me2208 -fmm lab manual 1 -1 -...

2

Observations:

Diameter of the inlet d1 =

Diameter of the orifice do =

Length of the collecting tank L =

Breath of the collecting tank B =

Height of water collection y =

Tabulation:

S.No.

Manometer Reading Venturi Head

ℎ = ℎ� �� − 1� of water

Time for ‘y’

cm rise (t)

Sec

Actual

Discharge (��) ��/��

Theoretical

Discharge

(��) ��/��

Co efficient of

discharge

�� =�� ℎ� ��

ℎ� ��

ℎ� = (ℎ� − ℎ�) ∗10�� m

3

Aim:

To determine the co-efficient of discharge of the given Orifice meter.

Apparatus Required:

1. Differential U tube manometer

2. Stop watch

3. Steel rule

4. Collecting tank fitted with piezometer

Description:

An orifice meter is a measuring device used to measure the flow rate of liquid flowing through a pipe. It measures the flow rate based on the Principle of Bernoulli’s equation. It consists of a plate containing a sharp edged orifice introduced in the pipeline. The orifice plate is fitted to the pipe by flanged joint.

Formula Used:

(i) Manometric difference of mercury, ℎ� = (ℎ� − ℎ�) ∗10�� m

(ii) Water head in Venturi meter ℎ = ℎ� �� − 1!�Where, S1 = Specific gravity of mercury

S2 = Specific gravity of water

(iii) Theoretical Discharge, �� = �� "�#$%��

Where, &�= diameter of the pipe, area of the pipe'� = () &�� &*= diameter at throat, area of the throat '* =() &*� g = Acceleration due to gravity

(iv) Actual Discharge, �� = +,�

Where, A = Cross sectional area of the collecting tank = (L x B)

y – Raise of head in collecting tank ‘m’

t - Time taken for ‘y’ m depth of collection sec

L- Length of the tank ‘m’

B- Breath of the tank ‘m’

(v) Co-efficient of Discharge, �� =-.-/

Ex.No:

Date :

DETERMINATION OF CO-EFFICIENT OF DISCHARGE OF

ORIFICEMETER

4

Model Calculations:

(i) Difference in Manometric mercury level ℎ� = (ℎ� − ℎ�) ∗ 10�� m =

(ii) Water head in Orifice meter ℎ = ℎ� �� − 1! =

(iii) Theoretical Discharge �� = �� "�#$%��

m3/s

'� =() &�� = '�= '� =04 &*� =

�� =

(iv) Actual Discharge Qa = Ay/t m3/s

A = (L x B) =

�� = +,�

(v) Co-efficient of Discharge �� = -.-/

�� =

5

Procedure:

1. The given Orifice meter is connected to the horizontal pipe line.

2. Diameter of the pipe, Diameter of the orifice, size of the collecting tank are noted as

observations.

3. Water is let to flow through the orifice meter and is let into the collecting tank by

opening the valve at downstream end of the orifice meter.

4. The limbs of the manometer are flushed by operating the manometric stop cocks.

5. The manometer cocks are set to read the position after eliminating the air bubbles.

6. The left limb & right limb readings of the manometers are observed for each volume of

discharge.

7. The exit valve of the collecting tank is closed and time taken for 10cm rise of water is

noted using stopwatch.

8. The steps 5 & 6 are repeated by varying the inlet valve opening orifice meter.

that is by varying the discharge.

7. After sufficient readings are taken, the valve of downstream is opened and inlet to

orifice meter is closed.

8. The observations are tabulated and Co efficient of discharge of orifice meter is

calculated.

Precautions:

• Care should be taken while operating the manometer, cocks are should be

used to avoid loss of mercury which may enter the pipe line.

• The overflow of the collecting tank should be avoided.

• The exit valve of the collecting tank should be completely closed while the

time taken for 10cm rise of water is noted.

Graph:

From the observations made the following graphs are plotted

(i) √h cm vs Qa (ii) log h vs log Qa

Result:

1. The Co-efficient of discharge of orificemeter Cd from calculation =

2. The Co-efficient of discharge of orificemeter Cd from graph =

6

Observations:

Diameter of the inlet d1 =

Diameter of throat d0 =



Height of water collection ‘y’ =

Tabulation:

S.No.


ℎ = ℎ� �� − 1� of water

Time for ‘y’

�� rise (t) Sec

Actual


Theoretical

Discharge

(��) ��/��

Co efficient of

discharge

�� =�� ℎ�� ℎ�� ℎ� = (ℎ� − ℎ�) ∗

10�� m

7

Aim:

To determine the co-efficient of discharge of the given Venturimeter.

Apparatus Required:


2. Stop watch

3. Steel rule

4. Collecting tank fitted with piezo meter

Description:

A venturimeter is a measuring device used to measure the flow rate of liquid flowing through a pipe. It measures the flow rate based on Bernoulli’s equation. It consists of converging pipe, throat and a diverging pipe. The venturimeter is fitted to the pipe by flanged joint.

Formula Used:

(i) Manometric difference of mercury, ℎ� = (ℎ� − ℎ�) ∗10�� m

(ii) Water head in Venturimeter ℎ = ℎ� �� − 1!�Where, S1 = Specific gravity of mercury


(iii) Theoretical Discharge, �� = �� "�#$%��

Where, &�= diameter of the pipe, area of the pipe'� = () &�� &*= diameter at throat, area of the throat '* =() &*� g = Acceleration due to gravity

(iv) Actual Discharge, �� = +,�

Where, A = Cross sectional area of the collecting tank = (L x B)

y – Raise of head in collecting tank ‘m’

t - Time taken for ‘y’ m depth of collection sec

L- Length of the tank ‘m’

B- Breath of the tank ‘m’

(v) Co-efficient of Discharge, �� =-.-/

DETERMINATION OF CO-EFFICIENT OF DISCHARGE OF

VENTURIMETER

Ex.No:

Date :

8

Model Calculations:

(i) Difference in Manometric mercury level ℎ� = (ℎ� − ℎ�) ∗ 10�� m =

(ii) Water head in Orifice meter ℎ = ℎ� �� − 1! =

(iii) Theoretical Discharge �� = �� "�#$%��

m3/s

'� =() &�� = '�= '� =04 &*� =

�� =

(iv) Actual Discharge Qa = Ay/t m3/s

A = (L x B) =

�� = +,� =

(v) Co-efficient of Discharge �� =-.-/ �� =

9

Procedure:

1. The given venturimeter is connected to the horizontal pipe line.

2. Diameter of the pipe, Diameter of the orifice, size of the collecting tank are noted as

observations.

3. Water is let to flow through the venturimeter and is let into the collecting tank by

opening the valve at downstream end of the venturimeter.

4. The limbs of the manometer are flushed by operating the manometric stop cocks.

5. The manometer cocks are set to read the position after eliminating the air bubbles.

6. The left limb & right limb readings of the manometers are observed for each volume of

discharge.

7. The exit valve of the collecting tank is closed and time taken for 10cm rise of water is

noted using stopwatch

8. The steps 5 & 6 are repeated by varying the inlet valve opening venturimeter that is

by varying the discharge.

9. After sufficient readings are taken, the valve of downstream is opened and inlet to

venturimeter is closed.

10. The observations are tabulated and Co-efficient of discharge of orificemeter is

calculated.

Precautions:

• Care should be taken while operating the manometer, cocks are should be

used to avoid loss of mercury which may enter the pipe line.




Graph:


√h cm vs Qa (ii) log h vs log Qa

Result:

The Co-efficient of discharge of venturimeter (Cd ) from calculation =

The Co-efficient of discharge of venturimeter (Cd) from graph =

10

Tabulations

Area of the measuring tank=

S.No.

Rotameter Reading

Depth of collection

‘y’ �� Time for ‘y’ �� rise (t)

Sec

Actual


Co efficient of

discharge

�� =�� Theoretical Discharge

(LPM)

11

Ex.No:

Date:

Aim:

To determine the co-efficient of discharge of the given Rotameter.

Apparatus Required:


2. Stop watch

3. Steel rule


Description:

A rotameter is a measuring device used to measure the flow rate of liquid flowing through a pipe. It measures the flow rate based on Bernoulli’s equation. The Rotameter having the range of 0-10 LPM range is fitted on the pipe line of the mono block pump set.

Formula Used:

(i) Actual Discharge �� = +,� ��/��

Where, A - Area of the collecting tank = Lx B m2

y - Depth of collection cm

t - Time taken for ‘y’ m depth of collection Sec

L - Length of the collecting tank m

B - Breath of the collecting tank m

(ii) Co-efficient of discharge �� =-.-/ �� − Theoretical discharge (LPM)

Procedure:

1. Switch on the motor and the delivery valve is opened

2. Adjust the delivery valve to control the rate in the pipe

3. Set the flow rate in the Rotometer, for example say 50 liters per minute

4. Note down the time taken for 10 cm rise in collecting tank

5. Repeat the experiment for different set of Rotometer readings

6. Tabular column is drawn and readings are noted.

DETERMINATION OF CO-EFFICIENT OF DISCHARGE

ROTAMETER

12

Model Calculations:

(i) Actual Discharge �� = +,� �

2345

�� =

(ii) Co-efficient of discharge �� =-.-/ �� =

13

Precautions:




Result:

The Co-efficient of discharge of Rotameter( Cd ) from calculation =

15

Ex.No:

Date:

Aim:

To determine the Darcy’s friction factor for the given set of pipes and to study

variation of Reynolds’s number under varying flow conditions.

Apparatus Required:


2. Stop watch

3. Steel rule


Description:

When a fluid flows through a pipe, it experiences a resistance to flow due to the

friction and obstacles. The velocity of the fluid layer adjacent to the pipe wall is zero. The

velocity goes on increasing from the wall and thus velocity gradient. Hence shear stresses

are produced in the whole fluid due to viscosity. This viscous action causes loss of energy

which is usually known as frictional loss. This frictional loss depends on friction factor,

length of flow, diameter of pipe and velocity of flow. Experimentally we can find out the

friction factor by conducting an experiment.

Formula Used:

i) Manometric difference of mercury, ℎ� = (ℎ� − ℎ�) ∗ 10��6789

ii) Head loss due to Friction ℎ = ℎ� �� − 1!� of water

Where, S1 = Specific gravity of mercury


iii) Actual Discharge �� = +,� ��/��

Where, A - Area of the collecting tank = Lx B m2

y - Depth of collection cm

t - Time taken for ‘y’ m depth of collection Sec

L - Length of the collecting tank m

B - Breath of the collecting tank m

DETERMINATION OF FRICTION FACTOR FOR GIVEN SET OF

PIPES

16

Diameter of the pipe d =

Length of the pipe l =



Height of water collection y =

Tabulation:

S.

No.


ℎ = ℎ� �� − 1� of water

Time for ‘y’

�� rise (t) Sec

Actual

Discharge(��) ��/��

Velocity (V)

�/��

V2

��

Co-efficient of

friction

‘f'’ ℎ�� ℎ�� ℎ� =

(ℎ� − ℎ�)10��

17

Model Calculations:

1) Manometric difference of mercury, ℎ� = (ℎ� − ℎ�)10��6789

ℎ� =

2) Head loss due to Friction, ℎ: = ℎ� �� − 1!� of water

ℎ: =

3) Actual Discharge �� = +,� ��/��

�� =

4) Actual velocity of flow ; = -.� �/��

; =

5) Friction Factor 7 = �#�$<=>

7 =

6) Reynolds’s number, ?4 = ;&/@

?4 =

19

iv) Actual velocity of flow ; = -.� m/sec

Where, Qa - Actual Discharge m3/sec

a - Cross sectional area of the pipe m2

v) Friction Factor 7 = �#�$<=>

Where, hf - Loss of head due to friction m of water

l - Length of pipe m

d - Diameter of pipe m

V -Velocity of flow m/sec

g - Acceleration due to gravity

vi) Reynold’s number, Re ?4 = ;&/@ Where, V - Velocity of flow m/Sec

d - Diameter of pipe m

@ - Kinematic viscosity of water

Procedure:

1. Length of the pipe, Diameter of the pipe, size of the collecting tank are observed and

noted.

2. Start the motor and the flow is admitted in to the pipe by opening the inlet valve.

3. After flushing the manometer, stop cocks are set to read position.

4. Adjust the gate valves to maintain the same level in the manometer limbs.

5. Adjust the gate valves to a certain pressure in the manometer and the left limb & right limb

readings of the manometers are noted.

6. The exit valve of the collecting tank is closed and time taken for 10cm rise of water is noted

using stopwatch.

7. The outlet of the collecting tank is opened immediately after taking reading to avoid

overflow of the tank.

8. The steps 5 & 6 are repeated by varying the inlet valve opening there by varying the

discharge.

9. After sufficient readings are taken, the inlet valve is closed.

10. From the readings Velocity of flow, Reynolds’s number and friction factor are find

calculated.

21

Precautions:

• Care should be taken while operating the manometer, cocks are should be used to

avoid loss of mercury which may enter the pipe line.


• The exit valve of the collecting tank should be completely closed while the time

taken for 10cm rise of water is noted.

Graph:

From the observations made the following graphs are drawn

(i) Re vs f

(ii) V2 vs hf

Result:

The variation of friction factor with varying Reynold’s number (Re) has been studied.

The average value of friction factor (f) is found as _________________

22

Observations:

Length of the collecting tank L = Breath of the collecting tank B = Height of water collection y =

Correction Head Hc =

Tabulation:

S.

No

Delivery Pr.

Gauge

reading Pd

A97/��

Vacuum

Gauge

reading Pv

mm of Hg

Total Head

‘H’

m of water

Actual

Discharge

(Qa)

m3/sec

Time for 10

cm raise

(T) in Sec

Time taken for

10 revolutions

of energy

meter disc

‘t’ sec

Input

power

kW

Output

power

kW

Efficiency

of the

centrifugal

pump

%

23

Aim:

To conduct an experiment and to draw the characteristics curves of the given

centrifugal pump and to find the best operating condition.

Apparatus Required:

1. Stop watch

2. Steel rule

Description:

The hydraulic machines which convert the mechanical energy into hydraulic energy (a

form of pressure energy) are called pumps. If this energy conversion achieved by means of

centrifugal force acting on the fluid, the hydraulic machine is called centrifugal pump. The

centrifugal pump works on the principle of forced vortex flow which means a certain mass of

liquid is rotated by an external torque, the rise in pressure head of the rotating liquid takes

place. The rise in pressure heads at any point of the rotating liquid is proportional to the square

of tangential velocity of the liquid at that point.

A centrifugal pump consists of impeller, casing, suction pipe with foot valve and

strainer and delivery line.

Formula used:

(i) Actual discharge �� = +,� m3/sec

Where,

A-Area of the collecting tank = (Lx B) m2

B- Breath of the Tank m

L- Lenght of the Tank m

y- Rise of water level in the collecting tank m

t- Time taken for collecting ‘y’ m of fluid Sec

Ex.No:

Date:

PERFORMANCE STUDY OF SINGLE STAGE CENTRIFUGAL PUMP

24

Model Calculations:

1. Actual discharge �� = +,� ��/��

�� =

�� =

2. Input Power to the centrifugal pump BCD = �E**FGHI/IJK�

BCD =

BCD =

3. Output power BLM� = N#-.O�*** AP

�Q�RS6Tℎ�'&83 =BU ��6789 = � VW�***! 13.6�67['R�\=

]�^S_�\`ℎ�'&8� = B3 a#:5� = B3 ∗ 10.34�67['R�\ = ;�^6�SR`ℎ�'&8U = b>c �# d − b>e �# d�67['R�\

= - �# f� �

+c ! –� �+e h =

�6\\��RS6Tℎ�'&85 = �67['R�\

i\S�RS6Tℎ�'&8: = b):=>c �#� d + b):=>e �#� d �67['R�\ =

k6R'^ℎ�'&8 = 83 +8� +8U +85 +8:

8 = 4. Overall Efficiency of the pump lLU4m�== = bLM�nM�nLo4mCDnM�nLo4m d ∗ 100% lLU4m�===

25

(ii) Input Power to the centrifugal pump BCD = �E**FGHI/IJK�

Where

N- Number of Revolution of the energy meter disc counted rpm

motor – Efficiency of Electrical Mot

R -Energy meter constant

t - Time taken for N revolutions of the energy meter disc sec

(iii) Output power BLM� = N#-.O�*** AP

Pout = 9.81��8 kW

Where

– Density of the pumping fluid kg/m3

g – Acceleration due to gravity m2/sec

Qa – actual discharge m3/sec

H – Total head to be pumped m of water

H = (Suction head + Delivery head + Net velocity head + Correction Head +Frictional head)

�Q�RS6Tℎ�'&83 =BU ��6789 = � VW�***! 13.6�67['R�\

BU − ;'�QQ�9'Q9�\�'&ST9��6789 ]�^S_�\`ℎ�'&8� = B3 A97�� = B3 ∗ 10.34�67['R�\ BU − ]�^S_�\`s\��Q\�9'Q9�\�'&ST9 A97��

;�^6�SR`ℎ�'&8U = b>c �# d − b>e �# d�67['R�\

= - �# f� �

+c ! –� �+e h =

Qa – Actual discharge m3/sec

As – Cross sectional area of the suction pipe m2

Ad – Cross sectional area of the delivery pipe m2

Correction head Hc = The distance between Vacuum gauge and delivery pressure gauge

m

k6R'^ℎ�'&8 = 83 +8� +8U +85 +8: m of water

27

Frictional head =b):=>c �#� d +b):=>e

�#� d

f- Frictional factor

l- Total length of the pipe line m

Vs -Velocity in suction pipe = Qa /As m/sec

Vd -Velocity in delivery pipe = Qa /Ad m/sec

g - Acceleration due to gravity m2/sec

(iv) Overall Efficiency of the pump lLU4m�== = bLM�nM�nLo4mCDnM�nLo4m d ∗ 100%

Procedure:

1. The pump setup is studied and the details of pump size, collecting tank size, diameter of

delivery pipe, diameter of suction pipe are noted.

2. The correction head and energy meter constant are noted.

3. Difference of level between the pressure gauge and vacuum gauge is noted.

4. Priming of the pump is done.

5. Pump is started and delivery value is brought to fully opened condition.

6. The following readings are noted

(i) The delivery pressure gauge reading

(ii) The suction vacuum gauge reading

(iii) Time taken for 10 revolutions of the energy meter disc.

(iv) Time taken for 10cm raise of fluid in the collecting tank.

7. Several sets of readings are taken by varying the delivery valve position from fully open

position to shut off position.

8. The motor is stopped the correction head is recorded.

9. From the readings taken efficiency of the centrifugal pump is calculated and graphs are

drawn.

29

Graph:

The tabulated results following graphs are drawn

i) Discharge [m³/sec] vs Overall efficiency

ii) Discharge vs Total head.

iii) Discharge vs Input power

iv) Discharge vs Output power

Result:

Thus the performance characteristics of the given single stage centrifugal pump is

observed and the corresponding graphs are drawn.

Maximum efficiency of pump =

Head at maximum efficiency =

Head at maximum output power =

Efficiency at maximum output power =

30

Observations:

Area of the collecting Tank (A) = m2

Depth of the liquid in the Tank (Y) = m

Correction Head (Hc) = m of water

Diameter of the Piston (D) = m

Stroke length (L) = m

Cross sectional area of the piston (AP) = m2

Energy meter constant (R) =

Diameter of the Suction pipe (ds) = m

Diameter of the Suction pipe (dd) = m

31

Aim:

To conduct an experiment and to determine the co efficient of discharge, Slip and

efficiency of the given reciprocating pump.

Apparatus Required:

1. Steel rule

2. Stop watch

Description:

A pump is a device used for lifting liquids from a lower level to a higher level. It

increases the pressure energy of the liquid in a closed system. Reciprocating pump is a positive

displacement plunger pump. The reciprocating pump increases the pressure energy of the

liquid by means of reciprocating motion of the piston or plunger. To and fro motion of the

piston or plunger inside the cylinder draws the fluid and forces it out of the cylinder. It is often

used where relatively small quantity of liquid is to be handled and where delivery pressure is

quite large. The pump delivers reliable discharge flows and is often used for metering duties

delivering accurate quantities of fluid. The reciprocating pump is not tolerant to solid particles.

There are two general types of reciprocating pumps. The piston pump and the

diaphragm pump

Formula Used:

1. Actual discharge �� = t`/R m3/sec

Where,






Ex.No:

Date : PERFORMANCE STUDY OF RECIPROCATING PUMP

32

Tabulation:

S.No

Suction

Head

(Hs )

Delivery

Head (Hd )

Total

Head

(H)

m of

water

Time

to ‘y’

m of

level

raise

t sec

Time for

10

revolution

of energy

meter disc

T sec

Actual

Discharge

(Qa)

m3/sec

Speed

(N)

rpm

Theoretical

Discharge

(Qt)

m3/sec

Co

efficient

of

discharge

Cd

%

Slip

Input

Power

(Pinput)

kW

Output

power

(Poutput)

kW

Efficiency

of the

pump

l %

mm

of

Hg

m of

water

mm

of

Hg

m of

water

33

2. Theoretical Discharge ��utnvw/60 Where,

AP = π/4 D2 - Cross Sectional area of the piston m2

D - Diameter of the piston m

L - Stroke length m

N - Crank speed rpm

3. Slip (S) = (Theoretical discharge Qt - Actual discharge Qa)

Percentage of Slip (%S) = [(Qt – Qa) / Qt ] 100

4. Volumetric efficiency = (Qa/Qt) X 100

5. Input Power to the reciprocating pump BCD = �E**FGHI/IJK� AP

Where


motor – Efficiency of Electrical Mot


T - Time taken for N revolutions of the energy meter disc sec

6. Output power BLM� = N#-.O�*** AP

Pout = 9.81��8 kW

Where

x – Density of the pumping fluid kg/m3




H = (Suction head + Delivery head + Velocity head + Correction Head +Frictional head)

Total Head H = (Hs + Hd + Hv + Hc + Hf )

Suction head Hs = Pv mm of Hg = ( Pv /1000) 13.6 m of water

Pv – Vaccuum gauge reading mm of Hg

Delivery Head Hd = Ps Kgf/ cm2 = Ps x 10.34 m of water

Pd - Delivery pressure gauge reading kgf/cm2

34

Model Calculations:

1. Actual discharge Qa = ( A y / t ) m3/sec

Qa =

Qa =

2. Theoretical Discharge Qt = AP LN /60

Qt =

Qt =

3. Slip (S) = (Theoretical discharge Qt - Actual discharge Qa)

Percentage of Slip (%S) = [(Qt – Qa) / Qt ] 100

4. % Volumetric efficiency v = (Qa/Qt) X 100

5. Input Power to the reciprocating pump BCD = �E**FGHI/IJK� AP

BCD =

6. Output power Pout = gQaH /1000 kW

Pout = 9.81 Qa H kW

�Q�RS6Tℎ�'&83 =BU ��6789 =� VW�***! 13.6�67['R�\=

]�^S_�\`ℎ�'&8� = B3 a#:5� = B3 ∗ 10.34�67['R�\ = ;�^6�SR`ℎ�'&8U = b>c �# d − b>e �# d�67['R�\

= - �# f� �

+c ! –� �+e h =

�6\\��RS6Tℎ�'&85 = �67['R�\

35

;�^6�SR`ℎ�'&8U = b>c �# d − b>e �# d �67['R�\ =

- �# f� �

+c ! –��+e h




i\S�RS6Tℎ�'&8: = y47^;3�

29& { + y47^;��29& { �67['R�\ f- Frictional factor





Correction head Hc = The distance between Vacuum gauge and delivery pressure gauge m

m

Total Head H = (Hs + Hd + Hv + Hc + Hf ) m of water

7. Overall % Efficiency of the pump = [Output power / Input power ] x 100%

Procedure:

1. The pump setup is studied and the details of pump size, collecting tank size, diameter

of delivery pipe, diameter of suction pipe are noted.



4. Delivery value is brought to fully opened condition and pump is started.


i.The delivery pressure gauge reading

ii.The suction vacuum gauge reading

iii.Time taken for 10 revolutions of the energy meter disc.




8. From the readings taken efficiency of the reciprocating pump is calculated and graphs

are drawn.

36

i\S�RS6Tℎ�'&8: = b):=>c �#� d + b):=>e �#� d �67['R�\ =

k6R'^ℎ�'&8 = 83 + 8� +8U + 85 +8:

8 =

Total Head H =

Pout =

7. Overall Efficiency of the pump = [Output power / Input power ] x 100%

Overall Efficiency of the pump =

8. Co efficient of discharge Cd = Qa / Qt

Cd =

37

Graph:

From the observations made the following graph is plotted

(i) Total Head vs ٪ Efficiency

(ii) Discharge vs Total Head (H)

(iii) Discharge vs Out put power

(iv) Discharge vs ٪ Efficiency

Result:

Thus the performance characteristics of the given single stage reciprocating pump

is observed and the corresponding graphs are drawn.

38

Observations:

Length of the collecting tank L = Breath of the collecting tank B = Height of water collection y =

Correction Head Hc =

Tabulation:

S.

No

Delivery

Pressure

Gauge

reading

Pd

A97/��

Suction

Vacuum

Gauge

reading

Pv

mm of Hg

Total Head

‘H’

m of water

Actual

Discharge

(Qa) m3/sec

Time for 10 cm

raise of oil

(T) in Sec

Time taken for 10

revolutions of

energy meter disc

‘t’ sec

Input power

kW

Output

power

kW

Efficiency of

the gear

oil pump

%

39

Aim:

To conduct an experiment and to draw the characteristics curves of the given gear

oil pump to find out the maximum efficiency of the pump.

Apparatus Required:

Stop watch

Steel rule

Description:

Gear oil pump consists of identical intermeshing spur pinions working inside a

casing with a fine clearance. One of the pinions is keyed to a driving shaft and the other

revolves idly. The space between the teeth and the casing is filled with oil. The oil is carried

round between the gears from the suction pipe to the delivery pipe. The oil pushed into the

delivery side cannot slip back into the inlet side due to the meshing of the gears.

Formula Used:

1. Actual discharge Qa = ( A y /t ) m3/sec

Where,






2. Input Power to the gear oil pump BCD = �E**FGHI/IJK� AP

Where,


motor – Efficiency of Electrical Motor


T - Time taken for N revolutions of the energy meter disc sec

Ex.No:

Date : PERFORMANCE STUDY OF GEAR OIL PUMP

40

Model Calculations:

1. Actual discharge Qa = ( A y /t ) m3/sec

Qa =

Qa =

2. Input Power to the gear oil pump BCD = �E**FGHI/IJK� AP

3. Output power Pout = 9.81 Qa H /1000 kW



Velocity head Hv = [Vs2 / 2g ] -[Vd

2 / 2g ] m of water

= Q2 /2g [ (1/As2) – (1/Ad

2)]

Correction head Hc = m of water

Total Head H = (Hs + Hd + Hv + Hc + Hf )

H =

4. Overall Efficiency of the pump = [Output power / Input power ] x 100%

41

3. Output power Pout = gQa H /1000 kW

Pout = 9.81 Qa H kW

Where

– Density of the pumping fluid kg/m3


Q – actual discharge m3/sec


H = (Suction head + Delivery head + Velocity head + Correction Head +Frictional head)


Pv – Vaccuum gauge reading mm of Hg


Pd - Delivery pressure gauge reading kgf/cm2

Velocity head Hv = [Vs2 / 2g ] -[Vd

2 / 2g ] m of water

= Qa2 /2g [ (1/As

2) – (1/Ad2)]




Frictional head = [4f l (Vs)2 / 2gd ] + [4f l (Vd)

2 / 2gd ]

f- Frictional factor





Correction head Hc = The distance between Vacuum gauge and delivery pressure gauge

m

Total Head H = (Hs + Hd + Hv + Hc + Hf ) m of water

4. Overall Efficiency of the pump = [Output power / Input power] x 100%

43

Procedure:

1. The pump setup is studied and the details of pump size, collecting tank size, diameter

of delivery pipe, diameter of suction pipe are noted.



4. Fill up the supply tank with oil to the required height. (3/4th of the tank)

5. Pump is started and delivery value is adjusted to get required head.


i. The delivery pressure gauge reading

ii. The suction vacuum gauge reading

iii. Time taken for 10 revolutions of the energy meter disc.

iv. Time taken for 10cm raise of fluid in the collecting tank.




9. From the readings taken efficiency of the centrifugal pump is calculated and graphs are

drawn.

Graph:

The following graphs are drawn

Discharge [m³/sec] vs Overall efficiency

Discharge vs Total head.

Discharge vs Input power

Result:

Thus the performance characteristics of the given gear oil pump is studied and the

corresponding graphs are drawn.

Maximum efficiency of pump =

Discharge at maximum Head =

Efficiency at maximum Head =

Input power maximum Head =

44

Observations:

Break drum diameter DB = Thickness of the belt tB = m

Effective radius of the break drum Reffective = (DB/2) + tB = m Inlet pipe diameter dp= m

Tabulation:

S.

No

Inlet

Pressur

e Gauge

reading

(P)

Kgf/cm2

Out let

Vacuum

gauge

reading

(Pv )

mm of

Hg

Inlet

Head

(H)

m of

wate

r

Orifice meter reading

Actual

Discharg

e (Qa)

m3/sec

Speed

(N)

rpm

Left

Spring

Balance

reading

(MS1)

Right

Spring

Balance

reading

(MS2)

Net

load

on the

turbine

(WNet )

N

Torque(T)

N-m

Input

Power

to

turbine

(Pinput)

kW

Out

put

power

from

turbine

(Poutput

)

kW

%

Efficienc

y of the

Francis

Turbine

Orifice

meter

Inlet

Pressur

e (P1 )

kgf/cm2

Orifice

meter

outlet

Pressur

e (P2 )

kgf/cm2

(P1 -P2)

kgf/cm2

Orifice

Head

(h)

h= (P1

- P2)

x10

m of

water

45

Aim:

To study the main characteristics of the given Pelton wheel turbine under constant

head and to draw the main characteristic curves.

Apparatus required:

1. Orifice meter

2. Vacuum gauge

3. Tachometer

4. Pressure gauges

5. Spring balances

Description:

Pelton turbine is an impulse turbine, which utilise high heads of fluid for generation of

electricity. All the available pressure head is converted into velocity energy by means of a

spear and nozzle arrangement. The water leaves the nozzle in a jet formation. The jet of

water then strikes the buckets of the Pelton wheel runner. These buckets are in the shape

of double cups, joined at the middle portion in a knife edge. The jet strikes the knife edge

of the buckets with least resistance and shock. Then the jet glides along the path of the cup,

and the jet is deflected through more than 1600 to 1700. While passing along the buckets,

water is deflected causing a change in momentum of the water jet and hence an impulsive

force is supplied to the cups. As a result, the cups attached to the runner moves, which in

turn rotate the shaft. The specific speed of the Pelton wheel varies from 10 to 100.

The Pelton wheel is supplied with water under high pressure by a centrifugal pump.

The water is flows through an orificemeter to the Pelton wheel. A gate valve is used to

control the flow rate to the turbine. The orificemeter with pressure gauges connected to it

is used to determine the flow rate of water in the pipe. The nozzle opening can be

decreased or increased by operating the spear wheel at the entrance side of turbine.

The turbine is loaded by applying load on the brake drum. This is done by means of

spring balance and screed rod arrangement fitted to the frame. The inlet head is read from

the pressure gauge. The speed of the turbine is measured with a tachometer

Ex.No:

Date :

PERFORMANCE STUDY OF PELTON WHEEL TURBINE

46

Model Calculations:

1. Actual Discharge�� = |e�� "�#$%��

�� =

�� =

2. Input Power Pinput = 9.81 Qa H kW

Hp = (Px 10.34) + [Pv /1000) x 13.6] m of water

Hv = [V2/2g] = [Qa

2/2g] (1/ A)

Pinput =

Pinput =

3. Power output of the pelton wheel (Poutput) =2πN T/60 x 1000 kW

Wnet = [(MS1 - MS2 ) x 0.25] x 9.81

Wnet =

T = (Wnet x Reffective ) =

T =

.

47

Formula used:

1. Actual Discharge �� = |e�� "�#$%��

Where, Cd- Co efficient of discharge of the Orifice meter

a1 = π/4 (d1)2- Cross sectional area of inlet pipe of orifice meter m2

a2 = π/4 (d2)2- Cross sectional area of orifice m2

h - Orifice head = (P1 –P2 ) x 10.34 m of water

g –Acceleration due to gravity m/s2

P1 – Orifice meter inlet Pressure gauge reading kg/cm2

P2 – Orifice meter outlet Pressure gauge reading kg/cm2

2. Input Power BCDnM� = g Qa H /1000 kW

BCDnM� = 9.81 Qa H kW

Where, – Density of the pumping fluid kg/m3


Qa – Actual volume of water strikes on the pelton wheel m3/sec

H – Total head on the pelton wheel m of water

Total Head H = (Hp + Hv) m of water


Hv = [V2/2g] = [Qa

2/2g] (1/ A)

A- Cross sectional area of the inlet pipe to turbine m2

48

3. Poutput = 2πN T/60 x 1000 kW

Poutput =

Poutput = kW

4. Overall Efficiency of the pelton wheellLU4m�== = bLM�nM�nLo4mCDnM�nLo4m d ∗ 100%

Overall Efficiency =

5. Unit speed wM = w/√8

6. Unit Power BM = V~��/O2

7. Unit Discharge �M = �/√8

8. Specific Speed w3 =F"VI�/��/O��

49

3. Power output of the pelton wheel (Poutput) =2πN T/60 x 1000 kW

Where, N- Speed of the turbine rpm

T = (Wnet x Reffective ) -Torque produced in the turbine N-m

Wnet = [(MS1 - MS2 ) x 0.25] x 9.81 N

Ms1 = Reading of the spring balance 1 kg


Reffective = (DB + tB ) –Effective radius of the break drum m

DB – Diameter of the Break drum m

tB – Thickness of the belt m

4. Overall Efficiency of the Pelton wheel = [Output power / Input power ] x 100%





Where N- Speed of the turbine rpm

Procedure:

1. Prime the pump if necessary and close the delivery gate valve completely

2. The pump is started and the discharge is directed on to the Pelton wheel.

3. After the motor starter changed to delta mode and the motor is running at rated speed,

the inlet gate valve (3/4 G.O Position) is adjusted for the required head.

4. For the noted constant head the following readings are noted

(i) Inlet pressure gauge reading (P)

(ii) Vacuum pressure gauge reading (Pv)

(iii) Shaft speed (N)

(iv) Orifice meter pressure gauge reading (P1 & P2)

(v) Dead weight of the hanger

(vi) Spring balance readings

5. Keeping the constant head, the experiment is repeated and readings are noted for

different load conditions on the turbine.

6. By changing the Gate opening (1/2 , 1/4 & Full G.O) the experiment is repeated.

51

7. The readings are tabulated and calculation is done to find out various performance

characteristics.

8. The characteristic curves are drawn by plotting speed along X-axis and variables

along Y-axis.

9. The following results are noted from the graph

(i) Maximum efficiency

(ii) Unit speed at maximum efficiency

(iii) Unit Power at maximum efficiency

Graph:


Unit speed vs Efficiency

Unit speed vs Unit power

Unit speed vs Unit discharge

Result:

Thus the main characteristics of the Pelton wheel turbine are experimentally studied

under constant head and the main characteristic curves are drawn.

Maximum efficiency of the turbine =

Unit Speed for maximum efficiency =

Unit power for maximum efficiency =

52

Observations:


Effective radius of the break drum Reffective = (DB/2) + tB = m Inlet pipe diameter dp= m

Tabulation:

S.

No

Inlet

Pressur

e Gauge

reading

(P)

Kgf/cm2

Out let

Vacuum

gauge

reading

(Pv )

mm of

Hg

Inlet

Head

(H)

m of

wate

r


Actual

Discharg

e (Qa)

m3/sec

Speed

(N)

rpm

Left

Spring

Balance

reading

(MS1)

Right

Spring

Balance

reading

(MS2)

Net

load

on the

turbine

(WNet )

N

Torque(T)

N-m

Input

Power

to

turbine

(Pinput)

kW

Out

put

power

from

turbine

(Poutput

)

kW

%

Efficienc

y of the

Francis

Turbine

Orifice

meter

Inlet

Pressur

e (P1 )

kgf/cm2

Orifice

meter

outlet

Pressur

e (P2 )

kgf/cm2

(P1 - P2)

kgf/cm2

Orifice

Head

(h)

h= (P1

- P2)

x10

m of

water

53

Aim:

To study the main characteristics of the given Francis turbine under constant head and

to draw the main characteristic curves.

Apparatus required:

1. Orifice meter

2. Vacuum gauge

3. Tachometer

4. Pressure gauges

5. Spring Balance-2 No.

Description:

Francis turbine is a reaction turbine, used in dams and reservoirs of medium height

to convert hydraulic energy into mechanical energy and subsequently into electrical

energy. Francis turbine is a radial inward flow reaction turbine. This has advantages of

centrifugal forces acting against the flow, thus reducing the tendency of turbine to over

speed. Francis turbines are best for medium heads, say 40 to 300m. The Specific speed

rangers than 25 to 300.

The turbine test rig consist of 3.72kw (5HP) turbine supplied with water from a

suitable 15 HP centrifugal pump through suitable pipelines. Sluice valve and a flow

measuring orificemeter. The turbine consists of a cast iron body with a volute casing and a

gunmetal runner consisting of two shrouds with aerofoil shaped curved vanes in between.

The runner is surrounded by a ring of adjustable gunmetal guide vanes. These vanes can be

rotated about their axis by a hand wheel & their position is indicated by a pair of dummy

guide vanes fixed outside the turbine casing. At the outlet, a draft tube is provided to

increase the net head across the turbine. The runner is attached to an output shaft with a

brake drum to absorb the energy produced.

Water under pressure from pump enters through guide vanes into runner. While

passing through the spiral casing and guide vanes, a portion of the pressure energy is

converted in to velocity energy. Water thus enters the runner at a high velocity and as it

passes through runner vanes, the remaining pressure energy is converted in to kinetic

energy & Mechanical energy. ie. The water head is converted in to mechanical energy and

hence the runner rotates. The water from the runner is then discharged into tailrace. The

discharge through the runner can be regulated by operating guide vanes also.

Ex.No:

Date :

PERFORMANCE STUDY OF FRANICS TURBINE

54

Model Calculations:


�� =

�� =


8n = (B ∗ 10.34) + f� BU1000 ∗ 13.6h �67['R�\

Hv = [V2/2g] = [Qa

2/2g] (1/ A)

Pinput =

Pinput =

3. Power output of the Francis Turbine (Poutput) =2πN T/60 x 1000 Kw

Wnet = [(MS1 - MS2 ) x 0.25] x 9.81

Wnet =


T =

55

The flow through the pipe lines into the turbine is measured with the orificemeter

fitted in the pipe line. The orificemeter is accompanied with pressure gauges. The net

pressure difference across the turbine inlet and exit is measured with a pressure gauge and

vacuum gauge. The turbine output torque is determined with a rope brake. A Tachometer

is used to measure the speed (rpm).

The turbine is loaded by applying load on the brake drum. This is done by means of

spring balance and screed rod arrangement fitted to the frame. The inlet head is read from

the pressure gauge. The speed of the turbine is measured with a tachometer.

Formula used:









2. Input Power (Pinput) = g Qa H /1000 kW

Pinput = 9.81 Qa H kW



Qa – Actual volume of water strikes on the Francis turbine m3/sec

H – Total head on the Francis turbine m of water



Hv = [V2/2g] = [Qa

2/2g] (1/ A)


56

4. Overall Efficiency of the Francis turbine = [Output power / Input power ] x 100%







57

3. Power output of the Francis turbine (Poutput) =2πN T/60 x 1000 kW



Wnet = [(MS1 - MS2 ) x 0.25] x 9.81 N






4. Overall Efficiency of the Francis turbine = [Output power / Input power ] x 100%






59

Procedure:


2. The pump is started and the discharge is directed on to the Francis turbine.

3. After the motor starter changed to delta mode and the motor is running at rated speed,

the inlet gate valve (3/4 G.O) is adjusted for the required head.








5. Keeping the constant head, the experiment is repeated and readings are noted for

different load conditions on the turbine.

6. By changing the Gate opening (1/2, 1/4 & full G.O) the experiment is repeated.


characteristics.

8. The characteristic curves are drawn by plotting speed along X-axis and variables along

Y-axis.


(i) Maximum efficiency (ii) Unit at maximum efficiency

(iii) Unit power at maximum efficiency

Graph:

Using the tabulated results following graphs are plotted

Unit speed vs Efficiency Unit speed vs Unit power


Result:

Thus the main characteristics of the Francis turbine are experimentally studied under

constant head and the main characteristic curves are drawn.

Maximum efficiency of the turbine = Unit Speed for maximum efficiency = Unit power for maximum efficiency =

60

Observations:


Effective radius of the break drum Reffective = (DB/2) + tB = m

Tabulation:

S.

No

Inlet

Pressur

e Gauge

reading

(P)

Kgf/cm2

Out let

Vacuum

gauge

reading

(Pv )

mm of

Hg

Inlet

Head

(H)

m of

wate

r


Actual

Discharg

e (Qa)

m3/sec

Speed

(N)

rpm

Left

Spring

Balance

reading

(MS1)

Right

Spring

Balance

reading

(MS2)

Net

load

on the

turbine

(WNet )

N

Torque(T)

N-m

Input

Power

to

turbine

(Pinput)

kW

Out

put

power

from

turbine

(Poutput

)

kW

%

Efficienc

y of the

Kaplan

Turbine

Orifice

meter

Inlet

Pressur

e (P1 )

kgf/cm2

Orifice

meter

outlet

Pressur

e (P2 )

kgf/cm2

(P1 -P2)

kgf/cm2

Orifice

Head

(h)

h= (P1

- P2)

x10

m of

water

61

Aim:

To study the main characteristics of the given Kaplan turbine under constant head and to

draw the main characteristic curves.

Apparatus required:

1. Orifice meter

2. Vacuum gauge

3. Tachometer

4. Pressure gauges

5. Spring balance-2No

Description:

Turbines are defined as the hydraulic machines which convert hydraulic energy into

mechanical energy. If the water flows parallel to the axis of the rotation of the shaft, and if the

head at the inlet of the turbine is the sum of pressure of pressure energy and kinetic energy and

during the flow of water through runner a part of pressure energy is converted into mechanical

energy the turbine is known as axial flow reaction turbine. There two types of axial flow

reaction turbines

1) Propeller turbine

The vanes are fixed to the hub and they are not adjustable.

2) Kaplan turbine

The vanes fitted to the hub are adjustable.

Axial flow reaction turbine is suitable where a large quantity of water at low head is available.

The specific speed of Kaplan or propeller turbine is 255 to 860.

The main parts of a Kaplan turbine are

1) Scroll casing

2) Guide vane mechanism

3) Hub with vanes or runner of the turbine and

4) Draft tube

The water from the penstock enters the scroll casing and then moves to the guide vanes,

the water turns through 900 and flows axially through runner.

PERFORMANCE STUDY OF KAPLAN TURBINE Ex.No:

Date :

62

Model Calculations:


Qa =

Qa =



Hv = [V2/2g] = [Qa

2/2g] (1/ A)

Pinput =

Pinput =

3. Power output of the Kaplan Turbine (Poutput) =2πN T/60 x 1000 kW

Wnet = [(MS1 - MS2 ) x 0.25] x 9.81

Wnet =


T =

63

Formula used:









2. Input Power (Pinput) = g Qa H /1000 kW

Pinput = 9.81 Qa H kW



Qa – Actual volume of water strikes on the Kaplan Turbine m3/sec

H – Total head on the Kaplan Turbine m of water



Hv = [V2/2g] = [Qa

2/2g] (1/ A)


3. Power output of the Kaplan Turbine (Poutput) =2πN T/60 x 1000 kW



Wnet = [(MS1 - MS2 ) x 0.25] x 9.81 N






64

4. Overall Efficiency of the Kaplan Turbine = [Output power / Input power] x 100%







65

4. Overall Efficiency of the Kaplan Turbine = [Output power / Input power] x 100%






Procedure:


2. The pump is started and the discharge is directed on to the Kaplan turbine.

3. After the motor starter changed to delta mode and the motor is running at rated speed, the

inlet gate valve (3/4 G.O Position) is adjusted for the required head.








5. Keeping the constant head, the experiment is repeated and readings are noted for different

load conditions on the turbine.

6. By changing the gate opening ( ½’ 1/4 & Full G.O) the experiments are repeated.


characteristics.

8. The characteristic curves are drawn by plotting speed along X-axis and variables along Y-

axis.


(i) Maximum efficiency (ii) Unit speed at maximum efficiency

(iii) Unit power at maximum efficiency

67

Graph:

From the tabulated result the following graphs are plotted

Unit speed vs Efficiency

Unit speed vs Unit power


Result:

Thus the main characteristics of the Kaplan turbine are experimentally studied under

constant head and the main characteristic curves are drawn.

Maximum efficiency of the turbine =

Unit Speed for maximum efficiency =

Unit power for maximum efficiency =

me2208 -fmm lab manual 1 -1 -...

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