hydraulic machines and fluid energy systems (engm...

Jazan University Faculty of Engineering Mechanical Eng. Dept.

Hydraulic Machines and Fluid Energy Systems

(EngM 426)

Experiment Report

Performance Curves of a Positive-Displacement Pump (Piston type)

Student Name:

----------------------------------------------------------------

Student ID:

--------------------------------

( )



(EngM 426)

Experiment Report

Pumps connected in series and parallel

Student Name:

----------------------------------------------------------------

Student ID:

--------------------------------

( )

Hydraulic Machines & Fluid Energy Systems (EngM 426)

Dr. Ahmed Bagabir Page 2 of 8

1. Objective: To determine the head-discharge characteristics of two identical centrifugal pumps operating in series and parallel and to compare with the theoretical results. 2. Apparatus: Hydraulic bench, two centrifugal pumps, power meter, flowrate meter, speed meter and pressure gauges.

Ref. no. Item 1 Valve for parallel operation 2 Pump no. 2 suction pressure gauge 3 Valve for series operation 4 Pump no. 2 suction valve 5 Pump no. 1 suction valve 6 Pump no. 1 suction pressure gauge

Pump specifications: Maximum head = 20 m Maximum discharge = 0.7 Lps (42 Lpm) Maximum speed = 6000 rpm



3. Procedure: 1. Connect the two pumps in series (as shown below).

2. Switch on pumps. 3. Set the pump speeds at same constant value. 4. Start the test with the regulating valve closed. 5. Read off pressures before and after the pumps, volumetric flow rate and electrical power. 6. Partially open the valve and take the readings. 7. Repeat above step until the valve is fully open.

8. Repeat above steps for the two pumps connected in parallel (as shown below).



4. Readings: 4.1 Pumps in series Speed =

No. Volume (Litre)

Time (s)

Inlet Exit p1 (bar) p2 (bar)

1 2 3 4 5 6 7

4.1 Pumps in parallel Speed =

No. Volume (Litre)

Time (s)

Inlet Exit p1 (bar) p2 (bar)

1 2 3 4 5 6 7



5. Calculations (2 marks):

5.1. Single pump (Given)

No. Flowrate (Litre/s)

Head (m)

1 0.0 11.5 2 0.2 10.2 3 0.4 8.2 4 0.6 3.0 5 0.7 0

5.2. Pumps in series


Head (m)

1 2 3 4 5 6 7

5.3. Pumps in parallel


Head (m)

1 2 3 4 5 6 7



6. Sample calculations (2 marks):



7. Results and Discussion (6 marks): 7.1. Pumps in series:

Fig. 1: Head against flowrate for single pump and pumps in series compared with theoretical

result.

0

5

10

15

20

25

30

0.0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 1.0

Hea

d (m

)

Q (L/s)



7.2. Pumps in parallel:

Fig. 2: Head against flowrate for single pump and pumps in parallel compared with theoretical

result.

0

5

10

15

20

25

30

0.0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 1.0

Hea

d (m

)

Q (L/s)



(EngM 426)

Experiment Report

Performance Curves of a Centrifugal Pump

Student Name:

----------------------------------------------------------------

Student ID:

--------------------------------

( )



1. Objective: Determine the actual performance curves of a centrifugal pump at constant speed. 2. Apparatus: centrifugal pump, hydraulic bench, power meter, flowrate meter, pressure gauges. Maximum pump head = 24 m Maximum pump discharge = 1400 L/min Maximum motor power = 4 kW Pump speed = 1450 - 2900 rpm



3. Procedure: 1. Switch on the pump. 2. Set pump speed at constant value. 3. Start the test with the regulating valve closed. 4. Read off pressures before and after the pump, volumetric flow rate and electrical power. 5. Partially open the valve and take the readings. 6. Repeat above step until the valve is fully open. 7. Change pump speed and repeat steps 3 - 6.

4. Readings: 4.1. At speed = rpm

Q (l/min) p1 (bar) p2 (bar) Power (W)

1

2

3

4

5

6

7

8

6.2. At speed = rpm

Q (l/min) p1 (bar) p2 (bar) Power (W)

1

2

3

4

5

6

7

8



5. Theory:

1

2

2

2

22 ⎟⎟⎠

⎞⎜⎜⎝

⎛++⎟⎟

⎠

⎞⎜⎜⎝

⎛++= z

gV

gp-z

gV

gpH

ρρ

dQ

AQV

42π==

power shaft

gQHρη =

Pump impeller diameter = 125 mm Suction pipe diameter = 0.065 m Discharge pipe diameter = 0.05 m β2 = 20o b2 = 20 mm

0.15m

0.3m

Din = 0.065m

Dout = 0.05m

grgHth ⎜⎜⎝−= 22π



6. Calculations (2 marks): 6.1. At speed = rpm

Q (m3/s) H (m) Pw (W) Pm (W) η (%) Hth (m) 1 2 3 4 5 6 7 8

6.2. At speed = rpm

Q (m3/s) H (m) Pw (W) Pm (W) η (%) Hth (m) 1 2 3 4 5 6 7 8



6.3. Sample calculations (2 marks): For point number ( ) of speed rpm:



7. Results and Discussion (6 marks):

Fig. 1: Pressure head against flowrate for two different speeds; compared with the theoretical

pressure head.

0

10

20

30

40

50

0 100 200 300 400 500 600

Hea

d (m

)

Q (L/min)



Fig. 2: Shaft power against flowrate for two different speeds.

0

10

20

30

40

50

0 100 200 300 400 500 600

Pow

er (W

)

Q (L/min)



Fig. 3: Pump efficiency against flowrate for two different speeds.

0

10

20

30

40

50

0 100 200 300 400 500 600

Effic

ienc

y (%

)

Q (L/min)



1. Objective: Determine the actual performance curves of a positive-displacement pump (piston type) at constant speed. 2. Apparatus: Positive-displacement pump (piston type) of maximum speed 1040rpm, hydraulic bench (max. pressure is 5 bar), power meter, flowrate meter, pressure gauges.



3. Procedure: 1. Switch on the pump in clockwise direction. 2. Set pump speed at constant value. 3. Start the test with discharge valve fully open. 4. Read off pressures before and after the pump, volumetric flow rate and brake force. 5. Partially close the valve and take the readings. 6. Repeat above step for maximum of 6 bar outlet pressure. 7. Do not fully close the valve. 8. Change pump speed and repeat steps 3 - 6.

4. Readings:

4.1. At speed = rpm

No. p1 (bar) p2 (bar) Q (l/min) Force (N) 1 2 3 4 5 6 7 8 9

6.2. At speed = rpm

No. p1 (bar) p2 (bar) Q (l/min) Force (N) 1 2 3 4 5 6 7 8 9



5. Theory:

inoutinout z

gV

gp-z

gV

gpHHHead ⎟⎟

⎠

⎞⎜⎜⎝

⎛++⎟⎟

⎠

⎞⎜⎜⎝

⎛++=−=

22

22

ρρ

( ) gQHP Power Water w ρ= ( ) ω×= T P Power Shaft m

( ) LFTorque ×=T

Arm length, L = 20 cm

power shaft

gQHρη =



6. Calculations (2 marks): 6.1. At speed = rpm

No. Head (m) Q (L/min) Pw Pm η (%) 1 2 3 4 5 6 7 8 9

6.2. At speed = rpm

No. Head (m) Q (L/min) Pw Pm η (%) 1 2 3 4 5 6 7 8 9



6.3. Sample calculations (2 marks): For point number ( ) of speed rpm:



7. Results and Discussion (6 marks):

0

5

10

15

20

25

0 10 20 30 40 50 60

Q (L

/min

)

Head (m)

Fig. 1: Flowrate against pressure head for two different speeds.



0

5

10

15

20

25

0 10 20 30 40 50 60

Pow

er (W

)

Head (m)

Fig. 2: Shaft power against pressure head for two different speeds.



0

5

10

15

20

25

0 10 20 30 40 50 60

Effic

ienc

y (%

)

Head (m)

Fig. 3: Pump efficiency against pressure head for two different speeds.



(EngM 426)

Experiment Report

Performance Curves of the Pelton’s Turbine

Student Name:

----------------------------------------------------------------

Student ID:

--------------------------------

( )



1. Objective: Determine performance curves of the Pelton’s turbine for different speeds. 2. Apparatus: Pelton’s turbine, hydraulic bench, optic tachometer, band brake with two dynamometers and pressure gauge.

3. Procedure:

1. Place the turbine in the bench and connect it to the water supply of the bench. 2. Switch on the pump. 3. Fully open the control valve of the bench. 4. Take the reading necessary to calculate the volume flow rate. 5. Set the band brake free (e.g. zero torque). 6. Take the reading of the brake device (F or M), tachometer (N) and pressure gauge (p). 7. Lower the braking device. 8. Repeat steps 6-7 for different turbine speeds.


Hydraulic Machines and Fluid Energy Systems (EngM 426)

Experiment Report

Performance Curves of Francis Turbine

Student Name:

----------------------------------------------------------------

Student ID:

--------------------------------



1. Objective: Determine performance curves of the Francis turbine at constant head. 2. Apparatus: Hydraulic bench, Francis turbine, brake drum, digital tachometer and pressure gauge.



3. Procedure: 1. Switch on the pump. 2. Fully open the control valve of the bench. 3. Fix guide vane position (eg. 1-10). 4. Set the brake free (e.g. zero torque). 5. Take the reading necessary to calculate the volume flow rate. 6. Take the reading of torque, speed and pressure of the inlet flow. 7. Lower the braking device for interval of about 500 rpm. 8. Repeat steps 6-7 for different turbine speeds.

4. Readings: Guide vane position =

No. Speed (rpm)

Flowrate (L/hr)

Pressure (bar)

Torque (N.m)

1

2

3

4

5

6

7

5. Calculations:

gQHPw ρ= NT velocity angulartorquePm π2×=×=

w

m

PP

=η

No. N (rpm)

Q (m3/s)

Pw (W)

Pm (W)

η (%)

1

2

3

4

5

6

7



Sample calculations:



6. Results and Discussion:

Fig. 1: Flowrate against speed.



Fig. 2: Head against speed.



Fig. 3: Mechanical power against speed.



Fig. 4: Efficiency against speed.



4. Readings: Volume = Liter Time = Seconds

No. F1 or M1 (N or g)

F2 or M2 (N or g)

Speed (rpm)

Pressure (bar)

1

2

3

4

5

6

7



5. Calculations: Mean turbine radius = 50 mm Torque arm, L = 30 mm k = 0.98 β = 165o Cv = 0.94

gHCvV j 2= gQHPw ρ=

ω×= TPm

gQH

TPP

w

m

ρωη ×

==

For force type:

( ) LFFLFarm TorqueForceTorque ×−=×=×= 12 where F is the spring force in Newton. For weight type:

( ) LgMMLFarm TorqueForceTorque ××−=×=×= 21 where M is the weight in grams.

Q = (m3/s) H = (m) Vj = (m/s) Pw = (W)

No u (m/s)

u/Vj

(φ)

Experimental Theoretical Torque (N.m)

Pm (W)

η (%)

Torque (N.m)

Pm (W)

η (%)

1 2 3 4 5 6 7



Sample calculations:



6. Results and Discussion:

Fig. 1: Experimental torque against φ (u/Vj) compared with theoretical results.

0.0

0.1

0.2

0.3

0.4

0.0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8

Torq

ue

U/Vj



Fig. 2: Experimental Mechanical power (Pm) against φ (u/Vj) compared with theoretical results.

0

5

10

15

20

25

30

0.0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8

Shaf

t Pow

er

U/Vj



Fig. 3: Experimental Efficiency (η) against φ (u/Vj) compared with theoretical results.

0

20

40

60

80

100

0.0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8

Effic

ienc

y (%

)

U/Vj

hydraulic machines and fluid energy systems (engm...

Documents