken in
seconds for
water
collection,
‘T’ in sec
Piezo tubes reading at duct points in mm of water
1 2 3 4 5 6 7 8 9 10
1
2
3
Sl.
No
Duct
point
Actual discharge
Qact = Ah/
(1000T)
Velocity,
Vi=Qact/ai
Where, i =1 to
10
V2
/ (2g) P/w Z H

I
II
1
2
3
4
5
6
7
8
9
10
1
2
3
4
5
6
7
8
9
10

12.PELTON WHEEL TURBINE at Constant speed
Objective: - To study the characteristic curves of a Pelton wheel turbine at constant speed condition.
Apparatus:- stop clock, meter scale, Pelton wheel turbine setup, 3-phase power supply.
Theory: - Pelton wheel is a tangential flow high head impulse turbine. Water from the nozzle strikes
the buckets tangentially to the runner wheel. Total energy of the water at the outlet of the
nozzle is in the form of kinetic energy. The pressure at the inlet and outlet of the Turbine is
atmospheric pressure.
H = 10P, Where P→is the pressure guage reading in kg/cm2
Qact = 8/15 x Cd√ 2g tan (θ/2) h5/2
, θ= 60
H.Ppump = wQH/75
; H→ Head over the Turbine in meters of water.
B.H.P = [2ΠN(F1-F2)r] / 4500
6). Percentage of Full Load
% Full load = (Part load B.H.P / Maximum load B.H.P) x 100
Procedure: -1Keep the butterfly valve and sphere valve closed,
become operational,

OFF the pump.

Graphs: -To study constant head characteristic curves of a Pelton wheel Turbine plot the following
graphs,
i). Discharge, Q on X- axis Vs ηturbine on Y- axis
ii). Discharge, Q on X- axis Vs B.H.P on Y- axis
iii) % of Full load on X- axis Vs ηoverall on Y- axis
Result: - 1. The constant speed characteristic curves of Pelton wheel have been obtained
2. The maximum efficiency of the pelton wheel turbine is=______
Table: 1
Sl.
No.
Runner speed,
‘N’ in RPM
Head over the
Turbine,
‘P’ in
kgf/cm2
Head over the
notch, ‘h’ in
meters
Spring balance reading in
kgf
F1 F2
Table: 2
Sl.
No.
Net Head, H
in
mete
rs
Flow rate, Q in
m3
/sec
H.Phyd B.H.P ηturbine
% Of
Full load

Expected Graphs: -
% Full load Vs Q
ηturbine Vs Q
BHP Vs Q
Q
13. KAPLAN TURBINE at Constant speed condition
Objective: - To study the characteristic curves of a Kaplan turbine at constant speed condition.
Apparatus: - stop clock, meter scale, Francis turbine setup, 3-phase power supply.
Theory: - Kaplan turbine is a reaction turbine operated at low head. It consists of guide vanes,
through the runner and thus rotating the runner shaft. The runner has four blades, which can
be turned about their own axis so that the angle of inclination may be adjusted while the
turbine is in operation. By varying the guide vane angles, high efficiency can be maintained
over a wide range of operating conditions. After passing through the turbine, water enters
into the collecting tank through draft tube. Loading of the turbine can be done by electrical
switches arrangement. (Electrical loading)
H = 10(P + Pv / 760)

Q = 2.95 x L x h3/2
Where, L → Crest width in meters (L= 0.5m)
H.Phyd = wQH/75
;
/s
H.Pelec = (5/1500) x (1000/736) x (60x60)/t = 16.3 / t
B.H.P = H.Pelec / ηgenerator
Where, ηgenerator→ Generator Efficiency (ηgenerator =75%)
ηturbine = (B.H.P / H.Phyd) x 100
7). Percentage of full load
Procedure: - 1. Keep the brake drum loading at minimum (zero),
become operational,
3. Slowly open the gate valve so that the Turbine runner picks up the speed and get the
required speed at any particular guide vane angle.
4. At one particular head on the Turbine note down the speed, head over notch, wattage of
electrical load bulbs in action, load on generator, energy meter reading and tabulate the
readings
5. Repeat the step no. 4 at different electrical bulb loads by keeping the rotor pitch constant
and changing the gate position and note down the readings.
6. After the experiment is over keep gate valve closed, and switch-OFF the pump.

Fig: Sectional arrangement of Kaplan Turbine
Graphs: -To study constant speed characteristic curves of a Kaplan Turbine plot the following
graphs,
Result: - 1. The constant speed characteristic curves of Kaplan turbine have been obtained
2. The maximum efficiency of the Kaplan turbine is=______
Sl.
No.
Runner
speed, ‘N’
in RPM
Head
over the
notch, ‘h’
in meters
Load on
generator
Wattage
of bulbs
in action
Time taken for 5
rev. of Energy
sec.
‘P’ in
kgf/cm2
Pv in mm of
Hg
V in
Volts
I in
Amps

Table: 2
Sl.
No.
Net Head, H
in
mete
rs
Flow rate, Q
in
m3
/se
c
% of Full
load
Expected Graphs: -
% Full load Vs Q
ηturbine Vs Q
BHP Vs Q
Q
14. FRANCIS TURBINE at Constant speed condition
Objective: - To study the characteristic curves of a Francis turbine at constant speed condition.
Apparatus: - stop clock, meter scale, Francis turbine setup, 3-phase power supply.
Theory: - Francis turbine is a reaction turbine operated at medium head. It consists of guide vanes,
through the runner and thus rotating the runner shaft. By varying the guide vane angles, high
efficiency can be maintained over a wide range of operating conditions. After passing

through the turbine, water enters into the collecting tank through draft tube. Loading of the
turbine can be done by brake drum arrangement.
H = 10(P + Pv / 760)
Q = 2/3 x b x Cd√ 2g h3/2
, b = 0.5m
H.Phyd = wQH/75
;
/s
B.H.P = [2ΠN(F1-F2)r] / 4500
6). Percentage of full load
Procedure: - 1. Keep the butterfly valve and gate valve closed,
become operational,
4. Slowly open the gate valve so that the Turbine runner picks up the speed and get the
required speed at any particular guide vane angle.

5. At one particular speed of the Turbine note down the head over the turbine, head over
notch, brake loads and tabulate the readings
6. Repeat the step no. 5 at different brake loads by keeping gate valve position as constant and
changing the guide vanes position.
OFF the pump.
Fig: Sectional arrangement of Francis Turbine
Graphs: -To study constant speed characteristic curves of a Francis Turbine plot the following
graphs,
Result: - 1. The constant speed characteristic curves of Francis Turbine have been obtained
2. The maximum efficiency of the Francis turbine is=______
Table: 1
Sl.
No.
kgf

Runner
speed, ‘N’
in RPM
Head over the
notch, ‘h’ in
meters
‘P’ in
kgf
/cm
2
Pv in mm of
Hg
F1 F2
Table: 2
Sl.
No.
Net Head, H
in
mete
rs
Flow rate, Q
in
m3
/se
c
% of Full
load
Expected Graphs: -
% Full load Vs Q
ηturbine Vs Q
BHP Vs Q

Q
15. RECIPROCATING PUMP TEST RIG. Multispeed condition
Objective: - To conduct performance test on a Reciprocating pump at variable speed condition
Apparatus: -Reciprocating pump test set-up, stop clock, meter scale etc.
potential/head.
pipe.
(i). 1kg/cm2

H.Pelec = (5/1500) x (1000/736) x (60x60)/t = 16.3 / t
H. Pshaft = 2Π NT / 4500 = 2Π N x 0.1 x F /4500 = 0.00014 N F
Where, F→ Spring balance readings in kgf
r→ Radius of the swing field arm in meters (r = 0.1m)
N→ The RPM of the DC motor
/sec
Q=(A x h) / (1000 x T) = 0.125h/1000T
where, A→ 0.125m2
H = 10(P + Pv/760)
, Pv→ Vacuum pressure in mm of Hg.
H.Ppump = wQH/75
; H→ Total/ Manometric head in meters.
7). Pump Efficiency
Procedure: - 1). Fill the sump tank with clean water,
3. Switch on the mains, so that the mains-ON indicator glows. Now switch-ON the
controller,
4. Ste the desired speed using stepped pulley and belt arrangement
energy meter disc at a particular load condition (i.e Close the delivery valve partially
until we get a particular delivery pressure)

7. Repeat the steps 5 & 6 for different speeds of the pump by keeping load as constant.
OFF the pump.
graphs,
i). Rotational speed of the pump, ‘N’ on X-axis Vs Discharge, ‘Q’ on Y-axis
ii). Rotational speed of the pump, ‘N’ on X-axis Vs Shaft Input power, on Y-axis
iii). Rotational speed of the pump, ‘N’ on X-axis Vs ηpump on Y-axis
Result: - 1. The performance test on a Reciprocating pump has been conducted
2. The maximum efficiency of the Reciprocating pump is =
Table: 1
Sl.
No.
Pump
Speed,
‘N’ in
RPM
Delivery
head
pressure, P in
kg/cm2
Suction head
(Vacuum), Pv
in mm of Hg
Time taken for 5
rev. of Energy
in sec.
Height of
water
collected,
‘h’ in mm
Discharge
time. ‘T’ in
sec

Table: 2
Sl. No.
Total Head,
H in meters
Rate of discharge,
‘Q’ in
m3
/sec
H.Ppump H.Pshaft
H.Pe
lec
ηpu
mp
ηoverall
Expected Graphs: -
Q Vs N
P Vs N
ηpumpVs N
N

CALIBRATION OF VENTURI METER
Aim: - To calibrate venturimeter and to determine the co-efficient of discharge of the given
venturimeter.
Apparatus: -Venturi meter fixed in a pipeline, manometer, collecting tank, stop watch.
Theory: -Venturi meter is a device which is used to measuring the rate of flow of fluid through a
pipeline. The basic principle on which a Venturi meter works is that by reducing the cross
throat and the measurement of pressure difference enables the determination of the
discharge through the pipe.
A Venturi meter consists of i). An inlet section followed by a convergent cone
section, ii). A cylindrical throat and iii). A gradually divergent cone section. At the inlet
section and at the throat of the Venturi meter pressure taps are provided through the
pressure rings.
(iii). Diameter of the throat, d2 = 25mm,
QThel = A1A2√ 2gH) / √ (A1
2
– A2
2
)
A1→ Cross sectional area of the inlet section of the Venturi, in m2
;
2→ Cross sectional area of the Outlet section of the Venturi, in m2
;
6. Actual discharge through Venturi meter
Qact= A Lr / T
Cd = Qact / QThe

Qact = k (H) n
2
– A2
2
)
12. Open the corresponding ball valve of the venturimeter pipes

Table: 1
Sl.
No.
tank
Time taken for
Table: 2
Sl.
N
o
Qact= ALr/
(1000T) in
m3
/ sec
Mean
Velocity,
V=Qact/a in
m/sec
Head
diff
ere
nce
, in
m
of
wa
ter
H = 0.136 x
h
log
(H)
QThe = A1A2√
2gH)/ √ (A1
2
–
A2
2
)
in m3
/ sec
log
(Qact)
Co efficient
of discharge
Cd = Qact /
QThe

Expected Graphs: -
Cd = slope
log (k)
log (H) Qthe

Aim: - To calibrate Orifice meter and to determine the co-efficient of discharge of the given Orifice
meter.
Apparatus: - Orifice meter fixed in a pipeline, manometer, collecting tank, stop watch.
Theory: - Orifice meter is a device which is used to measuring the rate of flow of fluid through a
pipeline. The basic principle on which a Orifice meter works is that by reducing the cross
vena-contracta and the measurement of pressure difference enables the determination of
the discharge through the pipe.
An Orifice meter consists of an inlet section followed by a suddenly reduced cross
section in form of orifice. At the inlet section and at the vena-contracta of the Orifice
meter pressure taps are provided through the pressure rings.
(ii). Diameter of the inlet pipeline, d1 = 50mm,
(iii). Diameter of the orifice, d2 = 25mm,
QThel = A1A2√ 2gH) / √ (A1
2
– A2
2
)
A1→ Cross sectional area of the inlet section of the Orifice, in m2
;
A2→ Cross sectional area of the Orifice, in m2
;
9. Actual discharge through Orifice meter
Qact= A Lr / T
Cd = Qact / QThe
Qact = k (H) n
2
– A2
2
)

17. Open the corresponding ball valve of the Orifice meter pipe

BERNOULLI’S EXPERIMENT
Objective: - To verify the validity of the Bernoulli’s equation for an incompressible flow.
Apparatus: - Duct of variable cross section with supply and discharge chambers, collecting tank
and stop watch etc.

Theory: - P/w + V2
/ (2g) + Z= const. is called Bernoulli’s equation. Each term in this equation
represents the energy possessed by the fluid. Each term in the equation represents the energy
per unit weight of the flowing fluid. The term ‘P/w’ is known as pressure head or static head;
‘V2
/ (2g)’ is known as velocity head or kinetic head and ‘Z’ is known as potential head or
datum head. The sum of P/w, V2
/ (2g) & Z is known as ‘Total head’ or the total energy per
unit weight of the fluid. The Bernoulli’s equation thus states that in a steady, irrotational flow
of an incompressible fluid the total energy at any point is constant. In other words, if the
Bernoulli’s equation is applied between any two points in a steady irrotational flow of an
incompressible fluid then, we get
P1/w + V1
2
/ (2g) + Z1 = P2/w + V2
2
/ (2g) + Z2
Where the different terms with subscripts 1 and 2 correspond to the two points considered.
3) Basic data
Cross sectional area of the pipe at different duct points, in mm2
a1= 490.87, a2= 376.68, a3= 260.16, a4= 162.86, a5= 128.68,
a6= 153.94, a7= 213.82, a8= 292.55, a9= 376.69, a10= 490.87.
4) Basic equation
Total Head, H = P/w + V2
/ (2g) + Z
Where, P/w Pressure head, V2
/ (2g) Pressure head
Z Elevation head above any arbitrary datum.
Procedure: - 1). The inflow valve is opened so that water flows into the supply chamber and heads
up.
2). Flow through the duct is controlled by the outlet valve located at down stream.
3). At steady flow, all the readings should be noted down simultaneously.
4). The discharge is measured in the collecting tank.
5). Repeat the steps no. 3 and 4 for different flow patterns
6). After the experiment is over keep supply valve closed, and switch-OFF the pump.
Precautions: -1.Do not start the pump if the supply voltage is less than the rating voltage.

Graphs: -Duct points on X-axis Vs Pressure head, velocity head, elevation head and Total head on
Y-axis and on the same graph.
Result: -
Sl.
No.
Height of water
collected ‘h’ in
mm
Time taken in
seconds for
water
collection,
‘T’ in sec
Piezo tubes reading at duct points in mm of water
1 2 3 4 5 6 7 8 9 10
1
2
3

Sl.
No
Duct
point
Actual discharge
Qact = Ah/
(1000T)
Velocity,
Vi=Qact/ai
Where, i =1 to
10
V2
/ (2g) P/w Z H

I
II
III
1
2
3
4
5
6
7
8
9
10
1
2
3
4
5
6
7
8
9
10
1
2
3
4
5
6
7
8
9
10

PELTON WHEEL TURBINE
Objective: - To study the characteristic curves of a Pelton wheel turbine at constant head condition.
Apparatus:- stop clock, meter scale, Pelton wheel turbine setup, 3-phase power supply.
Theory: - Pelton wheel is a tangential flow high head impulse turbine. Water from the nozzle strikes
the buckets tangentially to the runner wheel. Total energy of the water at the outlet of the
nozzle is in the form of kinetic energy. The pressure at the inlet and outlet of the Turbine is
atmospheric pressure.
H = 10P
Where P→is the pressure guage reading in kg/cm2
Qact = 8/15 x Cd√ 2g tan (θ/2) h5/2
, θ= 60
H.Ppump = wQH/75
;

B.H.P = [2ΠN(F1-F2)r] / 4500
7). Specific Speed
Ns = N √ P / H5/4
Procedure:-1. Fill up the sump tank with clean water,
2. Keep the butterfly valve and sphere valve closed,
become operational,
OFF the pump.

Graphs: -To study constant head characteristic curves of a Pelton wheel Turbine plot the following
graphs,
i). Unit Speed, Nu Vs Unit Power, Pu,
ii). Unit Speed, Nu Vs Unit discharge, Qu
iii). Unit Speed, Nu Vs ηoverall
Result: -
Table: 1
Sl.
No.
Runner speed,
‘N’ in RPM
Head over the
Turbine,
‘P’ in
kgf/cm2
Head over the
notch, ‘h’ in
meters
kgf
F1 F2
Table: 2
Sl.
No.
Speed, N in
RPM
Net Head, H in
meters
Flow rate , Q in
m3
/sec
H.Phyd B.
H.
P
ηturbi
ne

Table: 3
Sl.
No.
Net Head, H in
m
Unit Speed,
Nu
Unit Power,
Pu
Unit Discharge,
Qu
Specific
speed, Ns
ηturbi
ne
Expected Graphs: -
Qu Vs Nu
Pu Vs Nu
ηpumpVs Nu
Nu
RECIPROCATING PUMP TEST RIG.
Objective: - To obtain the operational characteristic curves of a Reciprocating pump.
Apparatus:-Reciprocating pump test set-up, stop clock, meter scale etc.
potential/head.

pipe.
(i). 1kg/cm2
H.Pelec = (5/1500) x (1000/736) x (60x60)/t = 16.3 / t
H. Pshaft = 2Π NT / 4500 = 2Π N x 0.1 x F /4500 = 0.00014 N F
Where, F→ Spring balance readings in kgf
r→ Radius of the swing field arm in meters (r = 0.1m)
N→ The RPM of the DC motor
/sec
Q=(A x h) / (1000 x T) = 0.125h/1000T
where, A→ 0.125m2
H = 10(P + Pv/760)
,
H.Ppump = wQH/75

;
7). Pump Efficiency
Procedure: - 1). Fill the sump tank with clean water,
3. Keep the speed control knob at zero,
3. Switch on the mains, so that the mains-ON indicator glows. Now switch-ON the
controller,
4. Ste the desired speed using the controller knob and digital RPM indicator
energy meter disc at full opening of delivery and suction valves,
7. Repeat the experiment for different openings of the delivery valve.
OFF the pump.
graphs,

i). Total head, ‘H’ on X-axis Vs Discharge, ‘Q’ on Y-axis
ii). Total head, ‘H’ on X-axis Vs Shaft Input power, on Y-axis
iii). Total head, ‘H’ on X-axis Vs ηpump on Y-axis
Result: -
Table: 1
Sl.
No.
Pump
Speed,
‘N’ in
RPM
Delivery
head
pressure, P
in kg/cm2
Suction
head
(Vacuum),
Pv in mm of
Hg
Swinging field
spring balance
reading , ‘F’ in
kgf
Time taken for 5
rev. of Energy
meter reading,
‘t’ in sec.
Height of
water
collected,
‘h’ in
mm
Dis
cha
rge
tim
e.
‘T’
in
sec

Table: 2
Sl.
No.
Pump
Speed, ‘N’
in RPM
Total
Head, H in
meters
Rate of
discha
rge,
‘Q’ in
m3
/sec
H.Ppu H.Pshaft H.
Pel
ec
ηp
um
p
ηover
all
Expected Graphs: -
Q Vs H
P Vs H

ηpumpVsH
H
MULTISTAGE CENTRIFUGAL PUMP TEST RIG.
Objective: - To plat the operational characteristic curves of a multistage centrifugal pump.
Apparatus:-Multistage (4-stage) centrifugal pump test set-up, stop clock, steel rule etc.
higher potential/head.
Multistage centrifugal pump falls in to the category of Roto-dynamic pumps. In these
pumps the liquid is made to rotate in a closed chamber/casing thus creating the centrifugal
action, which gradually builds the pressure gradient towards outlet, thus resulting in the
continuous flow. Hydraulic head developed by the centrifugal pump is low hence; it is not
suitable for high heads as compared to the reciprocating pumps of same capacity and stage.
But if the pump is of multistage construction the pressure gradually builds up in successive
stages all most equally in a stage.
(i). 1kg/cm2
/sec
Q=(A x h) / (1000 x T) = 0.25h/1000T
Where, A→ 0.25m2

H = 10(P + Pv/760)
,
H.Pelec = (10/150) x (1000/736) x (60x60)/t = 32.61 x 10/t
H.Ppump = wQH/75
;
6). Pump Efficiency
6. Note down the pressure at each stage and also other readings,
7. Repeat the experiment for different openings of delivery valve.
OFF the pump.

following graphs,
i). Discharge, ‘Q’ Vs Manometric Head, ‘H’
ii). Discharge, ‘Q’ Vs Input power,
iii). Discharge, ‘Q’ Vs ηoverall
Result: -
Table: 1
Sl.
No.
Delivery head pressure, P in
kg/cm2
Suction
he
ad
(V
ac
uu
m),
Pv
in
m
m
of
Hg
Time taken for
10 rev.
of
Energy
meter
reading,
‘t’ sec.
Height of
water
collected,
h in mm
Disch
arge
time
in sec
Stage
-I
Stage-
II
Stage-
III
Stage-IV

Table: 2
Sl.
No.
Head, H in
meters
m3
/s
H.Pelec (No
load)
H.Ppump ηpump H.Poveral
l
Expected Graphs: -
H Vs Q
P Vs Q
ηpumpVsQ
Q

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