1
KIT-KALAIGNARKARUNANIDHI
INSTITUTE OF TECHNOLOGY
Kannampalayam Post, Coimbatore-641402
DEPARTMENT OF MECHANICAL
ENGINEERING
CE6461-FLUID MECHANICS AND
MACHINERY
LABORATORY MANUAL
Prepared by,
C.RAMESH, AP/MECH
M.VIJAYAKUMAR, AP/MECH &
B.GOKULNATH, AP/MECH

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KIT-KALAIGNAR KARUNANIDHI INSTITUTE OF
TECHNOLOGY
COIMBATORE-641402
DEPARTMENT OF MECHANICAL ENGINEERING
CE6461-FLUID MECHANICS AND MACHINERY LABORATORY
LIST OF EXPERIMENTS
1. Determination of the Coefficient of discharge of
given
Orificemeter.
2. Determination of the Coefficient of discharge of
given
Venturimeter.
3. Calculation of the rate of flow using Rotameter.
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.

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LABARATORY CLASSES - INSTRUCTIONS TO STUDENTS
1. Students must attend the lab classes with ID cards and
in the prescribed uniform.
2. Boys-shirts tucked in and wearing closed leather shoes.
Girls’ students with cut shoes, overcoat, and plait incite
the coat. Girls’ students should not wear loose garments.
3. Students must check if the components, instruments and
machinery are in working condition before setting up the
experiment.
4. Power supply to the experimental set up/ equipment/
machine must be switched on only after the faculty checks
and gives approval for doing the experiment. Students must
start to the experiment. Students must start doing the
experiments only after getting permissions from the
faculty.
5. Any damage to any of the equipment/instrument/machine
caused due to carelessness, the cost will be fully
recovered from the individual (or) group of students.
6. Students may contact the lab in charge immediately for
any unexpected incidents and emergency.
7. The apparatus used for the experiments must be cleaned
and returned to the technicians, safely without any
damage.
8. Make sure, while leaving the lab after the stipulated
time, that all the power connections are switched off.

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CE6461-FLUID MECHANICS AND MACHINERY LABORATORY-SYLLABUS
OBJECTIVES:
Upon Completion of this subject, the students can able to have hands
on experience in flow measurements using different devices and also
perform calculation related to losses in pipes and also perform
characteristic study of pumps, turbines etc.,
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.
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.
TOTAL: 45 PERIODS
OUTCOMES:
1. Ability to use the measurement equipments for flow measurement
2. Ability to do performance trust on different fluid machinery
LIST OF EQUIPMENT FOR A BATCH OF 30 STUDENTS
S. NO. NAME OF THE EQUIPMENT Qty.
1 Orifice meter setup 1
2 Venturi meter setup 1
3 Rotameter setup 1
4 Pipe Flow analysis setup 1
5
Centrifugal pump/submergible pump
setup
1
6 Reciprocating pump setup 1
7 Gear pump setup 1
8 Pelton wheel setup 1
9 Francis turbine setup 1
10 Kaplan turbine setup 1

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SCHEMATIC DIAGRAM OF ORIFICEMETER

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DETERMINATION OF THE COEFFICIENT OF DISCHARGE OF GIVEN ORIFICE METER
EX. NO. : DATE :
AIM :
To determine the co-efficient discharge through orifice meter.
APPARATUS REQUIRED:
1. Orifice meter
2. Differential U tube
3. Collecting tank
4. Stop watch
5. Meter scale
FORMULA TO BE USED:
1. Actual Discharge 𝐐 𝐚𝐜𝐭 =
𝐀 ×𝐇
𝐭
m3
/sec
2. Theoretical Discharge 𝐐𝐭𝐡 =
𝐚 𝟏 𝐚 𝟐 𝟐𝐠𝐡
𝐚 𝟏
𝟐−𝐚 𝟐
𝟐
m3
/sec
3. Co efficient of Discharge 𝐂 𝐝 =
𝐐 𝐚𝐜𝐭
𝐐 𝐭𝐡
Where,
A - Area of the Collecting tank in m2
H - Height of collected water in tank in m
t - Time taken for H cm rise of water in sec
a1 - Area of inlet pipe in m2
a2 - Area of throat in m2
g - Specify gravity in m /s2
h - (h1-h2) [(Sm-S1)/S1]
h1 ,h2 - Manometric head in first & Second limb
Sm - Specific gravity of Manometric liquid
(For Mercury Sm =13.6)
S1 - Specific gravity of flowing liquid water (S1=1)

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TABULATION:
FOR 20mm Pipe
Sl.
No.
Manometer
Reading
h1 -
h2
x10-2
Manometric
Head
Time taken
for H cm
rise of
water
Actual
dischar
ge
Theoreti
cal
Discharg
e
Co
efficie
nt of
Dischar
ge
h1 h2
h=(h1-h2)
[(Sm-S1)/S1]
t Qact Qth Cd
cm of
Hg
cm
of
Hg
m of
water
m sec m3
/sec m3
/sec No Unit
Avg.
FOR 25mm Pipe
Sl.
No.
Manometer
Reading
h1 -
h2
x10-2
Manometri
c
Head
Time taken
for H cm
rise of
water
Actual
discharg
e
Theoret
ical
Dischar
ge
Co
efficie
nt of
Dischar
ge
h1 h2
h=(h1-h2)
[(Sm-S1)/S1]
t Qact Qth Cd
cm of
Hg
cm of
Hg
m of
water
m sec m3
/sec m3
/sec No Unit
Avg.

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MODEL CALCULATIONS:

9

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THEORY:
An orifice is an opening in the wall or base of a vessel through
which the fluid flows. The top edge of the orifice is always below the
free surface. Orifices are used to measure the discharge. An orifice is
termed small when its dimensions are small compared to the head causing
flow. The variation in the velocity from the top to the bottom edge is
considerable. According to shape there are circular orifices, rectangular
orifices, square orifices, Triangular orifices.
PROCEDURE:
1. The diameter of the inlet and outlet are recorded and the
dimensions of the collecting tank are measured
2. Priming is done
3. The inlet valve is opened slightly and the manometer heads on both
the h1, h2 are noted.
4. The outlet valve of the collecting tank is closed tightly and the
time taken for ‘H’ m rise of water in the collecting tank is
observed.
5. The above procedure is repeated by gradually increasing the flow
and observing the required readings.
6. The observations are tabulated and the coefficient of discharge of
the Orificemeter was computed
RESULT :
Thus, the coefficient of discharge of Orificemeter was determined.
For 20mm pipe Cd =
For 25mm pipe Cd =

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SCHEMATIC DIAGRAM OF VENTURIMETER

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DETERMINATION OF THE COEFFICIENT OF DISCHARGE OF GIVEN VENTURIMETER
EXP.NO.: DATE :
AIM :
To determine the co-efficient discharge through venturimeter.
APPARATUS REQUIRED:
1. Venturimeter
2. Differential U tube
3. Collecting tank
4. Stop watch
5. Meter scale
FORMULA TO BE USED:
1. Actual Discharge 𝐐 𝐚𝐜𝐭 =
𝐀 ×𝐇
𝐭
m3
/sec
2. Theoretical Discharge 𝐐𝐭𝐡 =
𝐚 𝟏 𝐚 𝟐 𝟐𝐠𝐡
𝐚 𝟏
𝟐−𝐚 𝟐
𝟐
m3
/sec
3. Co efficient of Discharge 𝐂 𝐝 =
𝐐 𝐚𝐜𝐭
𝐐 𝐭𝐡
Where,
A - Area of the Collecting tank in m2
H - Height of collected water in tank in m
t - Time taken for H cm rise of water in sec
a1 - Area of inlet pipe in m2
a2 - Area of throat in m2
g - Specify gravity in m /s2
h - (h1-h2) [(Sm-S1)/S1]
h1, h2 - Manometric head in first & Second limb
Sm - Specific gravity of Manometric liquid
(For Mercury Sm =13.6)
S1 - Specific gravity of flowing liquid water (S1=1)

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TABULATION:
FOR 20mm Pipe
Sl.
No.
Manometer
Reading h1-h2
x10-2
Manometric
Head
Time
taken for
H cm rise
of water
Actual
discharge
Theoretical
Discharge
Co
efficient
of
Discharge
h1 h2
h=(h1-h2)
[(Sm-S1)/S1]
t Qact Qth Cd
cm of Hg
cm of
Hg
m of
water
m sec m3
/sec m3
/sec No Unit
Avg.
FOR 25mm Pipe
Sl.
No.
Manometer
Reading h1-h2
x10-2
Manometric
Head
Time
taken for
H cm rise
of water
Actual
discharge
Theoretical
Discharge
Co
efficient
of
Discharge
h1 h2
H=(h1-h2)
[(Sm-S1)/S1]
t Qact Qth Cd
cm of Hg
cm of
Hg
m of
water
m sec m3
/sec m3
/sec No Unit
Avg.

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MODEL CALCULATIONS:

15

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THEORY:
A venturimeter is one of the most important practical applications
of Bernoulli’s theorem. It is an instrument used to measure the rate of
discharge in a pipe line and is often fixed permanently at different
sections of the pipe line
PROCEDURE:
1. The diameter of the inlet and outlet are recorded and the dimensions
of the collecting tank are measured
2. Priming is done
3. The inlet valve is opened slightly and the manometer heads on both
the h1, h2 are noted.
4. The outlet valve of the collecting tank is closed tightly and the
time taken for ‘H’ m rise of water in the collecting tank is
observed.
5. The above procedure is repeated by gradually increasing the flow and
observing the required readings.
6. The observations are tabulated and the coefficient of discharge of
the Venturimeter was computed
RESULT :
Thus, the coefficient of discharge of Venturimeter was determined.
For 20mm pipe Cd =
For 25mm pipe Cd =

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SCHEMATIC DIAGRAM OF ROTAMETER

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CALCULATION OF THE RATE OF FLOW USING ROTA METER
EXP. NO. : DATE :
AIM :
To determine the coefficient of discharge of the rotameter.
APPARATUS REQUIRED:
a. Rotameter setup
b. Measuring scale
c. Stopwatch.
FORMULA TO BE USED:
1. Actual Discharge 𝐐 𝐚𝐜𝐭 =
𝐀 ×𝐇
𝐭
m3
/sec
2. Co efficient of Discharge 𝐂 𝐝 =
𝐐 𝐚𝐜𝐭
𝐐 𝐑
Where,
QR - Rotameter Reading
A - Area of the collecting tank (m)
H - Rise of water in the capillary tube (m)
t - Time taken for H meter rise of water in the
capillary tube (s)
PROCEDURE:
1. Priming is done first for venting air from the pipes.
2. The inlet valve is opened slightly such that the discharge on the
rotameter is noted.
3. The outlet valve of the collecting tank is closed tightly and the
time taken for ‘H’ meter rise of water in the collecting tank is
observed.
4. The above procedure is repeated by gradually increasing the flow
and observing the required readings.
5. The observations are tabulated and the coefficient of discharge
of Rotameter is determined.
THEORY:
When the rate of flow increases the float rises in the tube and
consequently there is an increase in the annular area between the float
and the tube. Thus, the float rides higher or lowers depending on the
rate of flow.

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TABULATIONS:
FOR 20LPM
FOR 30LPM
Sl.
No.
Rotameter
discharge
Time for 10cm
rise of
water in the
capillary
tube
Actual
discharge
Co efficient
of Discharge
QR t Qact Cd
LPM m3
/sec sec m3
/sec -
1
2
3
4
Average
Sl.
No.
Rotameter
discharge
Time for 10cm
rise of
water in the
capillary
tube
Actual
discharge
Co efficient
of Discharge
QR t Qact Cd
LPM m3
/sec sec m3
/sec -
1
2
3
4
Average

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MODEL CALCULATIONS:
RESULT :
Thus, the coefficient of discharge (Cd) of Rotameter was determined.
For 20LPM Cd =
For 30LPM Cd =

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SCHEMATIC DIAGRAM OF FRICTION PIPES

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DETERMINATION OF FRICTION FACTOR FOR A GIVEN SET OF PIPES
EXP. NO. : DATE :
AIM :
To determine the friction factor for a given pipe.
APPARATUS REQUIRED:
 Pipe friction apparatus
 Manometer
 Stop watch
 Collecting tank
 Sump tank
FORMULAE TO BE USED:
1. FRICTION FACTOR f =
2gdhf
lv2
2. VELOCITY v=
𝑄
𝐴
m/sec
3. ACTUAL DISCHARGE Qact =
A ×H
t
m3
/sec
Where,
g - Acceleration due to gravity in m/s2
d - Diameter of the pipe in m
H - Height of collected water in tank in m
t - Time taken for H cm rise of water in sec
l - Length of the pipe in m
v - Velocity of the pipe in m/sec
hf - Loss of head due to friction
- (h1-h2)[(Sm-S1)/S1]
THEORY :
When water is flowing in a pipe, it experiences some resistance to
its motion. It effects in the reduction of the velocity and the head of
the water available. There are many types of losses, but the major loss
causes due to frictional resistance of the pipe only. The minor losses
are so small as compared to friction losses. The minor losses are such as
loss of head at entrance and loss of head due to velocity of water at
outlet.

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TABULATION :
FOR 15mm pipe
Sl.
No.
Manometer
Reading h1-h2
x10-2
Manometric
Head
Time
taken for
H cm rise
of water
Actual
discharge
Velocity
Friction
Factor
h1 h2
h=(h1-h2)
[(Sm-S1)/S1]
t Qact v f
cm of
Hg
cm of
Hg
m of
water
m sec m3
/sec m/sec No Unit
Avg.
FOR 20mm pipe
Sl.
No.
Manometer
Reading h1-h2
x10-2
Manometric
Head
Time
taken for
H cm rise
of water
Actual
discharge
Velocity
Friction
Factor
h1 h2
h=(h1-h2)
[(Sm-S1)/S1]
t Qact v f
cm of
Hg
cm of
Hg
m of
water
m sec m3
/sec m/sec No Unit
Avg.

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MODEL CALCULATIONS:

25

26
PROCEDURE :
 The diameter of the pipe is measured and the initial plan dimensions of
the collecting tank and the length of the pipe line between the two
pressure tapping cocks are measured.
 Keeping the outlet valve fully closed the inlet valve is opened
completely.
 The outlet valve is slightly opened and manometric heads in both the
limbs (h1 and h2) are measured.
 The outlet valve of the collecting tank is tightly closed and the
time‘t’ required for ‘H’ rise of water in the collecting tank is
observed by using a stop watch.
 The above procedure is repeated by gradually increasing the flow and
observing the corresponding readings.
 The observations are tabulated and the friction factor computed.
RESULT :
The frictional factor for given pipes were determined.
For 15mm pipe f =
For 20mm pipe f =

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SCHEMATIC DIAGRAM OF CENTRIFUGAL PUMP

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CONDUCTING EXPERIMENTS AND DRAWING THE CHARACTERISTIC CURVES OF
CENTRIFUGAL PUMP
EXP. NO. : DATE :
AIM:
To conduct the performance test of centrifugal pump, calculate the
efficiency and draw the characteristics curves.
APPARATUS REQUIRED:
 Centrifugal pump setup
 Meter scale
 Stop watch
FORMULA TO BE USED:
1. EFFICIENCY η =
PO
PI
× 100
2. OUTPUT POWER PO = ρgQH watts
3. INPUT POWER PI =
3600×N
E×T
watts
4. ACTUAL DISCHARGE Qact =
A ×h
t
m3
/sec
5. TOTAL HEAD H = hs + hd + z m
Where,
A = Area of the collecting tank (m2
)
h = 10 cm rise of water level in the collecting tank (m)
t = Time taken for 10 cm rise of water level in collecting tank
hs = Suction head; hs= Ps x 0.0136, m
hd = Discharge head; hd = Pd x 10, m
Z = Datum head, m
Pd = Pressure gauge reading, kg/cm2
Ps =Suction pressure gauge reading, mm of Hg
N = Number of revolutions of energy meter disc
E = Energy meter constant (rev / Kw hr)
T = Time taken for ‘N’ revolutions (seconds)
ρ = Density of water (kg/m3
)
g = Acceleration due to gravity (m /s2
)
H = Total head of water (m)

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TABULATION :
Sl.No.
Pressure Gauge
Reading
Pressure Head
Reading
TotalHead
Timetaken
for10cm
riseofwater
level
Timetaken
for‘N’
revolutions
Actual
Discharge
OutputPower
InputPower
Efficiency
Suction
Delivery
Suction
Delivery
Datum
Ps Pd hs hd Z H t T Qact PO PI η
mm of Hg kg/cm2
m m m m sec sec m3
/sec watts watts %
Average

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PRIMING:
The operation of filling water in the suction pipe casing and a
portion delivery pipe for the removal of air before starting is called
priming.
After priming the impeller is rotated by a prime mover. The rotating
vane gives a centrifugal head to the pump. When the pump attains a
constant speed, the delivery valve is gradually opened.
The water flows in a radially outward direction. Then, it leaves the
vanes at the outer circumference with a high velocity and pressure. Now
kinetic energy is gradually converted in to pressure energy.
The high-pressure water is through the delivery pipe to the required
height.
MODEL CALCULATIONS:

31

32
THEORY:
 The radial flow type pumps are commonly called as Centrifugal pumps.
Centrifugal pumps are the most widely used of all the turbo
machine(Rotodynamic) pumps. It has flow in relative direction through
the impeller. The flow takes place from the low pressure towards the
high pressure. This type of pumps uses the centrifugal force created
by an impeller which spins at high speed inside the pump casing.
 Water is drawn into the pump from the source of supply through a
short length of pipe (suction pipe). Impeller rotates; it spins the
liquid sitting in the cavities between the vanes outwards and
provides centrifugal acceleration with the kinetic energy.
 This kinetic energy of a liquid coming out an impeller is harnessed
by creating a resistance to flow. The first resistance is created by
the pump volute (casing) that catches the liquid and shows it down.
 In the discharge nozzle, the liquid further decelerates and its
velocity is converted to pressure according to BERNOULLI’S PRINCIPLE.
PROCEDURE:
1. Prime the pump close the delivery valve and switch on the unit
2.Open the delivery valve and maintain the required delivery head
3. Note down the reading and note the corresponding suction head
reading
4. Close the drain valve and note down the time taken for 10 cm rise
of water level in collecting tank
5. Measure the area of collecting tank
6. For different delivery tubes, repeat the experiment
7. For every set reading note down the time taken for 5 revolutions
of energy meter disc.
GRAPHS:
1. Actual discharge Vs Total head
2. Actual discharge Vs Input power
3. Actual discharge Vs Output power
4. Actual discharge Vs Efficiency
RESULT:
Thus the performance test of centrifugal pump was conducted and
characteristics curves were drawn.
The efficiency was found to be _____________

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SCHEMATIC DIAGRAM OF RECIPROCATING PUMP

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CONDUCTING EXPERIMENTS AND DRAWING THE CHARACTERISTIC CURVES OF
RECIPROCATING PUMP
EXP. NO. : DATE :
AIM:
To conduct the performance test of reciprocating pump, calculate the
efficiency and draw the characteristics curves.
APPARATUS REQUIRED:
 Reciprocating pump setup
 Meter scale
 Stop watch
FORMULA TO BE USED:
1. EFFICIENCY η =
PO
PI
× 100
2. OUTPUT POWER PO = ρgQH watts
3. INPUT POWER PI =
3600×N
E×T
watts
4. ACTUAL DISCHARGE Qact =
A ×h
t
m3
/sec
5. TOTAL HEAD H = hs + hd + z m
Where,
A = Area of the collecting tank (m2
)
h = 10 cm rise of water level in the collecting tank (m)
t = Time taken for 10 cm rise of water level in collecting tank
hs = Suction head; hs= Ps x 0.0136, m
hd = Discharge head; hd = Pd x 10, m
Z = Datum head, m
Pd = Pressure gauge reading, kg/cm2
Ps =Suction pressure gauge reading, mm of Hg
N = Number of revolutions of energy meter disc
E = Energy meter constant (rev / Kw hr)
T = Time taken for ‘N’ revolutions (seconds)
ρ = Density of water (kg/m3
)
g = Acceleration due to gravity (m /s2
)
H = Total head of water (m)

35
TABULATION :
Sl.No.
Pressure Gauge
Reading
Pressure Head
Reading
TotalHead
Timetaken
for10cm
riseofwater
level
Timetaken
for‘N’
revolutions
Actual
Discharge
OutputPower
InputPower
Efficiency
Suction
Delivery
Suction
Delivery
Datum
Ps Pd hs hd Z H t T Qact PO PI η
mm of Hg kg/cm2
m m m m sec sec m3
/sec watts watts %
Average

36
MODEL CALCULATIONS:

37

38
THEORY:
Reciprocating pumps are also classified as positive displacement
pumps. Here definite volume of liquid is trapped in a chamber which is
alternatively filled from the inlet and emptied at a higher pressure
through the discharge. Most piston pumps are acting with liquid admitted
alternatively on each side of the piston so that one part of the cylinder
is being filled where as the other being emptied to minimize fluctuations
in the discharge.
PROCEDURE:
1. Close the delivery valve and switch on the unit
2. Open the delivery valve and maintain the required delivery head
3. Note down the reading and note the corresponding suction head
reading
4. Close the drain valve and note down the time taken for 10 cm rise
of water level in collecting tank
5. Measure the area of collecting tank
6. For different delivery tubes, repeat the experiment
7. For every set reading note down the time taken for 5 revolutions
of energy meter disc.
GRAPHS:
1. Actual discharge Vs Total head
2. Actual discharge Vs Input power
3. Actual discharge Vs Output power
4. Actual discharge Vs Efficiency
RESULT:
Thus the performance test of reciprocating pump was conducted and
characteristics curves were drawn.
The efficiency was found to be _____________

39
SCHEMATIC DIAGRAM OF GEAR PUMP
EXTERNAL GEAR PUMP INTERNAL GEAR PUMP

40
CONDUCTING EXPERIMENTS AND DRAWING THE CHARACTERISTIC CURVES OF GEAR PUMP
EXP. NO. : DATE :
AIM:
To conduct the performance test of gear pump, calculate the
efficiency and draw the characteristics curves.
APPARATUS REQUIRED:
 Gear pump setup
 Meter scale
 Stop watch
FORMULA TO BE USED:
1. EFFICIENCY η =
PO
PI
× 100
2. OUTPUT POWER PO = ρgQH watts
3. INPUT POWER PI =
3600×N
E×T
watts
4. ACTUAL DISCHARGE Qact =
A ×h
t
m3
/sec
5. TOTAL HEAD H = hs + hd + z m
Where,
A = Area of the collecting tank (m2
)
h = Rise of oil level in the collecting tank (m)
t = Time taken for 10 cm rise of oil level in collecting tank
hs = Suction head; hs= Ps x 0.0136, m
hd = Discharge head; hd = Pd x 12.5, m
Z = Datum head, m
Pd = Pressure gauge reading, kg/cm2
Ps =Suction pressure gauge reading, mm of Hg
N = Number of revolutions of energy meter disc
E = Energy meter constant (rev / Kw hr)
T = Time taken for ‘N’ revolutions (seconds)
ρ = Density of water (kg/m3
)
g = Acceleration due to gravity (m /s2
)
H = Total head of water (m)

41
TABULATION :
Sl.No.
Pressure Gauge
Reading
Pressure Head
Reading
TotalHead
Timetaken
for10cm
riseofwater
level
Timetaken
for‘N’
revolutions
Actual
Discharge
OutputPower
InputPower
Efficiency
Suction
Delivery
Suction
Delivery
Datum
Ps Pd hs hd Z H t T Qact PO PI η
mm of Hg kg/cm2
m m m m sec sec m3
/sec watts watts %
Average

42
MODEL CALCULATIONS:

43

44
THEORY:
The gear pump test rig consisting of a gear pump coupled to an
induction motor through flexible coupling. The pump is mounted on an oil
sump and a suction pipe with suction gauge, delivery pipe with delivery
gauge, discharge control valve etc provided. This being a positive
displacement pumps full closing of the delivery control valve should be
avoided.
A collecting tank with gauge glass and scale fittings with drain
valve fittings provided to measure the pump discharge and to drain back
the oil to the sump.
A panel with switch, starter and energy meter provided to note the
input power. The gear pump consists of two identical intermeshing spur
wheels working with a fine clearance inside the casing. The wheels are so
designed that they form a fluid tight joint at the point of contact. One
o the wheels is keyed to the driving shaft and the other revolves as a
driven wheel.
The pump is first filled with the liquid before it is started, as
the gear rotate; the liquid is trapped in between their teeth and is
flown to the discharge end round the casing. The rotating gears build up
sufficient pressure to force the liquid into the delivery pipe. Each
tooth of gear acts like a piston of a reciprocating pump to force liquid
into the discharge line.
PROCEDURE:
1. The gear oil pump is stated.
2. The delivery gauge reading is adjusted for the required value.
3. The corresponding suction gauge reading is noted.
4. The time taken for ‘N’ revolutions in the energy meter is noted
with the help of a stopwatch.
5. The time taken for ‘h’ rise in oil level is also noted down after
closing the gate valve.
6. With the help of the meter scale the distance between the suction
and delivery gauge is noted.
7. For calculating the area of the collecting tank its dimensions
are noted down.
8. The experiment is repeated for different delivery gauge readings.
9. Finally the readings are tabulated.
GRAPHS:
1. Actual discharge Vs Total head
2. Actual discharge Vs Input power
3. Actual discharge Vs Output power
4. Actual discharge Vs Efficiency
RESULT:
Thus the performance test of gear pump was conducted and
characteristics curves were drawn.
The efficiency was found to be _____________

45
SCHEMATIC DIAGRAM OF PELTON WHEEL TURBINE

46
CONDUCTING EXPERIMENTS AND DRAWING THE CHARACTERISTIC CURVES OF PELTON WHEEL
EXP. NO. : DATE :
AIM:
To conduct the performance test of pelton wheel turbine, calculate
the efficiency and draw the characteristics curves.
APPARATUS REQUIRED:
 Pelton wheel turbine
 Tachometer
FORMULA TO BE USED:
1. EFFICIENCY η =
PO
PI
× 100
2. INPUT POWER PI = ρgQH watts
3. OUTPUT POWER PO =
2πNT
60
watts
4. ACTUAL DISCHARGE Qact = 0.0055 h m3
/sec
5. VENTURIMETER READUNG h = P1 − P2 × 10 m of water
6. TORQUE T= R x T1 − T2 × g N-m
THEORY:
There are two types of turbines, reaction and the impulse, the
difference being the manner of head conversion. In the reaction turbine,
the fluid fills the blade passages, and the head change or pressure drop
occurs within the runner. An impulse turbine first converts the water
head through a nozzle into a high-velocity jet, which then strikes the
buckets at one position as they pass by. The runner passages are not
fully filled, and the jet flow past the buckets is essentially at
constant pressure. Impulse turbines are ideally suited for high head and
relatively low power. The Pelton turbine used in this experiment is an
impulse turbine.

47
TABULATION:
Sl.No.
Pressure
Gauge
Reading
Venturimeter
Reading
Venturimeter
Reading
Spring
Balance
Reading
Speed
of
turbine
Total
Head
Actual
Discharge
Input
Power
Output
Power
Efficiency
hP P1 P2 h T1 T2 N H Qact PI PO η
Kg/cm2
Kg/cm2
m of water kg kg rpm m m3
/sec W W %

48
MODEL CALCULATION:

49

50
PROCEDURE:
1. Gradually, open the delivery valve of the pump.
2. Adjust the nozzle for half open by operating the needle valve by
hand wheel.
3. The head should be maintained by operating the delivery valve and at
Constant value.
4. Observe the speed of wheel using tachometer.
5. Observe the reading h1 &h2 in the two manometer limbs which are
connected to the venturimeter.
6. The experiment is repeated for different loads and the readings are
tabulated.
GRAPH:
 Speed Vs Input Power
 Speed Vs Output Power
 Speed Vs Actual Discharge
 Speed Vs Efficiency
RESULT:
Thus performance tests are conducted on the Pelton wheel turbine and
characteristic curves are drawn.
Efficiency of turbine is

51
SCHEMATIC DIAGRAM OF FRANCIS TURBINE

52
CONDUCTING EXPERIMENTS AND DRAWING THE CHARACTERISTIC CURVES OF FRANCIS TURBINE
EXP. NO. : DATE :
AIM:
To conduct the performance test of Francis turbine, calculate the
efficiency and draw the characteristics curves.
APPARATUS REQUIRED:
 Francis turbine
 Tachometer
FORMULA TO BE USED:
1. EFFICIENCY η =
PO
PI
× 100
2. INPUT POWER PI = ρgQH watts
3. OUTPUT POWER PO =
2πNT
60
watts
4. ACTUAL DISCHARGE Qact = 0.011 h m3
/sec
5. VENTURIMETER READUNG h = P1 − P2 × 10 m of water
6. TORQUE T= R x T1 − T2 × g N-m
THEORY:
The Francis turbine is a type of water turbine that was developed by
James B. Francis in Lowell, Massachusetts.[1] It is an inward-flow
reaction turbine that combines radial and axial flow concepts.
Francis turbines are the most common water turbine in use today.
They operate in a water head from 40 to 600 m (130 to 2,000 ft) and are
primarily used for electrical power production. The electric generator
which most often use this type of turbine, have a power output which
generally ranges just a few kilowatts up to 800 MW, though mini-hydro
installations may be lower. Penstock (input pipes) diameters are between
3 and 33 feet (0.91 and 10.06 metres). The speed range of the turbine is
from 83 to 1000 rpm. Wicket gates around the outside of the turbine's
rotating runner control the rate of water flow through the turbine for

53
TABULATION:
Sl.No.
Pressure
Gauge
Reading
Venturimeter
Reading
Venturimeter
Reading
Spring
Balance
Reading
Speed
of
turbine
Total
Head
Actual
Discharge
Input
Power
Output
Power
Efficiency
hP P1 P2 h T1 T2 N H Qact PI PO η
Kg/cm2
Kg/cm2
m of water kg kg rpm m m3
/sec W W %

54
different power production rates. Francis turbines are almost always
mounted with the shaft vertical to keep water away from the attached
generator and to facilitate installation and maintenance access to it and
the turbine.
MODEL CALCULATION:

55

56
PROCEDURE:
1. The Francis turbine is started
2. All the weights in the hanger are removed
3. The pressure gauge reading is noted down and this is to be
Maintained constant for different loads
4. Pressure gauge reading is ascended down
5. The Venturimeter reading and speed of turbine are noted down
6. The experiment is repeated for different loads and the readings
are tabulated.
GRAPH:
 Speed Vs Input Power
 Speed Vs Output Power
 Speed Vs Actual Discharge
 Speed Vs Efficiency
RESULT:
Thus performance tests are conducted on the Francis turbine and
characteristic curves are drawn.
Efficiency of turbine is

57
SCHEMATIC DIAGRAM OF KAPLAN TURBINE

58
CONDUCTING EXPERIMENTS AND DRAWING THE CHARACTERISTIC CURVES OF KAPLAN TURBINE
EXP. NO. : DATE :
AIM:
To conduct the performance test of Kaplan turbine, calculate the
efficiency and draw the characteristics curves.
APPARATUS REQUIRED:
 Kaplan turbine
 Tachometer
FORMULA TO BE USED:
1. EFFICIENCY η =
PO
PI
× 100
2. INPUT POWER PI = ρgQH watts
3. OUTPUT POWER PO =
2πNT
60
watts
4. ACTUAL DISCHARGE Qact = 0.0055 h m3
/sec
5. VENTURIMETER READUNG h = P1 − P2 × 10 m of water
6. TORQUE T= R x T1 − T2 × g N-m
THEORY:
Kaplan turbine is an axial flow reaction turbine used in dams and
reservoirs of low height to convert hydraulic energy into mechanical and
electrical energy. They are best suited for low heads say from 10m to 5m.
The specific speed ranges from 200 to 1000
The flow through the pipelines into the turbine is measured with the
office meter fitted in the pipeline. A mercury manometer is used to
measure the pressure difference across the orifice meter. The net
pressure difference across the turbine output torque is measured with a
pressure gauge and vacuum gauge. The turbine output torque is determined
with the rope brake drum. A tachometer is used to measure the rpm.

59
TABULATION:
Sl.No.
Pressure
Gauge
Reading
Venturimeter
Reading
Venturimeter
Reading
Spring
Balance
Reading
Speed
of
turbine
Total
Head
Actual
Discharge
Input
Power
Output
Power
Efficiency
hP P1 P2 h T1 T2 N H Qact PI PO η
Kg/cm2
Kg/cm2
m of water kg kg rpm m m3
/sec W W %

60
MODEL CALCULATION:

61

62
PROCEDURE:
1. Keep the runner vane at require opening
2. Keep the guide vanes at required opening
3. Prime the pump if necessary
4. Close the main sluice valve and they start the pump.
5. Open the sluice valve for the required discharge when the pump
motor switches from star to delta mode.
6. Load the turbine by adding weights in the weight hanger. Open the
brake drum cooling water gate valve for cooling the brake drum.
7. Measure the turbine rpm with tachometer
8. Note the pressure gauge and vacuum gauge readings
9. Note the orifice meter pressure readings.
10.Repeat the experiments for other loads.
GRAPH:
 Speed Vs Input Power
 Speed Vs Output Power
 Speed Vs Actual Discharge
 Speed Vs Efficiency
RESULT:
Thus performance tests are conducted on the Kaplan turbine and
characteristic curves are drawn.
Efficiency of turbine is