This document discusses various types of pumps used to move water from lower to higher points. It describes centrifugal pumps, which use centrifugal force to move water radially outward, and positive displacement pumps like screw and reciprocating pumps. Key parts of centrifugal pumps are identified, including the impeller, casing, suction pipe, and delivery pipe. Concepts discussed include total dynamic head, pump efficiency, cavitation, net positive suction head, and the process of selecting a pump by matching its characteristic curve to the system curve.

1. HYDRAULICS
(670441)
Philadelphia University
Faculty of Engineering
Civil Engineering Department
First Semester, 2011/2012

2. Lecture Title
Pumps

3. Definition
• Water pumps are devices designed to convert
mechanical energy to hydraulic energy.
• They are used to move water from lower
points to higher points with a required
discharge and pressure head.
• This chapter will deal with the basic hydraulic
concepts of water pumps

4. Pump Classification
• Turbo-hydraulic (kinetic) pumps
Centrifugal pumps (radial-flow pumps)
Propeller pumps (axial-flow pumps)
Jet pumps (mixed-flow pumps)
• Positive-displacement pumps
Screw pumps
Reciprocating pumps

5. • This classification is based on the
way by which the water leaves the
rotating part of the pump.
• In radial-flow pump the water
leaves the impeller in radial
direction,
• while in the axial-flow pump the
water leaves the propeller in the
axial direction.
• In the mixed-flow pump the water
leaves the impeller in an inclined
direction having both radial and
axial components

6. • Radial Flow - a centrifugal pump in which the
pressure is developed wholly by centrifugal force.
• Mixed Flow - a centrifugal pump in which the
pressure is developed partly by centrifugal force and
partly by the lift of the vanes of the impeller on the
liquid.
• Axial Flow - a centrifugal pump in which the pressure
is developed by the propelling or lifting action of the
vanes of the impeller on the liquid.

7. Schematic diagram of basic
elements of centrifugal
pump

8. Schematic diagram of axial-flow
pump arranged in vertical operation

9. Screw pumps.
• In the screw pump a revolving shaft fitted with
blades rotates in an inclined trough and pushes the
water up the trough.

11. Reciprocating pumps.
• In the reciprocating pump a piston sucks the
fluid into a cylinder then pushes it up causing
the water to rise.

12. Centrifugal Pumps
• Demour’s centrifugal pump - 1730
• Theory
– conservation of angular momentum
– conversion of kinetic energy to potential energy
• Pump components
– rotating element - impeller
– encloses the rotating element and seals the pressurized
liquid inside – casing or housing

13. Centrifugal Pumps
Impeller
Vanes
Casing
Suction Eye Impeller
Discharge
Flow Expansion
• Broad range of applicable flows and heads
• Higher heads can be achieved by increasing the
diameter or the rotational speed of the impeller

14. Centrifugal Pump:
• Centrifugal pumps (radial-flow pumps) are the most
used pumps for hydraulic purposes. For this reason,
their hydraulics will be studied in the following
sections.

17. Main Parts of Centrifugal Pumps
• which is the rotating part of
the centrifugal pump.
• It consists of a series of
backwards curved vanes
(blades).
• The impeller is driven by a
shaft which is connected to the
shaft of an electric motor.
1. Impeller:

18. Main Parts of Centrifugal Pumps
• Which is an air-tight
passage surrounding the
impeller
• designed to direct the
liquid to the impeller
and lead it away
• Volute casing. It is of
spiral type in which the
area of the flow
increases gradually.
2. Casing

19. 3. Suction Pipe.
4. Delivery Pipe.
5. The Shaft: which is the bar by which the
power is transmitted from the motor drive to
the impeller.
6. The driving motor: which is responsible for
rotating the shaft. It can be mounted directly
on the pump, above it, or adjacent to it.

20. Note that a centrifugal pump can be
either submersible (wet) or dry.

22. Hydraulic Analysis of Pumps and Piping
Systems
• Pump can be placed in two possible position in
reference to the water levels in the reservoirs.
• We begin our study by defining all the
different terms used to describe the pump
performance in the piping system.

23. Hydraulic Analysis of Pumps and Piping Systems
Ht
hd
Hstat
hs
Hms
Hmd
Datum pump
center line
hfs
hfd
Case 1

24. Hstat
HmdHms
hd
Ht
hs
Datum pump
center line
hfd
hfs
Case 2

25. The following terms can be defined
• hs (static suction head): it is the difference in
elevation between the suction liquid level and the
centerline of the pump impeller.
• hd (static discharge head): it is the difference in
elevation between the discharge liquid level and
the centerline of the pump impeller.
• Hstat (static head): it is the difference (or sum) in
elevation between the static discharge and the
static suction heads: H h hstat d s= ±

26. • Hms (manometric suction head): it is the suction
gage reading (if a manometer is installed just at the
inlet of the pump, then Hms is the height to which
the water will rise in the manometer).
• Hmd (manometric discharge head): it is the
discharge gage reading (if a manometer is installed
just at the outlet of the pump, then Hmd is the height
to which the water will rise in the manometer).
• Hm (manometric head): it is the increase of
pressure head generated by the pump:
H H Hm md ms= ±

27. • Ht (total dynamic head): it is the total head
delivered by the pump:
H H
V
g
H
V
gt md
d
m s
s
= + − +
2 2
2 2
( )
H H
V
g
H
V
gt md
d
m s
s
= + + −
2 2
2 2
( )
Case 1
Case 2
Eq.(1)
Eq.(2)

28. • Ht can be written in another form as follows:
H h h hmd d f d md= + + ∑
H h h h
V
gms s f s ms
s
= − − −∑
2
2
H h h h
V
gms s f s ms
s
= + + +∑
2
2
Case 1
Case 2
H h h h
V
g
h h h
V
g
V
gt d f d md
d
s f s ms
s s
= + + ∑ + − − − − +∑








2 2 2
2 2 2
H h hstat d s= −
but
H H h h h h
V
gt stat f d md f s ms
d
= + + ∑ + + +∑
2
2
Substitute into eq. (1)
Eq.(3)
Case 1

29. • Equation (3) can be applied to Case 2 with the
exception that : H h hstat d s= +
In the above equations; we define:
hfs : is the friction losses in the suction pipe.
hfd : is the friction losses in the discharge (delivery) pipe.
hms : is the minor losses in the suction pipe.
hmd: is the minor losses in the discharge (delivery) pipe.

30. • Bernoulli’s equation can also be applied to find Ht
H
P V
g
Z
P V
g
Zt
d d
d
s s
s= + + ± + +





γ γ
2 2
2 2
Eq.(4)

31. Pump Efficiency
η
γ
p
o
i
t
i
Power output
Power input
P
P
Q H
P
= = =
P
Q H
i
t
p
=
γ
η
or
Which is the power input delivered from the motor to the
impeller of the pump.

32. Motor efficiency : ηm
ηm
i
m
P
P
=
P
P
m
i
m
=
η
which is the power input delivered to the motor.
ηo
η η ηo p m=
ηo
o
m
P
P
=
Overall efficiency of the motor-pump system:

33. Cavitation of Pumps and NPSH
• In general, cavitation occurs when the liquid pressure
at a given location is reduced to the vapor pressure of
the liquid.
• For a piping system that includes a pump, cavitation
occurs when the absolute pressure at the inlet falls
below the vapor pressure of the water.
• This phenomenon may occur at the inlet to a pump and
on the impeller blades, particularly if the pump is
mounted above the level in the suction reservoir.

34. • Under this condition, vapor bubbles form (water
starts to boil) at the impeller inlet and when these
bubbles are carried into a zone of higher pressure,
they collapse abruptly and hit the vanes of the
impeller (near the tips of the impeller vanes).
causing:
• Damage to the pump (pump impeller)
• Violet vibrations (and noise).
• Reduce pump capacity.
• Reduce pump efficiency

35. • To avoid cavitation, the pressure head at the inlet should not fall
below a certain minimum which is influenced by the further
reduction in pressure within the pump impeller.
• To accomplish this, we use the difference between the total head
at the inlet , and the water vapor pressure head
g
VP ss
2
2
+
γ
γ
vaporP
How we avoid Cavitation ??

36. Where we take the datum through the centerline of the pump
impeller inlet (eye). This difference is called the Net Positive
Suction Head (NPSH), so that
NPSH
P V
g
Ps s vapor
= + −
γ γ
2
2
There are two values of NPSH of interest. The first is the required NPSH,
denoted (NPSH)R , that must be maintained or exceeded so that cavitation
will not occur and usually determined experimentally and provided by the
manufacturer.
The second value for NPSH of concern is the available NPSH, denoted
(NPSH)A , which represents the head that actually occurs for the particular
piping system. This value can be determined experimentally, or calculated if
the system parameters are known.

37. How we avoid Cavitation ??
• For proper pump operation (no cavitation) :
(NPSH)A > (NPSH)R

38. Determination of
(NPSH)A
datum
hs
applying the energy equation between
point (1) and (2), datum at pump
center line
Vapor
Vapor
LS
air
atm
A
Vapor
Vapor
LS
air
atm
Vapor
VaporSS
LS
air
atmSS
L
SS
S
air
atm
P
hh
P
NPSH
P
hh
PP
g
VP
hh
P
g
VP
h
g
VP
h
P
γγ
γγγγ
γγ
γγ
−−−=
−−−=−+
−−=+
++=−
∑
∑
∑
∑
)(
2
2
2
2
2
2

39. ( )NPSH h h h
P P
A s f s m s
atm vapor
= − − + −∑
γ γ
Note that (+) is used if hs is above the pump centerline (datum).
2
2
o
/335.2
/14.10
20Tat
mkNP
mkNP
Vapor
atm
=
=
=

40. Thoma’s cavitation constant
The cavitation constant: is the ratio of (NPSH)R
to
the total dynamic head (Ht
) is known as the Thoma’s
cavitation constant ( )σ
σ =
( )NPSH
H
R
t
Note: If the cavitation constant is given, we can find the
maximum allowable elevation of the pump inlet (eye)
above the surface of the supply (suction) reservoir.

41. Selection of A Pump
It has been seen that the efficiency of a pump depends on the discharge,
head, and power requirement of the pump. The approximate ranges of
application of each type of pump are indicated in the following Figure.

42. Selection of A Pump
• In selecting a particular pump for a given system:
• The design conditions are specified and a pump is selected
for the range of applications.
• A system characteristic curve (H-Q) is then prepared.
• The H-Q curve is then matched to the pump characteristics
chart which is provided by the manufacturer.
• The matching point (operating point) indicates the actual
working conditions.

43. System Characteristic Curve
The total head, Ht , that the pump delivers includes the
elevation head and the head losses incurred in the system. The
friction loss and other minor losses in the pipeline depend on the
velocity of the water in the pipe, and hence the total head loss
can be related to the discharge rate
For a given pipeline system (including a pump or a group of
pumps), a unique system head-capacity (H-Q) curve can be
plotted. This curve is usually referred to as a system
characteristic curve or simply system curve. It is a graphic
representation of the system head and is developed by plotting
the total head, over a range of flow rates starting from zero to
the maximum expected value of Q.

44. ∑+= Lstatt hHH

45. )()( 12 QfnzzH p +−=
system
system
curve
0
20
40
60
80
100
120
0 0.2 0.4 0.6 0.8
Discharge (m3
/s)
Head(m)
Static head (z2-z1)
System with valve partially closed

46. System Characteristic Curve
H H ht stat L= + ∑

47. Pump Characteristic Curves
• Pump manufacturers provide information on the performance
of their pumps in the form of curves, commonly called pump
characteristic curves (or simply pump curves).
• In pump curves the following information may be given:
• the discharge on the x-axis,
• the head on the left y-axis,
• the pump power input on the right y-axis,
• the pump efficiency as a percentage,
• the speed of the pump (rpm = revolutions/min).
• the NPSH of the pump.

49. Pumps Group

52. • The pump characteristic curves are very important to help
select the required pump for the specified conditions.
• If the system curve is plotted on the pump curves in we may
produce the following Figure:
• The point of intersection is called the operating point.
• This matching point indicates the actual working conditions,
and therefore the proper pump that satisfy all required
performance characteristic is selected.
Matching the system and pump curves.

54. System Characteristic Curve
H H ht stat L= + ∑

55. Selected Pump

56. Elevated Tank

57. Selected Pump

58. System Curve & Pump Curve cases
Pump Curve
Pump Curve
Pump Curve
System Curve
System Curve
System Curve

59. Example 1
A Pump has a cavitation constant = 0.12, this pump was instructed
on well using UPVC pipe of 10m length and 200mm diameter, there
are elbow (ke=1) and valve (ke=4.5) in the system. the flow is 35m3
and The total Dynamic Head Ht = 25m (from pump curve)
f=0.0167
Calculate the maximum suction head
m
m
2.0headpressureVapour
69.9headpressureatm.
=
=

60. 325120
120
=×=×=
=
.HσNPSH
.σ
tR
m.
g
.
.
g
V
.h S
V 2830
2
111
54
2
54
22
=×==0630
2
111
2
22
.
g
.
g
V
h S
e ===
m.
g
.
.
.
g
V
D
L
fhfS 0530
2
111
20
10
01670
2
22
=××=×=
( ) ( )
m.h
....h
γ
P
γ
P
hhh(NPSH)
S
S
Vapor
Vapor
air
atm
mSf SSA
0886
2069.90630283005303
−=
−++−−=
−+−−±= ∑
Vapor
Vapor
air
atm
mSf SSA
γ
P
γ
P
hhh(NPSH) −+−−±= ∑
( )
m/s.
.π
.
A
Q
VS 111
20
4
0350
2
=
×
==

61. Example 2
For the following pump, determine the required pipes diameter to
pump 60 L/s and also calculate the needed power.
Minor losses 10 v2
/2g
Pipe length 10 km
roughness = 0.15 mm
hs = 20 m
Q
L/s
70 60 50 40 30 20 10 0
Ht 31 35 38 40.6 42.5 43.7 44.7 45
40 53 60 60 57 50 35 -Pη

62. To get 60 L/s from the pump hs + hL must be < 35 m
Assume the diameter = 300mm
Then:
( ) mh
fDKR
smVmA
f
Se
32.23
62.193.0
85.010000019.0
019.0,0005.0/,1025.2
/85.0,070.0
2
5
2
=
×
××
=
==×=
==
( ) m
gg
V
hm 37.0
2
85.010
2
10
22
=
×
=
×
=
mmhhh mfs 3569.43 >=++

63. Assume the diameter = 350mm
Then:
smVmA /624.0,0962.0 2
==
,48.10
0185.0,00043.0/,1093.1 5
mh
fDKR
f
Se
=
==×=
( ) m
gg
V
hm 2.0
2
624.010
2
10
22
=
×
=
×
=
mmhhh mfs 3568.30 <=++∴
kWW
HQ
P
p
t
i 87.388.38869
53.0
3581.91000 1000
60
==
×××
==
η
γ

64. Example 3
A pump was designed to satisfy the following system
Q (m3
/hr( 3 6 9
hf
(m( 12 20 38
m
m
25.0headpressureVapour
3.10headpressureatm.
=
=
mhd 13=
Pipe diameter is 50mm
( )
g
V
hL
2
24
Partsuction
2
×
=
Check whether the pump is suitable or not

66. 1- Draw the system curve and check the operation point
20m713hhH SdSTAT =+=+=

67. There are an operation point at:
Q = 9 m3
/hr H =58m
NPSHR =4.1
Then Check NPSHA
( )
( ) m.
g
.
h
m/s.
.
π
/
A
Q
V
L 02
2
27124
271
050
4
36009
2
2
=
×
=
=
×
==
4.11.05(NPSH)
0.2510.327(NPSH)
γ
P
γ
P
hhh(NPSH)
A
A
Vapor
Vapor
air
atm
mSSSA
<=
−+−−=
−+−−±= ∑f
pump is not suitable, the cavitation will occur

69. Multiple-Pump Operation
• To install a pumping station that can be effectively
operated over a large range of fluctuations in both
discharge and pressure head, it may be advantageous
to install several identical pumps at the station.
Pumps in Parallel Pumps in Series

70. (a) Parallel Operation
• Pumping stations frequently contain several (two or
more) pumps in a parallel arrangement.
Q1 Q2 Q3
Pump PumpPump
Manifold
Qtotal
Qtotal =Q1+Q2+Q3

71. • In this configuration any number of the pumps can be
operated simultaneously.
• The objective being to deliver a range of discharges,
i.e.; the discharge is increased but the pressure head
remains the same as with a single pump.
• This is a common feature of sewage pumping stations
where the inflow rate varies during the day.
• By automatic switching according to the level in the
suction reservoir any number of the pumps can be
brought into operation.

72. How to draw the pump curve for pumps in
parallel???
• The manufacturer gives the pump curve for a single
pump operation only.
• If two or pumps are in operation, the pumps curve
should be calculated and drawn using the single pump
curve.
• For pumps in parallel, the curve of two pumps, for
example, is produced by adding the discharges of the
two pumps at the same head (assuming identical
pumps).

73. Pumps in series & Parallel
Pumps in Parallel:
mnm3m2m1m
nj
1j
n321
HHHHH
QQQQQQ
=====
==+++= ∑
=
=



75. (b) Series Operation
• The series configuration which is used whenever we
need to increase the pressure head and keep the
discharge approximately the same as that of a single
pump
• This configuration is the basis of multistage pumps;
the discharge from the first pump (or stage) is
delivered to the inlet of the second pump, and so on.
• The same discharge passes through each pump
receiving a pressure boost in doing so

76. Q
Pump PumpPump
Q
Htotal =H1+H2+H3

77. How to draw the pump curve for pumps in
series???
• the manufacturer gives the pump curve for a single
pump operation only.
• For pumps in series, the curve of two pumps, for
example, is produced by adding the heads of the two
pumps at the same discharge.
• Note that, of course, all pumps in a series system
must be operating simultaneously

78. H
Q
Q1
H1
H1
H1
2H1
H1
3H1
Single pump
Two pumps
in series
Three pumps
in series

79. Constant- and Variable-Speed Pumps
• The speed of the pump is specified by the angular
speed of the impeller which is measured in
revolution per minutes (rpm).
• Based on this speed, N , pumps can be divided into
two types:
• Constant-speed pumps
• Variable-speed pumps

80. Constant-speed pumps
• For this type, the angular speed , N , is constant.
• There is only one pump curve which represents the
performance of the pump

81. Variable-speed pumps
• For this type, the angular
speed , N , is variable, i.e.;
pump can operate at
different speeds.
• The pump performance is
presented by several pump
curves, one for each speed
• Each curve is used to suit
certain operating
requirements of the
system.

82. Similarity Laws:
Affinity laws
• The actual performance characteristics curves of
pumps have to be determined by experimental testing.
• Furthermore, pumps belonging to the same family,
i.e.; being of the same design but manufactured in
different sizes and, thus, constituting a series of
geometrically similar machines, may also run at
different speeds within practical limits.
• Each size and speed combination will produce a
unique characteristics curve, so that for one family of
pumps the number of characteristics curves needed to
be determined is impossibly large.

83. • The problem is solved by the application of
dimensional analysis and by replacing the variables
by dimensionless groups so obtained. These
dimensionless groups provide the similarity
(affinity) laws governing the relationships between
the variables within one family of geometrically
similar pumps.
• Thus, the similarity laws enable us to obtain a set of
characteristic curves for a pump from the known test
data of a geometrically similar pump.

84. (a) Change in pump speed
(constant size)
• If a pump delivers a discharge Q1 at a head H1 when
running at speed N1, the corresponding values when
the same pump is running at speed N2 are given by
the similarity (affinity) laws:
Q
Q
N
N
2
1
2
1
= H
H
N
N
2
1
2
1
2
=






P
P
N
N
i
i
2
1
2
1
3
=






where Q = discharge (m3
/s, or l/s).
H = pump head (m).
N = pump rotational speed (rpm).
Pi = power input (HP, or kw).

85. • Therefore, if the pump
curve for speed N1 is
given, we can construct
the pump curve for the
speed N2 using previous
relationships.
Effect of speed change on pump
characteristic curves.
N1
N2

86. (b) Change in pump size
(constant speed)
• A change in pump size and therefore, impeller
diameter (D), results in a new set of characteristic
curves using the following similarity (affinity) laws:
Q
Q
D
D
2
1
2
1
3
=






H
H
D
D
2
1
2
1
2
=






P
P
D
D
i
i
2
1
2
1
5
=






where D = impeller diameter (m, cm).
Note : D indicated the size of the pump

87. Example 4

88. Solution

90. Specific Speed
• Pump types may be more explicitly defined by the
parameter called specific speed (Ns) expressed by:
Where: Q = discharge (m3
/s, or l/s).
H = pump total head (m).
N = rotational speed (rpm).
N
N Q
H
s = 3
4

91. • This expression is derived from dynamical similarity
considerations and may be interpreted as the speed in
rev/min at which a geometrically scaled model would have
to operate to deliver unit discharge (1 l/s) when generating
unit head (1 m).
• The given table shows the range of Ns values for the turbo-
hydraulic pumps:
Pump type Ns range (Q - l/s, H-m)
centrifugal up to 2600
mixed flow 2600 to 5000
axial flow 5000 to 10 000

92. Example 5
• A centrifugal pump running at 1000 rpm gave the following
relation between head and discharge:
Discharge (m3
/min) 0 4.5 9.0 13.5 18.0 22.5
Head (m) 22.5 22.2 21.6 19.5 14.1 0
• The pump is connected to a 300 mm suction and delivery pipe
the total length of which is 69 m and the discharge to
atmosphere is 15 m above sump level. The entrance loss is
equivalent to an additional 6m of pipe and f is assumed as
0.024.
1. Calculate the discharge in m3
per minute.
2. If it is required to adjust the flow by regulating the pump
speed, estimate the speed to reduce the flow to one-half

93. 1) System curve:
• The head required from pump =
static + friction + velocity head
• Hstat = 15 m
• Friction losses (including equivalent entrance losses) =
H H h h h h
V
gt stat f d md f s m s
d
= + +∑ + + +∑
2
2
52
2
8
Dg
QLf
hhhh mdfdmsfs
π
=+++∑ ∑
2
52
)3.0(
)669(024.08
Q
gπ
+××
=
2
21.61 Q= where Q in m3
/s

94. • Velocity head in delivery pipe =
where Q in m3
/s
Thus:
• where Q in m3
/s
or
• where Q in m3
/min
• From this equation and the figures given in the problem the
following table is compiled:
2
22
2.10
2
1
2
Q
A
Q
gg
Vd
=





=
2
41.7115 QHt +=
23
1083.1915 QHt
−
×+=
Discharge (m3/min) 0 4.5 9.0 13.5 18.0 22.5
Head available (m) 22.5 22.2 21.6 19.5 14.1 0
Head required (m) 15.0 15.4 16.6 18.6 21.4 25.0

95. Pump and Sytem Curves
0
2
4
6
8
10
12
14
16
18
20
22
24
26
28
0 2 4 6 8 10 12 14 16 18 20 22 24
Discharge, Q (m
3
/min)
Head,Ht(m)
Pump Curve
System Curve

96. From the previous Figure, The operating point is:
• QA = 14 m3
/min
• HA = 19 m
• At reduced speed: For half flow (Q = 7 m3
/min) there
will be a new operating point B at which:
• QB = 7 m3
/min
• HB = 16 m
• HomeWork
How to estimate the new speed ?????

97. Pump and Sytem Curves
0
2
4
6
8
10
12
14
16
18
20
22
24
26
28
0 2 4 6 8 10 12 14 16 18 20 22 24
Discharge, Q (m
3
/min)
Head,Ht(m)
Pump Curve
System Curve
A
B
A
B

98. Q
Q
N
N
2
1
2
1
= H
H
N
N
2
1
2
1
2
=






2






=
BB Q
Q
H
H
22
2
327.0
7
16
QQH ==
This curve intersects the original curve for N1 = 1000 rpm
at C where Qc= 8.2 m3
/ hr and Hc= 21.9 m, then
1
2
N
N
Q
Q
C
B
=
10002.8
7 2N
= N2 = 855rpm

99. Pump and Sytem Curves
0
2
4
6
8
10
12
14
16
18
20
22
24
26
28
0 2 4 6 8 10 12 14 16 18 20 22 24
Discharge, Q (m
3
/min)
Head,Ht(m)
Pump Curve
System Curve
A
B
C
A
B
C

100. Example 6
Abbreviations:
G.V = Gate Valve
C.V = Check Valve
A.V = Air release Valve
E.R = Eccentric Reducer
C.I = Concentric increase
I.N = Inlet Nozzle
O.N = Outlet Nozzle
S.P = Suction Pipe
D.P = Delivery Pipe
W.W = Wet Well
D.W = Dry Well

101. Data:
1. Flow rates and dimensions:
Qmax = 0.05 m3
/s Qmin = 0.025 m3
/s
LS.P = 5.0 m LD.P = 513.5 m
DS.P = 250mm DD.P = 200mm
Hstat = 5.3 m, hS = 3.0 m
2. Minor Losses Coefficients (k):
G.V = 0.1 C.V = 2.5 A.V = 0.05,
E.R = 0.1 C.I = 0.05 Elbow = 0.2
Bends in D.P = 0.05,
Entrance of S.P = 0.3 (bell mouth)
3. Coefficient of friction:
f = 0.02 (assumed constant).
φ φI N O N mm. .= = 150

102. 4. Pump characteristic curves:

103. Required??
The given Figure shows a pump station.
Use the pump characteristic curves and the data given above to:
a) Choose a suitable pump which satisfies the requirements of
the piping system shown,
b) Find the power and efficiency of the pump,
c) Find the overall efficiency (motor and pump) if the motor
efficiency is given to be 90%, also find the required power
input to the motor.
d) Check the pump for cavitation at T = 25o
C

104. Solution
A. Pump Selection:
• The first step in selecting a pump is to draw the system
curve:
• To draw the system curve we need to calculate the values of
Ht that correspond to several values of Q, using :
• We start with Qmax = 0.05 m3
/s as the first value of Q in the
system and find the corresponding Ht
H H ht stat L= + ∑ or
H H h h h h
V
gt stat f s m s f d md
d
= + + ∑ + + +∑
2
2

105. Head losses in the suction pipe:
• For Qmax = 0.05 m3
/s.
• Friction losses:
• Minor losses:
V
Q
A
m ss
s
= = =max . *
(0. )
. /
005 4
25
1022
π
h f
L
D
V
g
mfs
s
s
s
= = =
2 2
2
0 02
50
0 25
102
2 9 81
0 021. *
.
.
*
( . )
* .
.
hms
V
g
ms
∑ = + + = =
2 2
2
0 3 01 01 05
102
2 9 81
0 027( . . . ) . *
( . )
* .
.

106. Head losses in the delivery pipe:
• For Qmax = 0.05 m3
/s.
• Friction losses:
• Minor losses:
V
Q
A
m sd
d
= = =max . *
( . )
. /
0 05 4
0 20
162
π
h f
L
D
V
g
mfd
d
d
d
= = =
2 2
2
0 02
5135
0 2
16
2 9 81
6 7. *
.
.
*
( . )
* .
.
hmd
V
g
md
∑ = + + + + + + = =
2 2
2
0 2 0 05 0 2 0 05 2 5 01 2 0 05 32
16
2 9 81
0 42( . . . . . . * . ) . *
( . )
* .
.

107. Therefore
H mwct = + + + + + = + =53 0 027 0 021 0 42 6 7
16
2 9 81
53 7 3 12 6
2
. . . . .
( . )
* .
. . .
H H h h h h
V
gt stat f s m s f d md
d
= + + ∑ + + +∑
2
2
therefore, we found the first point on the system curve:
(Q, H) = (0.05, 12.6)
which is the operating point of the system at Qmax.

108. • If we repeat previous step for several Q values it will possible
to draw the (Q, H) or system curve.
• However, it will be very cumbersome and long procedure.
• So, another procedure will be adopted:
• where K is constant and it is a unique property of the given
system.
H H ht stat L= + ∑
hL h h h h
V
g
k
f L
D
V
g
k
f L
D
f s m s f d md
s
s
s
s
d
d
d
d
∑ = + ∑ + + = ∑ + + ∑ +∑
2 2
2 2
( ) ( )
hL
Q
A g
k
f L
D
Q
A g
k
f L
Ds
s
s
s d
d
d
d
∑ = ∑ + + ∑ +
2
2
2
2
2 2
( ) ( )
hL Q K Q K Q K K∑ = ′ + ′′ = ′ + ′′2 2 2
( ) ( ) ( )
hL Q K∑ = 2

109. • Therefore
• Thus:
)2.435.51(
2
)5.04(
2 2
2
2
2
+++=∑
gA
Q
gA
Q
L
h
ds
22
64.51)2.435.51(15.21)5.04( QQ
L
h +++=∑
2
88.2963 Q
L
h =∑
2
88.29633.5 QHt +=

110. • for a given Qi , we have
• for Qmax , we have
• Therefore
• Or
hLi Q Ki∑ = 2
hL Q Kmax max∑ = 2
h
h
Q
Q
Li
L
i∑
∑
=
max max
2
2
h
Q
Q
hLi
i
L∑ =





 ∑
max
max*
2
From previous calculations we obtained for Qmax
= 0.05 m3
/s. Therefore, we can use the above equation along with the
above values to find for several values of Qi . In order to
calculate Hti.
hL mwcmax .∑ = 7 3
hLi∑

112. System curve

113. Operating
point
System curve
12.6
It is clear from the above figure that the required pump is the
35-cm impeller pump

114. Pump Power Input and Efficiency
• From the pump curve we can read Pi = 7.5 kw
• and hence
P kw HPi = = ≅75
75 10
745
10
3
.
. *
η
γ
p
o
i
t
i
P
P
Q H
P
= = = = = ≅
1000 9 81 0 05 12 60
7 5 1000
618
7 6
0824 82%
* . * . * .
. *
.
.
.

115. Overall Efficiency and Motor Power Input
• Overall efficiency
• and hence
η η ηo p m= = = =0 9 082 0 738 738. * . . . %
ηo
o
m m
P
P P
= = =
618
0 738
.
.
P kw HPm ≅ =8 27 112. .

116. Check for Cavitation:
• To prevent cavitation we must have:
(NPSH)A (NPSH)R
• From pump curve figure we can read:
(NPSH)R = 3 m at Qmax = 0.05 m3
/s.
• For water at T=25o
C, Patm= 101 kN/m2
, and Pvapor = 3.17 kN/m2
.
• Using the equation
• we can write
• no cavitation.
≥
( )NPSH
P
h h h
P
A
atm
s f s ms
vapor
= + − − −∑
γ γ
( )
*
* .
. .
. *
* .
NPSH A = + − − −
101 1000
1000 9 81
3 0 021 0 027
317 1000
1000 9 81
( ) .NPSH m mA = >>12 924 3

117. Home Work