fmm new lab (1) - copy
DESCRIPTION
FMM LAB MANUALTRANSCRIPT
DEPARTMENT OF MECHANICAL ENGINEERING
ANNA UNIVERSITY, CHENNAI
AFFILIATED INSTITUTION
REGULATION 2013
CE 6461 - FLUID MECHANICS AND MACHINERY LABORATORY
BATCH – 2014 – 2018
ACADEMIC YEAR: 2015-2016
YEAR / SEMESTER: II / IV
Prepared by: Verified by: Approved by: Name: Name: Name: Date: Date: Date:
Department of Mechanical Engineering-ACET Page | 1
GENERAL INSTRUCTIONS TO THE STUDENTS
1. Wear shoes and overcoat before entering in to the Laboratory.
2. Come with the observations/Manuals and the previous experiments getting
signed from the lab in charge, well in advance. Fail to do so, will not be
allowed to do the next experiment.
3. Have a clear idea about the experiment which has to be done at a particular
class.
4. Operate the equipments/instruments only in the presence of lab in charge/
lab technician.
Department of Mechanical Engineering-ACET Page | 2
CE6461 FLUID MECHANICS AND MACHINERY LABORATORY
SYLLABUS R - 2013
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/
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.
Department of Mechanical Engineering-ACET Page | 3
INDEX
S.NO.
DATE NAME OF THE EXPERIMENTPAGE NO.,
MARKS STAFF SIGN
1Determination of the Co-efficient of discharge of given venturi meter
6
2Determination of the Co-efficient of discharge of given orifice meter 11
3Calculation Of The Rate Of Flow Using Roto Meter 16
4Determination Of Friction Factor Of Given Set Of Pipes 19
5Characteristics Curves Of Centrifugal Pump
25
6Characteristics Curves Of Reciprocating Pump
32
7 Characteristics Curves Of Gear Pump 37
8 Characteristics Curves Of Pelton Wheel 42
9 Characteristics Curves Of Francis Turbine
46
10 Kaplan Turbine Test Rig 52
Completed date:
Average Mark: Staff - in - charge
Department of Mechanical Engineering-ACET Page | 4
DETERMINATION OF THE CO EFFICIENT OFDISCHARGE OF GIVEN VENTURIMETER
Exp No: 1
Date:
AIM:
To determine the coefficient of discharge for liquid flowing through venturimeter.
APPARATUS REQUIRED:
1. Venturimeter
2. Stop watch
3. Collecting tank
4. Differential U-tube
5. Manometer
6. Scale
FORMULAE:
1. ACTUAL DISCHARGE:
Q act = A x h / t (m3 / s)
2. THEORTICAL DISCHARGE:
Qth = a 1 x a 2 x Ö 2 g h / Ö a 12 – a 2
2 (m3 / s)
Where:
A = Area of collecting tank in m2
h = Height of collected water in tank = 10 cm
a 1 = Area of inlet pipe in m2
a 2 = Area of the throat in m2
g = Specify gravity in m / s2
t = Time taken for h cm rise of water
H = Orifice head in terms of flowing liquid = (H1 ~ H2) (s m /s 1 - 1)
Department of Mechanical Engineering-ACET Page | 5
Where:
H1 = Manometric head in first limb
H2 = Manometric head in second limb
s m = Specific gravity of Manometric liquid
(i.e.) Liquid mercury Hg = 13.6
s1 = Specific gravity of flowing liquid water = 1
3. CO EFFICENT OF DISCHARGE:
Co- efficient of discharge = Q act / Q th
DESCRIPTION
For routine practical measurements of fluid flows, there exists a plentiful supply of flow
meters and flow-measuring devices as shown below.
Flow meters and flow measuring devices
For closed conduit flows For open Channel flows
Positive displacement Differential measurement (types) (types) Weirs Multiple current meter
Reciprocating Rotating Rotary Venturi- Orifices Nozzles& Piston meter Disc meter Piston& meter Elbow meter Vane meters
No flow meter or measuring technique is fool proof & hence the calibration of instrument
is highly necessary. Calibration of venturimeter means that determination of coefficient of
discharge (i.e., Cd) which truly indicates the discrepancy between actual and real or theoretical
discharge. The following sketches depict the parts of a venturimeter & also its principles of
construction:
Department of Mechanical Engineering-ACET Page | 6
Schematic of a venturimeter
The pressure difference between 1 and 2 is measured by the differential mercury
manometer. Venturimeter is highly applicable for the computation of flow rates in the closed
Pipes, including the measurement of gas flow rates. They yield a very high coefficient of discharge
(i.e., 0.95 to 0.99). Because of their constructional aspects and no suitability in congested spaces,
other flow meter are used.
PROCEDURE:
1. The pipe is selected for doing experiments
2. The motor is switched on, as a result water will flow
3. According to the flow, the mercury level fluctuates in the U-tube manometer
4. The reading of H1 and H2 are noted
5. The time taken for 10 cm rise of water in the collecting tank is noted
6. The experiment is repeated for various flow in the same pipe
7. The co-efficient of discharge is calculated
Department of Mechanical Engineering-ACET Page | 7
Ob
serv
atio
ns
Len
gth
of c
olle
ctin
g ta
nk =
L =
m
, b
read
th o
f co
llec
ting
tank
= B
m,
Pla
n ar
ea o
f ta
nk =
A =
L x
B =
m
2 .
Tab
ula
tion
s
Exp
erim
enta
l dat
a p
erta
inin
g to
Ven
turi
met
er 1
(i.e
., at
tach
ed t
o P
ipe
1)
Inle
t dia
met
er o
f V
entu
rim
eter
1 =
Pip
e 1
dia
= d
1 =
m
.
Thr
oat d
iam
eter
of
vent
urim
eter
1 =
d2 =
m
C/s
are
a of
inle
t = a
1 =
m
2
C/s
are
a of
thro
at =
a2 =
m
2
Co-
effi
cien
t of
d
isch
arge
C
d
(no
un
it)
Th
eore
tica
l d
isch
arge
Q
th
in m
3 / s
M
ean
Cd
=
Act
ual
d
isch
arge
Q
act
in m
3 / s
Tim
e ta
ken
for
h
cm
ris
e of
wat
er t
in s
ec
Man
omet
ric
hea
d
H=
(H1~
H2)
x 1
2.6
in m
of
wat
er
Man
omet
ric
read
ing
H2
cm
of H
gH
1 cm
of
Hg
Dia
met
er
in m
m
S.n
o
GRAPH :
Department of Mechanical Engineering-ACET Page | 8
Coefficient of discharge from the graph of Qa v/s Qth:
Slope = Cd = Constant.
Qact
Qth
Coefficient of discharge from the graph = Cd =
RESULT
Coefficient of discharge of the venturimeter (Cd)
by direct computation = ___________
by graph. = ___________
DETERMINATION OF THE CO-EFFICIENT OFDISCHARGE OF GIVEN ORIFICE METER
Department of Mechanical Engineering-ACET Page | 9
Exp No : 2Date :
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. Scale
FORMULAE :
1. ACTUAL DISCHARGE:
Q act = A x h / t (m3 / s)
2. THEORTICAL DISCHARGE:
Q th = a 1 x a 0 x Ö 2 g h / Ö a 12 – a 0
2 (m3 / s)
Where:
A = Area of collecting tank in m2
h = Height of collected water in tank = 10 cm
a 1 = Area of inlet pipe in, m2
a 0 = Area of the orifice in m2
g = Specify gravity in m / s2
t = Time taken for h cm rise of water
H = Orifice head in terms of flowing liquid = (H1 ~ H2) (s m / s 1 - 1)
Where:
H1 = Manometric head in first limb
Department of Mechanical Engineering-ACET Page | 10
H2 = Manometric head in second limb
s m = Specific gravity of Manometric liquid
(i.e.) Liquid mercury Hg = 13.6
s1 = Specific gravity of flowing liquid water = 1
3. CO EFFICENT OF DISCHARGE:
Co- efficient of discharge, Cd = Q act / Q th
DESCRIPTION:
For routine practical measurements of fluid flows, there exists umpteen supply of
flow meters and flow-measuring techniques as mentioned in the previous experiment (Refer the
venturimeter Expt.). Calibration of orifice meter means that determination of coefficient of
discharge (i.e., Cd) which reveals the difference between actual and theoretical discharge. The
following sketches depict the orifice and also its principle of construction.
Schematic of streamlines in an Orifice meter(During fluid flow)
Although the basic principle for both venturimeter and orifice meter is somewhat same, the
flow separation and energy dissipation is predominant in orifice meter due to the formation of vena
Department of Mechanical Engineering-ACET Page | 11
contracta (i.e., where the jet of water contracts w.r.t. the diameter of orifice) at the downstream of
flow. Hence, orifice meters yield a comparatively lesser value of Cd than for venturimeter.
Orifices serves many purposes in engineering practice other than the metering of fluid
flow, but the study of the orifice as a metering device will allow the application of principles to
other problems. Orifices may be used in closed conduits or fitted to the containers for discharging
the fluids. They are highly preferred over venturimeter because of its simplicity in construction and
utility in space congestions, in spite of this lower Cd values.
PROCEDURE:
1. The pipe is selected for doing experiments
2. The motor is switched on, as a result water will flow
3. According to the flow, the mercury level fluctuates in the U-tube manometer
4. The reading of H1 and H2 are noted
5. The time taken for 10 cm rise of water in the collecting tank is noted
6. The experiment is repeated for various flow in the same pipe
7. The co-efficient of discharge is calculated
Department of Mechanical Engineering-ACET Page | 12
Ob
serv
atio
ns
Len
gth
of c
olle
ctin
g ta
nk =
L =
m
,
brea
dth
of c
olle
ctin
g ta
nk =
B
m
,
Pla
n ar
ea o
f ta
nk =
A =
L x
B =
m
2 .
Tab
ula
tion
s
Exp
erim
enta
l dat
a p
erta
inin
g to
ori
fice
met
er 1
(i.e
., at
tach
ed t
o P
ipe
1)
Dia
met
er o
f P
ipe
1 =
d1 =
m
,
Dia
met
er o
f or
ific
e 1
= d
2 =
m
C/s
are
a of
inle
t = a
1 =
m2
C/s
are
a of
ori
fice
= a
0 =
m2
Co-
effi
cien
t of
d
isch
arge
C
d
(no
un
it)
Th
eore
tica
l d
isch
arge
Q
th
in m
3 / s
M
ean
Cd
=
Act
ual
d
isch
arge
Q
act
in m
3 / s
Tim
e ta
ken
for
h
cm
ris
e of
wat
er t
in s
ec
Man
omet
ric
hea
d
H=
(H1~
H2)
x 1
2.6
in m
of
wat
er
Man
omet
ric
read
ing
H2
cm
of H
gH
1 cm
of
Hg
Dia
met
er
in m
m
S.n
o
Department of Mechanical Engineering-ACET Page | 13
GRAPH :
Coefficient of discharge from the graph of Qa v/s Qth:
Slope = Cd = Constant.
Qact
Qth
Coefficient of discharge from the graph = Cd =
RESULT:
Coefficient of discharge of the orifice meter (Cd)
by direct computation = __________
by graph. = __________
CALCULATION OF THE RATE OF FLOW USING ROTOMETER
Department of Mechanical Engineering-ACET Page | 14
Exp No: 3
Date:
AIM:
To determine the percentage error in Rotometer with the actual flow rate.
APPARATUS REQUIRED:
1. Rotometer setup
2. Measuring scale
3. Stopwatch.
FORMULAE:
1. ACTUAL DISCHARGE:
Q act = A x h/ t (m3 / s)
Where:
A = Area of the collecting tank (m2)
h= 10 cm rise of water level in the collecting tank (10-2 m).
t = Time taken for 10 cm rise of water level in collecting tank.
CONVERSION:
Actual flow rate (lit / min), Qact = Qact x 1000 x 60 lit /min
Rotometer reading ~ Actual x 100 % Percentage error of Rotometer =
Rotometer reading
= R ~ Qact / R x 100 %
Department of Mechanical Engineering-ACET Page | 15
DESCRIPTION:
A Roto meter is a device used for measuring the rate of flow of water flowing through the
pipe. A Roto meter consists of a tapered metering glass tube, inside of which is located a rotor
(float) of the meter. The tube is provided with suitable inlet and outlet connections. The float tube
has a specific gravity higher than that of the fluid to be metered. The spherical slots cut on a part of
the float causes it to rotate slowly about the axis of the tube and keep it centered. With increase in
the flow rate, the float rises in the tube and there occurs an increase in the annular area between the
float and the tube. The float rides may be higher or lower depending on the flow rate.
Glass tube Rotometer
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 litres 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
7. Graph is drawn by ploting Rotometer reading Vs percentage error of the Rotometer
Department of Mechanical Engineering-ACET Page | 16
Ob
serv
atio
ns
Len
gth
of c
olle
ctin
g ta
nk =
L =
m
, B
read
th o
f co
llec
ting
tank
= B
m,
Pla
n ar
ea o
f ta
nk =
A =
L x
B =
m
2
Tab
ula
tion
s
Exp
erim
enta
l dat
a p
erta
inin
g to
Rot
omet
er
Per
cen
tage
Err
or o
f R
otom
eter
I
n %
Act
ual
dis
char
geQ
act
in lp
m
Tim
e ta
ken
for
10c
m
rise
of
wat
er in
tan
kt
in s
ec
Act
ual
Dis
char
geQ
act
In m
3 /sec
Rot
omet
erR
ead
ing
in lp
m
S.n
o
Department of Mechanical Engineering-ACET Page | 17
GRAPH :
Percentage error of rotometer from the graph by Qact vs R
Qact
R
The percentage error of the Rotometer by graph is =
RESULT :
The percentage error of the Rotometer was found to be
by direct computation = ___________
by graph. = ___________
DETERMINATION OF FRICTION FACTOR OF
Department of Mechanical Engineering-ACET Page | 18
GIVEN SET OF PIPES
Exp No: 4
Date:
AIM:
To find the friction factor, ‘f ’ for the given pipe.
APPARATUS REQUIRED:
1. A pipe provided with inlet and outlet and pressure tapping
2. Differential u-tube manometer
3. Collecting tank with piezometer
4. Stopwatch
5. Scale
FORMULAE:
1. FRICTION FACTOR ( F ):
f = 2 x g x d x h f / l x v2
Where,
g = Acceleration due to gravity, (m / sec2)
d = Diameter of the pipe
l = Length of the pipe, (m)
v = Velocity of liquid following in the pipe, (m / s)
h f = Loss of head due to friction, (m)
= h1 ~ h2
Where
h1 = Manometric head in the first limbs
h2 = Manometric head in the second limbs
2. ACTUAL DISCHARGE:
Department of Mechanical Engineering-ACET Page | 19
Q = A x h / t (m3 / sec)
Where
A = Area of the collecting tank, (m2)
h = Rise of water for 5 cm, (m)
t = Time taken for 5 cm rise, (sec)
3. VELOCITY:
V = Q / a (m / sec)
Where
Q = Actual discharge, (m3/ sec)
A = Area of the pipe, (m2)
DESCRIPTION:
In steady incompressible flow in a pipe irreversibilities are expressed in terms of a head
loss, or drop in grade line. Losses, or irreversibilities, cause this line to drop in the direction of
flow. Experiments on the flow of water in long, straight, cylindrical pipes indicated head loss
varied directly with velocity head and pipe length, and inversely with pipe diameter (as shown in
figure)
Schematic of Pipe Friction
The Darcy–Weisbach equation is probably more rationally based than other empirical
formulations and has received wide applications & acceptance. The equation is given by h f =
flv2/2gd, where, hf is loss due to friction in m; f is dimensionless friction factor; V is the average
Department of Mechanical Engineering-ACET Page | 20
velocity across the C/S in m/s; d is pipe diameter in m. The friction factor f also depends upon
fluid properties (such as density and viscosity) and also on material roughness.
The main significance of friction factor is to assess the extent of energy loss in pipe flow,
while designing a pipe, pump to pressurize the fluid in pipes and other similar situations.
PROCEDURE :
1. The diameter of the pipe is measured and the internal dimensions of the collecting tank
and the length of the pipe line is measured
2. Keeping the outlet valve closed and the inlet valve opened
3. The outlet valve is slightly opened and the manometer head on the limbs h1 and h2 are
noted
4. The above procedure is repeated by gradually increasing the flow rate and then the
corresponding readings are noted.
Department of Mechanical Engineering-ACET Page | 21
Ob
serv
atio
ns
Len
gth
of c
olle
ctin
g ta
nk =
L =
m
, br
eath
of
coll
ecti
ng ta
nk =
B =
m,
Pla
n ar
ea o
f ta
nk =
A =
L x
B =
m2 .
Dia
met
er o
f P
ipe
1 =
d1 =
m,c
/s a
rea
= a
1 ==
m2
Len
gth
of P
ipe
unde
r co
nsid
erat
ion
= l=
m
Tab
ula
tion
s
(a)
Exp
erim
enta
l dat
a p
erta
inin
g to
Pip
e 1
Dia
met
er o
f P
ipe
1 =
d1 =
m
. and
a1 =
m
2 .
Fri
ctio
n
fact
orf
x 10
-2
(no
un
it)
V2
m2 /
s 2
M
ean
f =V
eloc
ity
V m/s
Act
ual
d
isch
arge
Qac
t
m3 /
s
Tim
e fo
r 10
cm r
ise
of w
ater
t s
ec
Man
omet
er r
ead
ings h
f =
(h1-
h2)
x 1
2.6
in m
h2
cm o
f H
g
h1
cm o
f H
g
Dia
met
er
of
pip
e
in m
m
S.n
o
Department of Mechanical Engineering-ACET Page | 22
Friction factor from the graph of hf v/s V2/2g
Slope = hf/(Va2/2g) = Const.
hf
Va2/2g
from the graph
Slope = fl/d
f = slope * d/l
RESULT Friction factor for the given pipe material (i.e., ‘f’)
By computation = ____________
By graph = ___________
Department of Mechanical Engineering-ACET Page | 23
CHARACTERISTICS TEST ON CENTRIFUGAL PUMP
Exp No: 5
Date:
AIM :To study the performance characteristics of a centrifugal pump and to determine the
characteristic with maximum efficiency.
APPARATUS REQUIRED :
1. Centrifugal pump setup
2. Meter scale
3. Stop watch
FORMULAE :
1. ACTUAL DISCHARGE:
Q act = A x h/ t (m3 / s)
Where:
A = Area of the collecting tank (m2)
h = 10 cm rise of water level in the collecting tank
t = Time taken for 10 cm rise of water level in collecting tank.
2. TOTAL HEAD:
H = Hd + Hs + Z
Where:
Hd = Discharge head, meter
Hs = Suction head, meter
Z = Datum head, meter
Department of Mechanical Engineering-ACET Page | 24
3. INPUT POWER:
I/P = (3600 ´ N ´ 1000) / (E ´ T) (watts)
Where, N = Number of revolutions of energy meter disc
E = Energy meter constant (rev / Kw hr)
T = time taken for ‘Nr’ revolutions (seconds)
4. OUTPUT POWER:
O/ P = ρ x g x Q x H / 1000 (watts) Where, ρ = Density of water (kg / m³)
g = Acceleration due to gravity (m / s2)
H = Total head of water (m)
5. EFFICIENCY: ho = (Output power o/p / input power I/p) ´ 100 %
Where,O/p = Output power kW
I/ p = Input power kW
DESCRIPTION: Pumps add energy to liquids; Turbo pumps are radial flow, axial flow or a
combination of two, called mixed flow. For high heads the radial (centrifugal) pump, frequently
with two or more stages (two or more impellers in series), is best adopted. For large flows under
small heads the axial flow pump or blower is best suited. The mixed flow pump is used for
medium head and medium discharge. The centrifugal pump is so called because the pressure
increase within its rotor due to centrifugal action is an important factor in its operation. In brief, it
consists of an impeller rotating within a case as shown in Fig. given below:-
Department of Mechanical Engineering-ACET Page | 25
used for lifting water from deep tube wells
used for liftingwater from deepwells, especially when the alignment is poor
Cut-view of Vortex and Volute Centrifugal Pump
Fluid enters the impeller in the center portion, called the eye, flows outwardly and is discharged
around the circumference into a casing. During flow through the rotating impeller the fluid
receives energy from the vanes, resulting in both pressure and absolute velocity. Since a large part
of the energy of the fluid having the impeller is kinetic, it is necessary to reduce the absolute
velocity into transformation pressure head. This is accomplished in the volute casing surrounding
the impeller or in flow through diffuser vanes. Following is the classification of centrifugal pumps
with their applications.
Centrifugal Pump(very widely used in water supply &waste water schemes)
Single stage (usual head) Multistage (when the head & discharge is large)
Volute pump Diffuser pump
Radial flow Mixed flow Deep well Submersible pump Turbine pump
Open type Closed type(to handle slurries (to handle treated Raw water &others) & unturbid water)
Department of Mechanical Engineering-ACET Page | 26
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.
Department of Mechanical Engineering-ACET Page | 27
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.
Department of Mechanical Engineering-ACET Page | 28
Department of Mechanical Engineering-ACET Page | 29
Ob
serv
atio
nL
engt
h of
the
coll
ecti
ng ta
nk=
L =
m
Bre
adth
of
the
coll
ecti
ng ta
nk =
B =
m
Pla
n ar
ea o
f ta
nk A
= L
x B
= =
m2
Ene
rgy
met
er c
onst
ant
K =
imp/
kwh
Dis
tanc
e be
twee
n th
e su
ctio
n an
d de
live
ry g
auge
s =
Dat
um h
ead
=Z
= m
Tab
ula
tion
Exp
erim
enta
l dat
a p
erta
inin
g to
c.f
. pu
mp
(si
ngl
e st
age
oper
atio
ns)
:
h %
Ou
tpu
tP
ower
(Po)
wat
t
Inp
ut
Pow
er
(Pi )
wat
t
Act
ual
Dis
char
ge
(Qac
t)
m3 \s
ec
Tim
e ta
ken
for
N
r re
volu
tion
t S
Tim
e ta
ken
fo
r ‘h
’ ri
seof
wat
er(t
)
S
Tot
alH
ead
(H)
m o
f w
ater
Del
iver
yH
ead
(Hd
)
m o
f w
ater
Del
iver
yG
auge
Rea
din
g(h
d)
m o
f w
ater
Su
ctio
n
hea
d
Hs
m o
f w
ater
Su
ctio
n
gau
ge
Hs
m o
f w
ater
S.
no
Performance of C.F. Pump through graph
Though some C.F. pumps are driven by variable speed motors the usual mode of
operation of pump is at constant speed and typical characteristics of a C.F. Pump for such
operation as shown in figure.
Optimum head = m
Normal head = m
Optimum discharge = m3/s
& Normal discharge = m3/s
Graph H O/P h1. Actual discharge Vs Total head
2. Actual discharge Vs Efficiency
3. Actual discharge Vs Output power
Q
RESULTPerformance of given centrifugal pump (single stage)
Optimum head = m
Normal head = m
Optimum discharge = m3/s
& Normal discharge = m3/s
Department of Mechanical Engineering-ACET Page | 30
CHARACTERISTICS CURVES OF RECIPROCATING PUMP
Exp No: 6
Date:
AIM:To study the performance characteristics of a reciprocating pump and to determine the
characteristic with maximum efficiency.
APPARATUS REQUIRED:
1. Reciprocating pump
2. Meter scale
3. Stop watch
FORMULAE:
1. ACTUAL DISCHARGE:
Q act = A x y / t (m3 / s)
Where: A = Area of the collecting tank (m2)
y = 10 cm rise of water level in the collecting tank
t = Time taken for 10 cm rise of water level in collecting tank
2.TOTAL HEAD:
H = Hd + Hs + Z
Where:
Hd = Discharge head; Hd = Pd x 10, m
Hs = Suction head; Pd = Ps x 0.0136, m
Z = Datum head, m
Pd = Pressure gauge reading, kg / cm2
Ps = Suction pressure gauge reading, mm of Hg
Department of Mechanical Engineering-ACET Page | 31
3.INPUT POWER:
Pi = (3600 ´ N) / (E ´ T) (Kw)
Where, N = Number of revolutions of energy meter disc
E = Energy meter constant (rev / Kw hr)
T = time taken for ‘N’ revolutions (seconds)
4. OUTPUT POWER:
Po = ρ x g x Q x H / 1000 (Kw) Where,
ρ = Density of water (kg / m³)
g = Acceleration due to gravity (m / s2)
H = Total head of water (m)
Q = Discharge (m3 / sec)
5.EFFICIENCY: ho = (Output power po / input power pi) ´ 100 %
Where,Po = Output power KW
Pi = Input power KW
DESCRIPTION
Reciprocating pumps, the name given to the pumping machinery in which the essential
working components are cylinder and plunger or piston (refer Fig.1). These small pumps have
single cylinder and are single acting.(i.e., they suck the liquid to be pumped during forward stroke
and deliver it during backward or return stroke). Large industrial pumps can be multi cylinder and
double acting. Since forward and backward strokes are completed during one complete revolution
of crank and since the pump is single acting, rate of liquid delivered per second is given by AlN .
Department of Mechanical Engineering-ACET Page | 32
Sche
mati c
Diagram of a Single-cylinder and
Single acting Reciprocating pump
Usually due to leakage losses, the actual discharge is somewhat less than theoretical
discharge and the difference between actual and theoretical discharges is known as ‘slip’ of pump
which is given by,
Percentage slip= Theoretical discharge –Actual discharge x 100
Theoretical discharge
The variation between the pressure in the cylinder and volume swept by piston for one
complete revolution is known as indicator diagram. Figure 2 represents the indicator diagram and
in that; ab represents a constant pressure of (Pa/r-hs ) acting during suction or forward stroke , cd
represents a constant pressure of hd acting during delivery or backward stroke, and bc and da are
imaginary lines that represent the instantaneous jump at the end of suction and delivery strokes ,
respectively.
Small hand operated pumps, such as cycle and football pumps, kerosene pumps, village
well pumps; pumps in milk shops and pumps in hydraulic jack are some applications of the
reciprocating pumps. Reciprocating pumps for industrial uses have now almost become obsolete
because of their capital cost and maintenance cost when compared to centrifugal pumps. However,
they are also less efficient. Hence, centrifugal pumps dominate these pumps.
Department of Mechanical Engineering-ACET Page | 33
Department of Mechanical Engineering-ACET Page | 34
Ob
serv
atio
ns
Len
gth
of th
e co
llec
ting
tank
= L
=m
Bre
adth
of
the
coll
ecti
ng ta
nk =
B =
m
Pla
n ar
ea o
f ta
nk =
A=
L *
B =
m2
Dis
tanc
e be
twee
n th
e ga
uges
= D
atum
hea
d =
z=
m
& E
nerg
y m
eter
con
stan
t = K
=
rev/
kwh
Tab
ula
tion
Exp
erim
enta
l dat
a p
erta
inin
g to
th
e si
ngl
e cy
lin
der
an
d s
ingl
e-ac
tin
g re
cip
roca
tin
g p
um
p:
h %
Ou
tpu
t p
ower
Po
Kw
Mea
n =
Inp
ut
pow
er
Pi
Kw
Tim
e ta
ken
fo
r N
rev
of
en
ergy
m
eter
dis
c
t
sec
Act
ual
d
isch
arge
Qac
t
m³/s
Tim
e ta
ken
fo
r 10
cm
of
rise
of
wat
er
in t
ank
t sec
Tot
al
hea
d
H m
Dat
um
h
ead
Z
m
Su
ctio
n
hea
d
Hs
=
Ps
x .0
136
m
Del
iver
y h
ead
Hd=
Pd
x10.
0
m
Su
ctio
n
pre
ssu
re
read
ing
Ps
mm
of
Hg
Del
iver
y p
ress
ure
re
adin
g
Pd
kg
/ cm
2
S. n o
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.
PERFORMANCE OF RECIPROCATING PUMP THROUGH GRAPH
Though some reciprocating pumps are driven by variable speed motors, the usual
mode of operation of pump is at constant speed and typical characteristics of a Reciprocating
pump for such operation is as shown in figure.
Optimum head = m
Normal head = m
Optimum discharge = m3/s
& Normal discharge = m3/s
Graph H O/P h1. Actual discharge Vs Total head
2. Actual discharge Vs Efficiency
3. Actual discharge Vs Output
Q
RESULTPerformance of given centrifugal pump (single stage)
Optimum head = m
Normal head = m
Optimum discharge = m3/s
& Normal discharge = m3/s
Department of Mechanical Engineering-ACET Page | 35
CHARACTERISTICS CURVES OF GEAR OIL PUMP
Exp No: 7
Date:
AIM:
To draw the characteristics curves of gear oil pump and also to determine efficiency of
given gear oil pump.
APPARATUS REQUIRED:
1. Gear oil pump setup
2. Meter scale
3. Stop watch
FORMULAE: 1. ACTUAL DISCHARGE:
Qact = A x y / t (m³ / sec)
Where, A = Area of the collecting tank (m²)
y = Rise of oil level in collecting tank (cm)
t = Time taken for ‘h’ rise of oil in collecting tank (s)
2. TOTAL HEAD:
H = Hd + Hs + Z
Where
Hd = Discharge head; Hd = Pd x 12.5, m
Hs = Suction head; Pd = Ps x 0.0136, m
Z = Datum head, m
Pd = Pressure gauge reading, kg / cm2
Department of Mechanical Engineering-ACET Page | 36
Ps = Suction pressure gauge reading, mm of Hg
3. INPUT POWER:
Pi = (3600 ´ N) / (E´ T) (kw)
Where, Nr = Number of revolutions of energy meter disc
Ne = Energy meter constant (rev / Kw hr)
te = Time taken for ‘Nr’ revolutions (seconds)
4. OUTPUT POWER:
Po = W ´ Qact ´ H /1000 (watts)
Where, W = Specific weight of oil (N / m³)
Qact = Actual discharge (m³ / s)
h = Total head of oil (m)
5. EFFICIENCY:
%h = (Output power Po / input power Pi) ´ 100
DESCRIPTION
Although the gear pump (which consists of two gears), is a rotating machine, yet its
action on liquid to be pumped is not dynamic and it merely displaces the liquid from one side to
the other. Hence, this type of pump comes under positive displacement pumps. The following
diagram illustrates the working principle of a gear pump.
Department of Mechanical Engineering-ACET Page | 37
From the above Fig., it seems that, on suction side, the liquid fills up the gaps between the
meshing gears. This liquid, then after passing round the casing, finds its way to pressure side,
when the gears rotate. On the pressure side, the two streams come again together. The major
portion is pushed towards delivery side and a small volume returns back to suction side. The
separation of suction side from delivery side occurs through the flanks of meshing teeth and the
outside casing of the pump, which should have very small clearance with the gears. Since more
than one tooth of each gear may mesh with one another, in between suction and delivery side, a
sort of closed space is formed. The volume of liquid in these closed space changes during rotation
and reaches a certain minimum (i.e., zero when no play). Hence, an arrangement should be
provided such that the entrapped liquid should be able to move out and this is achieved through
sidewalls of pump.
Normally gear pumps are expected to work against small heads of a few atmospheres. High
speed pumps can produce a suction of about 7m. This type of pump is widely used for cooling
water and pressure oil to be supplied for lubrication to motors, turbines, machine tools, and other
similar situations.
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.
Department of Mechanical Engineering-ACET Page | 38
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.
Department of Mechanical Engineering-ACET Page | 39
Department of Mechanical Engineering-ACET Page | 40
Ob
serv
atio
ns
Len
gth
of o
il c
olle
ctin
g ta
nk =
L
=m
,
brea
dth
of o
il c
olle
ctin
g ta
nk =
B
= m
P
lan
area
of
tank
= A
=
LxB
=m
2
Ene
rgy
met
er c
onst
ant =
K
=re
v/kw
h
Dis
tanc
e be
twee
n th
e su
ctio
n an
d de
live
ry g
auge
s =
Dat
um h
ead
= Z
= m
Tab
ula
tion
s
Exp
erim
enta
l dat
a pe
rtai
ning
to g
ear
oil p
ump
wit
h lu
be o
il 4
0 S
AE
:
h %
Ou
tpu
t p
ower
Po
Kw
Mea
n =
Inp
ut
pow
er
Pi
Kw
Tim
e ta
ken
for
N
rev
of
ener
gy
met
er d
isc
t
se
c
Act
ual
d
isch
arge
Qac
t
m³/s
Tim
e ta
ken
fo
r 10
cm
of
ris
e of
w
ater
in
tan
k
t sec
Tot
al
hea
d
H
m
Dat
um
h
ead
Z
m
Su
ctio
n
hea
d
Hs
=
Ps
x 0.
0136
m
Del
iver
y h
ead
H
d=
Pd
x12.
5
m
Su
ctio
n
pre
ssu
re
read
ing
Ps
mm
of
Hg
Del
iver
y p
ress
ure
re
adin
g P
d
kgf
/ cm
2
S.
no
PERFORMANCE OF GEAR OIL PUMP THROUGH GRAPH
The operating characteristics of gear pump, showing the relationship of discharge,
power and efficiency are given below:
Maximum efficiency = %
At maximum efficiency,
Discharge = m3/s
Power = kW
& Head = m
GRAPH H O/P h1. Actual discharge Vs Total head
2. Actual discharge Vs Efficiency
3. Actual discharge Vs Output
Q
RESULT
Maximum efficiency = %
At maximum efficiency,
Discharge = m3/s
Power = kW
& Head = m
CHARACTERISTICS CURVES OF PELTON WHEEL
Department of Mechanical Engineering-ACET Page | 41
Exp No: 8
Date:
AIM:
To conduct load test on pelton wheel turbine and to study the characteristics of pelton wheel turbine.
APPARATUS REQUIRED :
1. Venturimeter
2. Stopwatch
3. Tachometer
4. Dead weight
FORMULAE:
1. VENTURIMETER READING:
h = (P1 ~ P2) ´ 10 (m of water) Where, P1, P2 - venturimeter reading in Kg /cm2
2. DISCHARGE: Q = 0.0055 ´ Ö h (m3 / s)
3. BRAKE HORSE POWER:
BHP = (p x D x N x T) / (60 ´75) (hp) Where,
N = Speed of the turbine in (rpm)
D = Effective diameter of brake drum = 0.315 m
T = Torsion in To + T1 – T2 (Kg)
4. INDICATED HORSE POWER: IHP = (1000 ´ Q ´ H) / 75 (hp) Where,
H = Total head (m)
5. PERCENTAGE EFFICIENCY:
Department of Mechanical Engineering-ACET Page | 42
%h = (B.H.P / I.H.P x 100) (%)
DESCRIPTION:
An impulse turbine, whether for water, stream, or gas, is one in which the total drop in
pressure of the fluid takes place in one or more stationary nozzles and there is no change in
pressure of the fluid as it flows through the rotating wheel. As there is no pressure variation in flow
over buckets or vanes, the fluid does no fill the passageway between one bucket or vane and the
next. Customarily, the fluid only acts upon a portion of the circumference of the wheel at any
instant.
Several types of hydraulic impulse turbines have been produced in the past, but the only one
that has survived is the Pelton wheel (Refer Fig) so called in honour of Lester.A.Pelton
Fig: Pelton Wheel Installation
Department of Mechanical Engineering-ACET Page | 43
(1829-1908). Pelton patented the wheel with buckets having a splitter in the middle and
W.A.Double brought out the ellipsoidal bucket, which is the basis of the modern forms.
Impulse turbines are usually set with the shaft horizontal, and there is usually only one jet on a
wheel. But more commonly, the multi jet arrangement is used with a vertical shaft arrangement.
Pelton wheels are usually installed under high heads, the pressure loss due to setting is small (i.e.,
Z). If any turbine, in order to maintain a constant speed of rotation, it is necessary that the flow rate
be varied in accordance with the load on the machine; and for the impulse wheel, this is done by
varying the size of the jet and is accomplished by varying the position of the needle in the nozzle.
An important feature in attaining high efficiency in an impulse wheel is that the jet be uniform and
with no spreading out of the jet. The rotative speed of an impulse turbine is maintained constant
throughout, with the use of a governor. The Figure shows an impulse runner where the buckets are
bolted to a rim. The faces of buckets are smooth ground. They are made of bronze or steel. The
height and width of the bucket should each be 2.5 to 4 times the jet diameter, otherwise bucket
efficiency will suffer. Under normal operations all water that issues from the nozzle will act upon
the buckets, for whatever water does not act on the first bucket will act on the second bucket and
so on.
Pelton wheels are highly applicable in generating electricity through generators, only
when the static head (as explained earlier) available is very large. These are also adopted in India
(i.e., Pykara dam)
Department of Mechanical Engineering-ACET Page | 44
Department of Mechanical Engineering-ACET Page | 45
Ob
serv
atio
ns
Dia
met
er o
f in
let o
f pi
pe =
Dia
. of
inle
t of
vent
urim
eter
= d
1 =
m
Dia
met
er o
f th
roat
of
vent
urim
eter
= d
2 =
m
Dia
met
er o
f w
heel
dru
m =
D =
m
Dia
met
er o
f ro
pe u
sed
in d
ead
wei
ght s
yste
m =
d =
m
Ave
rage
spr
ing
wei
ght (
used
in th
e lo
adin
g sy
stem
) =
Ws =
kg
.
Tab
ula
tion
Exp
erim
enta
l dat
a p
erta
inin
g to
th
e gi
ven
Pel
ton
Wh
eel:
h
%
I.H
.P
hp
Mea
n =
B.H
.P
hp
Dis
char
ge
Q
m3 \s
ec
Ten
sion
T Kg
Sp
rin
gB
alan
ce
T2
Kg
Wei
gh
of
han
ger
T1
Kg
Sp
eed
of
turb
ine
N
Rp
m
Wei
ght
of
han
ger
To
Kg
H=
(P
1-P
2)
x 10
m o
f w
ater
Ven
turi
met
er
read
ing
Kg\
cm2 P2
P1
Tot
al
Hea
d
H
m o
f w
ater
Pre
ssu
reG
auge
Rea
din
gH
p
Kg\
cm2
S.n
o
PROCEDURE:
1. The Pelton wheel turbine is started.
2. All the weight in the hanger is removed.
3. The pressure gauge reading is noted down and it is to be maintained constant for
different loads.
4. The venturimeter readings are noted down.
5. The spring balance reading and speed of the turbine are also noted down.
6. A 5Kg load is put on the hanger, similarly all the corresponding readings are
noted down.
7. The experiment is repeated for different loads and the readings are tabulated.
Performance of Pelton WheelBased on the data collected for the given Pelton wheel or turbine, plots are drawn as shown below.
From the graph,
Optimum discharge = m3/s
Optimum speed = rpm
Normal discharge = m3/s
Normal speed = rpm
Graph Q O/P h1. Speed Vs Total head
2. Speed Vs Efficiency
3. Speed Vs Output
NRESULTPerformance of the given Pelton Turbine or Wheel:
Optimum discharge = m3/s
Optimum speed = rpm
Normal discharge = m3/s
& Normal speed = rpm
Department of Mechanical Engineering-ACET Page | 46
CHARACTERISTICS CURVES OF FRANCIS TURBINE
Exp No: 9
Date:
AIM:
To conduct load test on franchis turbine and to study the characteristics of francis turbine.
APPARATUS REQUIRED:
1. Stop watch
2. Tachometer
FORMULAE:
1. VENTURIMETER READING:
h = (P1 - P2) x 10 (m)
Where
P1, P2- venturimeter readings in kg / cm2
2. DISCHARGE:
Q = 0.011 x Ö h (m3 / s)
3. BRAKE HORSEPOWER:
BHP = p x D x N x T / 60 x 75 (h p)
Where
N = Speed of turbine in (rpm)
D = Effective diameter of brake drum = 0.315m
T = torsion in [kg]
4. INDICATED HORSEPOWER:
HP = 1000 x Q x H / 75 (hp)
Where
H – total head in (m)
5. PERCENTAGE EFFICIENCY:
%h = B.H.P x 100 / I.H.P ( %)
Department of Mechanical Engineering-ACET Page | 47
DESCRIPTION:
A reaction turbine is one in which the major portion of pressure drop takes place in the
rotating wheel. As a consequence the proportions must be such that the fluid fills all the runner
passages completely. This makes it necessary that the fluid be admitted to the rotor around its
entire circumference. Since the entire circumference of the reaction turbine is in action, its rotor
need not be as large as that of an impulse wheel for the same power.
The first reaction turbine known is the steam turbine of Hero in Egypt about 120 B.C.
In the hydraulic field the rotating lawn sprinkler is an elementary reaction turbine. The first to be
well-designed inward flow turbine was built in 1849 by eminent hydraulic engineer James
B.Francis. The design of the Francis turbine is shown in Fig (also known as mixed flow runner or
Francis runner). In this runner, all flow lines have both axial and radial components throughout.
Guide Vane Assembly Francis Turbine Installation with Straight
Conical Draft Tube
Francis runner is surrounded by pivoted guide vanes (i.e., the assembly is known as
wicket gates) (Ref. Fig.1). The water is greatly accelerated in guide vanes passages and given a
definite tangential velocity component as it enters the runner. The governor regulates the flow rates
by rotating these vanes about their pivots so that the variation of area occurs between them. The
value of velocity however, is not much affected by the change in the guide vane angle.
Department of Mechanical Engineering-ACET Page | 48
Schematic of Various Heads on Reaction Turbine
The water rotates as a free vortex in the space between the ends of the guide vanes and the
entrance edges of the turbine runner. The guide vanes assembly is surrounded in turn by a spiral
case or scroll case, which maintains an uniform velocity around the turbine circumference.
Majority of Francis turbines are set with vertical shafts and the greatest advantage from it is that
the draft tube is then more efficient.
The draft tube is an integral part of a reaction turbine and it has two important functions.
One is to enable the turbine to be set above the tail water level without losing any head thereby.
The second function is to reduce the head loss at submerged discharge and thereby increase the net
head available to the turbine runner. This is accomplished by using a gradually diverting tube.
\ Cavitation phenomenon (when a liquid flows into a region where its pressure is reduced
to vapor pressure, it boils and vapor pockets develop in it) is undesirable because it RESULTs in
pitting of material, mechanical vibrations and loss of efficiency in turbines. In reaction turbines the
most likely place for the occurrence of cavitation is on the backsides of the runner blades near their
trailing edges. Cavitation may be avoided by designing, installing and operating a turbine in such a
manner that at no point that the local absolute pressure drop to the vapor pressure of water. The
most critical factor in the installation of reaction turbines is the vertical distance from the runner to
the tail water.
Department of Mechanical Engineering-ACET Page | 49
Ob
serv
atio
ns
Dia
met
er o
f in
let o
f pi
pe =
Dia
. of
inle
t of
vent
urim
eter
= d
1 =
m
Dia
met
er o
f th
roat
of
vent
urim
eter
= d
2 =
m
Dia
met
er o
f w
heel
dru
m =
D =
m
Dia
met
er o
f ro
pe u
sed
in d
ead
wei
ght s
yste
m =
d =
m
Ave
rage
spr
ing
wei
ght (
used
in th
e lo
adin
g sy
stem
) =
Ws =
kg
.
Tab
ula
tion
Exp
erim
enta
l dat
a p
erta
inin
g to
th
e gi
ven
Fra
nci
s T
urb
ine:
h
%
I.H
.P
hp
B.H
.P
hp
Dis
cha
rge
Q
m3 \s
ec
Ten
sion
T Kg
Sp
rin
gB
alan
ce
T2
Kg
Wei
gh
of
han
ger T1
kg
Sp
eed
of
tu
rbin
e
N
Rp
m
Wei
ght
of
han
ger
To
Kg
H=
(P
1-P
2) x
10 m o
f w
ater
Ven
turi
met
er
read
ing
Kg\
cm2 P2
P1
Tot
al
Hea
d
[H]
m o
f H
2O
Pre
ssu
reG
auge
Rea
din
g[H
p]
Kg\
cm2
Department of Mechanical Engineering-ACET Page | 50
Mea
n
h
S. n
o
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 assended down
5. The venturimeter reading and speed of turbine are noted down
6. The experiment is repeated for different loads and the reading are tabulated.
PERFORMANCE OF FRANCIS TURBINEBased on the data collected for the given Francis turbine, plots are drawn as shown below.
From the graph,
Optimum discharge = m3/s
Optimum speed = rpm
Normal discharge = m3/s
Normal speed = rpm
GRAPHQ O/P h
1. Speed Vs Actual Discharge
2. Speed Vs Efficiency
3. Speed Vs Output
N
RESULT
Performance of the given Francis turbine or Runner:
Optimum discharge = m3/s
Optimum speed = rpm
Normal discharge = m3/s
Department of Mechanical Engineering-ACET Page | 51
& Normal speed = rpm
KAPLAN TURBINE TEST RIGExp No: 10
Date:
AIM:
To study the characteristics of a Kaplan turbine
DESCRIPTION:
A reaction turbine is one in which the major portion of pressure drop takes place in the
rotating wheel. As a consequence the proportions must be such that the fluid fills all the runner
passages completely. This makes it necessary that the fluid be admitted to the rotor around its
entire circumference. Since the entire circumference of the reaction turbine is in action, its rotor
need not be as large as that of an impulse wheel for the same power.
The first reaction turbine known is the steam turbine of Hero in Egypt about 120 B.C.
In the hydraulic field the rotating lawn sprinkler is an elementary reaction turbine. The first to be
well-designed inward flow turbine was built in 1849 by eminent hydraulic engineer James
B.Francis. The design of the Kaplan turbine is shown in figure 1 (also known as mixed flow runner
or Kaplan runner). In this runner, all flow lines have both axial and radial components throughout.
Kaplan runner is surrounded by pivoted guide vanes (i.e., the assembly is known as wicket
gates) (Ref. Figure.). The water is greatly accelerated in guide vanes passages and given a definite
tangential velocity component as it enters the runner. The governor regulates the flow rates by
rotating these vanes about their pivots so that the variation of area occurs between them. The value
of velocity however, is not much affected by the change in the guide vane angle.
The water rotates as a free vortex in the space between the ends of the guide vanes and
the entrance edges of the turbine runner. The guide vanes assembly, is surrounded in turn by a
spiral case or scroll case which maintains an uniform velocity around the turbine circumference.
Majority of Kaplan turbines are set with vertical shafts and the greatest advantage from it is that
the draft tube is then more efficient.
The draft tube is an integral part of a reaction turbine and it has two important functions. One is to
enable the turbine to be set above the tail water level without losing any head thereby. The second
Department of Mechanical Engineering-ACET Page | 52
function is to reduce the head loss at submerged discharge and thereby increase the net head
available to the turbine runner. This is accomplished by using a gradually diverting tube.
Kaplan Turbine Installation with an Elbow Type Draft Tube
Schematic of Various Heads on Reaction Turbine
Cavitation phenomenon (when a liquid flows into a region where its pressure is reduced
to vapor pressure, it boils and vapor pockets develop in it) is undesirable because it RESULTs in
Department of Mechanical Engineering-ACET Page | 53
pitting of material, mechanical vibrations and loss of efficiency in turbines. In reaction turbines the
most likely place for the occurrence of Cavitation is on the backsides of the runner blades near
their trailing edges. Cavitation may be avoided by designing, installing and operating a turbine in
such a manner that at no point that the local absolute pressure drop to the vapor pressure of water.
The most critical factor in the installation of reaction turbines is the vertical distance from the
runner to the tail water.
EXPERIMENTAL 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 them 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 vacum gauge readings
9. Note the orifice meter pressure readings.
Repeat the experiments for other loads
Department of Mechanical Engineering-ACET Page | 54
Ob
serv
atio
nD
iam
eter
of
inle
t of
pipe
= D
ia. o
f in
let o
f ve
ntur
imet
er =
d1 =
m
Dia
met
er o
f th
roat
of
vent
urim
eter
= d
2 =
m
Dia
met
er o
f w
heel
dru
m =
D =
m
Dia
met
er o
f ro
pe u
sed
in d
ead
wei
ght s
yste
m =
d =
m
Ave
rage
spr
ing
wei
ght (
used
in th
e lo
adin
g sy
stem
) =
Ws =
kg.
Tab
ula
tion
Exp
erim
enta
l dat
a p
erta
inin
g to
th
e gi
ven
Kap
lan
Tu
rbin
e:
h
%
I.H
.P
hp
Mea
n h
B.H
.P
hp
Dis
cha
rge
Q
m3 \s
ec
Ten
sio
n T Kg
Sp
rin
gB
alan
ce
T2
Kg
Wei
gh
of
han
ger T1
kg
Sp
eed
of
tu
rbin
e
N
Rp
m
Wei
ght
of
han
ger
To
Kg
H=
(P
1-P
2)
x 10
m o
f w
ater
Ven
turi
met
er
read
ing
Kg\
cm2 P
2P
1
Tot
al
Hea
d
[H]
m o
f H
2O
Pre
ssu
reG
auge
Rea
din
g[H
p]
Kg\
cm2
S.
no
Department of Mechanical Engineering-ACET Page | 55
PERFORMANCE OF KAPLAN TURBINE BY GRAPH
Based on the data collected for the given Kaplan turbine, plots are drawn as shown below.
From the graph,
Optimum discharge = m3/s
Optimum speed = rpm
Normal discharge = m3/s
Normal speed = rpm
GRAPH
1. Speed Vs Actual Discharge
2. Speed Vs Efficiency Q O/P h
3. Speed Vs Output
N
RESULT
Performance of the given Kaplan turbine or Runner:
Optimum discharge = m3/s
Optimum speed = rpm
Normal discharge = m3/s
& Normal speed = rpm
Department of Mechanical Engineering-ACET Page | 56