This document discusses water pumps, including their definition, classification, components, and operation. It describes how pumps work to convert mechanical energy into hydraulic energy to move water from lower to higher points. Pumps are classified as either turbo-hydraulic (centrifugal or positive displacement). Centrifugal pumps are the most common and their components and operation are explained in detail. Key concepts discussed include pump efficiency, cavitation, net positive suction head (NPSH), and selecting the appropriate pump based on system characteristics.
Basics Fundamentals and working Principle of Centrifugal Pump.SHASHI BHUSHAN
Basics Fundamentals and working Principle of Centrifugal Pump. Centrifugal pumps are the rotodynamic machines that convert mechanical energy of shaft into kinetic and pressure energy of Fluid which may be used to raise the level of fluid. A centrifugal pump is named so, because the energy added by the impeller to the fluid is largely due to centrifugal effects.
Centrifugal Pumps - Concept E-Learning Program - Study MaterialPankaj Khandelwal
Study Material of Koncept Learning Center's Concept E-Learning Program on Distillation .
The course is directed by Mr. Pankaj Khandelwal
Centrifugal pump is one of the widely used liquid transportation rotary equipment in most of the industries either for the chemical transfer or utilities circulation.
Like any pumps, it also increases fluid energy due to which liquid is transferred from its low energy source to high energy destination. Impeller plays a major role for this purpose. Impeller is driven by the suitable drive either by the electric motor or diesel engine set.
Centrifugal pump supplier’s have their own pump designs while users have vary much varied applications from low flow & high differential pressure to high flow & low differential pressure. Thus the selection of centrifugal pumps is critical. This is done by matching duty point determined by the user and the characteristics curves supplied by the suppliers.
Contents:
1) Why Pump is required?
2) Pumping System
3) Industrial applications
4) Parts of Pumps
5) MWC Concepts
6) Fluid Energy Concepts
7) Cavitation Concepts
8) Characteristics Curves
9) Hydraulic Calculations
10) Pump Selection
For course details - klcenter@gmail.com / www.konceptlearningcenter.com
Call / Whatsapp - 8237829150 or 9371121220
Prithviraj Khandelwal
Basics Fundamentals and working Principle of Centrifugal Pump.SHASHI BHUSHAN
Basics Fundamentals and working Principle of Centrifugal Pump. Centrifugal pumps are the rotodynamic machines that convert mechanical energy of shaft into kinetic and pressure energy of Fluid which may be used to raise the level of fluid. A centrifugal pump is named so, because the energy added by the impeller to the fluid is largely due to centrifugal effects.
Centrifugal Pumps - Concept E-Learning Program - Study MaterialPankaj Khandelwal
Study Material of Koncept Learning Center's Concept E-Learning Program on Distillation .
The course is directed by Mr. Pankaj Khandelwal
Centrifugal pump is one of the widely used liquid transportation rotary equipment in most of the industries either for the chemical transfer or utilities circulation.
Like any pumps, it also increases fluid energy due to which liquid is transferred from its low energy source to high energy destination. Impeller plays a major role for this purpose. Impeller is driven by the suitable drive either by the electric motor or diesel engine set.
Centrifugal pump supplier’s have their own pump designs while users have vary much varied applications from low flow & high differential pressure to high flow & low differential pressure. Thus the selection of centrifugal pumps is critical. This is done by matching duty point determined by the user and the characteristics curves supplied by the suppliers.
Contents:
1) Why Pump is required?
2) Pumping System
3) Industrial applications
4) Parts of Pumps
5) MWC Concepts
6) Fluid Energy Concepts
7) Cavitation Concepts
8) Characteristics Curves
9) Hydraulic Calculations
10) Pump Selection
For course details - klcenter@gmail.com / www.konceptlearningcenter.com
Call / Whatsapp - 8237829150 or 9371121220
Prithviraj Khandelwal
Pumps are widely used in process plants to transfer fluid from one point to the other and the Process Engineer is often required to specify the correct size of pumps that will optimize system performance. Though pump sizing can easily be performed using software such as Pipe-Flo®, understanding the basic principle will not only aid one to better interpret the results obtained by pump sizing software but also to better design pumps. Centrifugal pump sizing overview is presented in this tutorial.
Positive displacement pumps are reciprocating and rotary pumps that move liquid by the positive displacement of liquid volume. In this presentation, you will learn the operating principles and performance characteristics of positive displacement pumps, what determines their capacity, pressure, horsepower and efficiency, and how NPSH is calculated. You will also learn the basic types of reciprocating and rotary pumps, including piston pumps, plunger pumps, diaphragm pumps, direct-acting steam and air pumps, and rotary lobe, vane, gear and screw pumps, and how these pumps differ from each other in design and performance.
Pumps are widely used in process plants to transfer fluid from one point to the other and the Process Engineer is often required to specify the correct size of pumps that will optimize system performance. Though pump sizing can easily be performed using software such as Pipe-Flo®, understanding the basic principle will not only aid one to better interpret the results obtained by pump sizing software but also to better design pumps. Centrifugal pump sizing overview is presented in this tutorial.
Positive displacement pumps are reciprocating and rotary pumps that move liquid by the positive displacement of liquid volume. In this presentation, you will learn the operating principles and performance characteristics of positive displacement pumps, what determines their capacity, pressure, horsepower and efficiency, and how NPSH is calculated. You will also learn the basic types of reciprocating and rotary pumps, including piston pumps, plunger pumps, diaphragm pumps, direct-acting steam and air pumps, and rotary lobe, vane, gear and screw pumps, and how these pumps differ from each other in design and performance.
Southern Methodist UniversityBobby B. Lyle School of Engineeri.docxwhitneyleman54422
Southern Methodist University
Bobby B. Lyle School of Engineering
CEE 2342/ME 2342 Fluid Mechanics
Roger O. Dickey, Ph.D., P.E.
V. STEADY PIPE FLOW
D. Pump Selection
Reading Assignment:
Chapter 12 Turbomachines
Section 12.4 – The Centrifugal Pump, pp. 687-700
E. Pump Selection
Pump Applications –
Pumps are used in a wide array of engineering applications including:
Low-lift pumps high-volume, low-head pumps used to elevate fluids, e.g., elevating water from a supply source to a water treatment plant or wastewater from a gravity sewer to a wastewater treatment plant.
High-service pumps used to deliver fluids under “adequate” pressure throughout a distribution piping network, or through long transmission pipelines.
Booster pumps used to increase fluid pressure at intermediate points along transmission pipelines, or within distribution piping networks.
Recirculation and transfer pumps used to convey fluids for one unit operation or process to another within an engineered system or facility.
Well pumps used to lift water from ground water aquifers for water supply purposes.
Chemical metering pumps used to deliver reagent chemicals at precisely controlled rates to chemical processes.
Fire pumps used for delivering high flow rates at high pressures for firefighting.
Sludge pumps used to convey thick slurries from one unit operation or process to another within an engineered system or facility.
Sampling pumps used in both portable and fixed equipment designed to collect precise sample volumes over precise time intervals within engineered systems or facilities.
Pump Types -
Pumps can be broadly classified as either,
Dynamic
Positive displacement
Dynamic pumps deliver flow rates that vary as a function of the discharge head on the pump.
Conversely, positive displacement pumps deliver flow rates that remain relatively constant, regardless of changes in the discharge head.
Dynamic pumps can be further subdivided into classes,
Centrifugal – axial flow, radial flow, mixed flow, and peripheral flow pumps
Special effect – including eductor (or jet), ejector, and air lift pumps
10
Positive displacement pumps can be further subdivided into classes,
Reciprocating – piston (or plunger) and diaphragm pumps
Rotary – including gear, lobe, screw, progressing cavity, vane, and peristaltic (or tubing) pumps
11
Centrifugal pumps are the most widely used type in engineering applications including:
Low-lift – Vertical Turbine
Axial Flow
Archimedes Screw
High-service – Split-case, double suction centrifugal
Vertical-turbine Pump
Axial Flow (Vertical Propeller) Pump
Archimedes Screw Pumps
Split-case, Double-suction Centrifugal Pump
Booster
Recirculation and transfer
Well – down-hole pumps
Firefighting
Figure 12.6 – Schematic of Basic Elements of Centrifugal Pumps
Centrifugal Pumps
Submersible
Vertical Sump Pump
Horizontal
Fire Pump System, Internal Combustion Driver
Ce.
The hydraulic machines which convert the mechanical energy into hydraulic energy are called pumps.”
“If the mechanical energy is converted into pressure energy or kinetic energy by means of centrifugal force
acting on the fluid, the hydraulic machine is called Centrifugal pump.”
Industrial Training at Shahjalal Fertilizer Company Limited (SFCL)MdTanvirMahtab2
This presentation is about the working procedure of Shahjalal Fertilizer Company Limited (SFCL). A Govt. owned Company of Bangladesh Chemical Industries Corporation under Ministry of Industries.
Democratizing Fuzzing at Scale by Abhishek Aryaabh.arya
Presented at NUS: Fuzzing and Software Security Summer School 2024
This keynote talks about the democratization of fuzzing at scale, highlighting the collaboration between open source communities, academia, and industry to advance the field of fuzzing. It delves into the history of fuzzing, the development of scalable fuzzing platforms, and the empowerment of community-driven research. The talk will further discuss recent advancements leveraging AI/ML and offer insights into the future evolution of the fuzzing landscape.
Explore the innovative world of trenchless pipe repair with our comprehensive guide, "The Benefits and Techniques of Trenchless Pipe Repair." This document delves into the modern methods of repairing underground pipes without the need for extensive excavation, highlighting the numerous advantages and the latest techniques used in the industry.
Learn about the cost savings, reduced environmental impact, and minimal disruption associated with trenchless technology. Discover detailed explanations of popular techniques such as pipe bursting, cured-in-place pipe (CIPP) lining, and directional drilling. Understand how these methods can be applied to various types of infrastructure, from residential plumbing to large-scale municipal systems.
Ideal for homeowners, contractors, engineers, and anyone interested in modern plumbing solutions, this guide provides valuable insights into why trenchless pipe repair is becoming the preferred choice for pipe rehabilitation. Stay informed about the latest advancements and best practices in the field.
Vaccine management system project report documentation..pdfKamal Acharya
The Division of Vaccine and Immunization is facing increasing difficulty monitoring vaccines and other commodities distribution once they have been distributed from the national stores. With the introduction of new vaccines, more challenges have been anticipated with this additions posing serious threat to the already over strained vaccine supply chain system in Kenya.
Saudi Arabia stands as a titan in the global energy landscape, renowned for its abundant oil and gas resources. It's the largest exporter of petroleum and holds some of the world's most significant reserves. Let's delve into the top 10 oil and gas projects shaping Saudi Arabia's energy future in 2024.
Courier management system project report.pdfKamal Acharya
It is now-a-days very important for the people to send or receive articles like imported furniture, electronic items, gifts, business goods and the like. People depend vastly on different transport systems which mostly use the manual way of receiving and delivering the articles. There is no way to track the articles till they are received and there is no way to let the customer know what happened in transit, once he booked some articles. In such a situation, we need a system which completely computerizes the cargo activities including time to time tracking of the articles sent. This need is fulfilled by Courier Management System software which is online software for the cargo management people that enables them to receive the goods from a source and send them to a required destination and track their status from time to time.
Quality defects in TMT Bars, Possible causes and Potential Solutions.PrashantGoswami42
Maintaining high-quality standards in the production of TMT bars is crucial for ensuring structural integrity in construction. Addressing common defects through careful monitoring, standardized processes, and advanced technology can significantly improve the quality of TMT bars. Continuous training and adherence to quality control measures will also play a pivotal role in minimizing these defects.
CFD Simulation of By-pass Flow in a HRSG module by R&R Consult.pptxR&R Consult
CFD analysis is incredibly effective at solving mysteries and improving the performance of complex systems!
Here's a great example: At a large natural gas-fired power plant, where they use waste heat to generate steam and energy, they were puzzled that their boiler wasn't producing as much steam as expected.
R&R and Tetra Engineering Group Inc. were asked to solve the issue with reduced steam production.
An inspection had shown that a significant amount of hot flue gas was bypassing the boiler tubes, where the heat was supposed to be transferred.
R&R Consult conducted a CFD analysis, which revealed that 6.3% of the flue gas was bypassing the boiler tubes without transferring heat. The analysis also showed that the flue gas was instead being directed along the sides of the boiler and between the modules that were supposed to capture the heat. This was the cause of the reduced performance.
Based on our results, Tetra Engineering installed covering plates to reduce the bypass flow. This improved the boiler's performance and increased electricity production.
It is always satisfying when we can help solve complex challenges like this. Do your systems also need a check-up or optimization? Give us a call!
Work done in cooperation with James Malloy and David Moelling from Tetra Engineering.
More examples of our work https://www.r-r-consult.dk/en/cases-en/
Overview of the fundamental roles in Hydropower generation and the components involved in wider Electrical Engineering.
This paper presents the design and construction of hydroelectric dams from the hydrologist’s survey of the valley before construction, all aspects and involved disciplines, fluid dynamics, structural engineering, generation and mains frequency regulation to the very transmission of power through the network in the United Kingdom.
Author: Robbie Edward Sayers
Collaborators and co editors: Charlie Sims and Connor Healey.
(C) 2024 Robbie E. Sayers
Planning Of Procurement o different goods and services
Pumps
1. Water Pumps
The Islamic University of Gaza
Faculty of Engineering
Civil Engineering Department
Hydraulics - ECIV 3322
Chapter 5Chapter 5
2. 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. • 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
11. 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
12. 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
13. 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.
14.
15.
16. 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:
17. 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
18. 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.
19. Note that a centrifugal pump can be
either submersible (wet) or dry.
20.
21. 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.
22. Hydraulic Analysis of Pumps and Piping Systems
Ht
hd
Hstat
hs
Hms
Hmd
Datum pump
center line
hfs
hfd
Case 1
24. 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= ±
25. • 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= ±
26. • 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)
27. • 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 ino eq. (1)
Eq.(3)
Case 1
28. • 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.
29. • 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. 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:
32. 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.
33. • 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
34. • 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 ??
35. 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.
36. How we avoid Cavitation ??
• For proper pump operation (no cavitation) :
(NPSH)A > (NPSH)R
37. Determination of
(NPSH)A
datum
hs
applying the energy equation between
point (1) and (2), datum at pump
center line
γγ
γγγγ
γγ
γγ
Vapor
LS
atm
A
Vapor
LS
atmVaporSS
LS
atmSS
L
SS
S
atm
P
hh
P
NPSH
P
hh
PP
g
VP
hh
P
g
VP
h
g
VP
h
P
−−−=
−−−=−+
−−=+
++=−
∑
∑
∑
∑
)(
2
2
2
2
2
2
38. ( )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
=
=
=
39. 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.
40. 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.
41. 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.
42. 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.
46. 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.
51. • 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.
57. System Curve & Pump Curve cases
Pump Curve
Pump Curve
Pump Curve
System Curve
System Curve
System Curve
58. 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. 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
61. 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 >=++
62. 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
63. 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
64.
65. 1- Draw the system curve and check the operation point
20m713hhH SdSTAT =+=+=
66. 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
Vaporatm
mSSSA
<=
−+−−=
−+−−±= ∑f
pump is not suitable, the cavitation will occur
67.
68. 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
69. (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
70. • 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.
71. 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).
72. Pumps in series & Parallel
Pumps in Parallel:
mnm3m2m1m
nj
1j
n321
HHHHH
QQQQQQ
=====
==+++= ∑
=
=
73.
74. (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. 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. 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
79. 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
80. 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.
81. 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.
82. • 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.
83. (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).
84. • 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
85. (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
89. 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
90. • 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
91. 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
92. 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
93. • 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. 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 ?????
96. 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
102. 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
103. 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
104. 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( . . . ) . *
( . )
* .
.
105. 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( . . . . . . * . ) . *
( . )
* .
.
106. 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.
107. • 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. • 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∑
113. 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%
* . * . * .
. *
.
.
.
114. 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. .
115. 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