IRJET- Modelling, Simulation and Testing of Diesel Engine Water Pump

International Research Journal of Engineering and Technology (IRJET) e-ISSN: 2395-0056
Volume: 06 Issue: 06 | June 2019 www.irjet.net p-ISSN: 2395-0072
© 2019, IRJET | Impact Factor value: 7.211 | ISO 9001:2008 Certified Journal | Page 571
Modelling, Simulation and Testing of Diesel Engine Water Pump
Prof. Rahul T. Dhanore1, Sandeep D. Jadhav2, Arvind P. Kaware3, Amit R. Karkhile4,
Shubham L. Lilhare5
1Assistant Professor, Department of Mechanical Engineering, JSPM Imperial College of Engineering &
Research, Pune.
2,3,4,5 Research Scholar & JSPM Imperial College of Engineering & Research, Pune, India.
---------------------------------------------------------------------***---------------------------------------------------------------------
Abstract - Centrifugal pump is most common pump used in
industries, agriculture, domestic applications and the diesel
engine for cooling purpose. For cost-effectivedesignofpumpit
is very crucial to predict their performance in advance before
manufacturing them, which requires understanding of the
flow behavior in different parts of the pump. Experimental
model is tedious, time consuming and costly. Conversely
theoretical approach merely gives a value but is unable to
determine the root cause of the problem. In recent years CFD
play a very Key role for prediction of the flow through pumps.
The objective was to obtain higher head then the existing to
increase of pump used in the diesel engine. The increase
efficiency will lead to rapid cooling and faster heatdissipation
in diesel engine. To get this certain changes implemented in
the design and its validation was done by comparing
Simulation result with experimental result.
Key Words: CFD, Centrifugal pump, Simulation, pressure
head, experimental testing etc.
1. INTRODUCTION
A centrifugal pump is a mechanical device designed to
move a fluid by means of the transfer of rotational energy
from one or more driven rotors, called impellers. Fluid
enters the rapidly rotating impeller along its axis and is cast
out by centrifugal force along its circumference through the
impeller’s vane tips. The action of the impellerincreasesthe
fluid’s velocity and pressure and also directs it towards the
pump outlet. The pump casing is specially designed to
constrict the fluid from the pump inlet, direct it into the
impeller and then slow and control the fluid before
discharge.
1.1 Working of centrifugal pump
Fluid enters the impeller at its axis (the ‘eye’) and exits
along the circumference between the vanes. The impeller,
on the opposite side to the eye, is connected through a drive
shaft to a motor and rotated at high speed (typically 500-
5000rpm). The rotational motionoftheimpelleraccelerates
the fluid out through the impeller vanes into the pump
casing. There are two basic designs of pump casing
volute and diffuser. The purpose in both designs is to
translate the fluid flow into a controlled discharge at
pressure. In a volute casing, the impeller is offset, effectively
creating a curved funnel with an increasing cross-sectional
area towards the pump outlet. This design causes the fluid
pressure to increase towards the outlet.
Fig. 1.1.1 Working of centrifugal pump
1.2 Computational Fluid Dynamics
Computational fluid dynamics is the art of replacing the
governing partial differential equations of fluid flow with
numbers, and advancing thesenumbersinspaceand/ortime
to obtain a final numerical description of the complete flow
field of interest.
Fig. 1.2.1 work flow CFD simulation
Firstly, we have a fluid problem. To solvethisproblem,we
should know the physical properties of fluid by using Fluid
Mechanics. Then we can use mathematical equations to

describe these physical properties. This is Navier-Stokes
Equation and it is the governing equation of CFD. As the
Navier-Stokes Equation is analytical, human canunderstand
it and solve them on a piece of paper. But if we want to solve
this equation by computer, we have to translate it to the
discretized form. The translators are numerical
discretization methods, such as Finite Difference, Finite
Element, Finite Volume methods. Consequently, we also
need to divide our whole problem domain into many small
parts because our discretization is based on them. Then, we
can write programs to solve them.
1.2 CFD Analysis Of Centrifugal Pump
CFD simulation makes it possible to visualize the flow
condition inside a centrifugal pump and provide valuable
information about the pump’s hydraulics design. Simulation
results are used to calculate and predict the performance of
a centrifugal pump whichreplacesthelengthyandexpensive
physical experiment of the past. A great deal of work is
saved, in addition to shortening the entire design cycle.
Computational fluid dynamics isbeing progressivelyapplied
in the design of centrifugal pumps. Thus CFD is most
dominant tool for pump designers. The application of CFD
tools is quiet common in industry today. Many tasks can be
solved much faster and cheaper then means of experiments.
With the aid of CFD approach, the complex internal flow
through different component of pump can be studied at the
different operating conditionswhichhelpinimprovement in
the performance at off-design conditions.
Computational fluid dynamics (CFD) is an advanced
computer-based design and analysis technique. A
computational model is designed using CFD. CFD uses
Numerical methods to solve the fundamental nonlinear
differential equations. Computational Fluid Design has
become very popular approach for designing the such
complex geometry. Design can be improved by analyzing
arrangements of multiple geometry using an identical set of
simplification. A better performancecanbeobtainedwiththe
mathematical and computational error and using these
resources in different manners accuracy can be improved
using larger number of elements and due to this techniques
results obtained in a very short time.
2. LITERATURE REVIEW
[1]CFD Analysis of domestic centrifugal pump for
performance enhancement- Satish M Rajmane work to
improve the head of regenerative pump whichisavailablein
the market. The dismantle pump and the geometrical
dimensions were measured using the geometric details the
numerical model was constructed and the CFD analysis was
carried out with ANSYS (Fluent) software thus validate the
numerical model with calculation by analyzing the existing
report recompiled with the analytic solutions.
Boundary conditions used by them are Rotational speed =
2880 rpm, Working fluid = Water, Turbulence model = K-
Omega viscous with turbulence intensity 5%.
They made three modifications to analysis:-
1.Providing additional splitter in Outlet.
2. Increase the no vanes.
3. Inclining the vanes.
He conclude that with each of the modification there is
increase in the head :-
1.By first modification, they found 6 m increase in the
head of the pump.
2. By second modification, they found 7 m increase in the
head of the pump.
3.By third modification, they found 5 m increase in the
head of the pump.
[2]Experimental and CFD Analysis of Centrifugal Pump
Impeller “ A Case Study”-Prof. Kamlesh H. Thakkar analysis
the centrifugal pump usingCFDtechniqueandpredicting the
performance of a mixed flow impellerofcentrifugal pump. In
this paper experimental investigation were conducted on
centrifugal pump with 111 m outlet impeller diameter,
backward curved blades, nominal discharge of 4 liter per
second to assess the impact of various operating condition
like head, discharge, power, and speed on the performance
of pump. Further the impeller is modeled using solid work
software and CFD analysis is carried out using Ansys CFX on
developed model of impeller to predict theperformanceand
verify with the experimental result of pump. After
experiment at various operating condition, the best
operating condition suggested that flow rate 6.25 lps , head
12.49 m, and efficiency of 3.61 % for selected pump.
[3]Md. Abdul Raheem Junaidia , N.B.V Laksmi Kumari ,
Mohd. Abdul Samad , G.M.Sayeed Ahmed-In this research
work the study of fitting the Inner guide vanes at the
entrance of centrifugal fan impeller is to resolve the non-
uniformity of the flow and to get rid of the vortices that are
generated by the existence of Inner distortion. The main
purpose of this work is to evaluate the use of the Inner guide
vanes (IGV) made of sheet metal and fiber reinforced plastic
to improve the fan performance and saving of energy. For
this purpose the ring of blades in radial direction i.e. Radial
cascade, with different exit blade angles of impellers is used.
Comparison with free inner (without IGV)fansisperformed.
Measurement of static head, shaft power and energysavings
at different loads are made for dissimilar cases. The study of
these measurements gives some informationconcerning the
operating range and how energy could be saved in V.A.V.
(variable air volume) system in air conditioning. By using
the above method the overall size of the fan could be
reduced. Hence, after reviewing the available literature,
Inner guide vanes are chosen for the study in the present
research work. Poor efficiency and lack of capacity control
range (which are often found with ageing centrifugal turbo

machines like centrifugal compressor,centrifugal pump, and
centrifugal fan) are observed when performance tested in
various applications. For this reason, improvement in the
stable operating range and reduction in part load power
consumptions, particularly in off-design conditions was
required. This was achieved byupgradingtheaerodynamics
and fitting Inner guide vane control to the machines in this
work.
[4]M.Lorussoa,T. Capursoa , M. Torresia , B. Fortunatoa,
F.Fornarellia,S.M.Camporealea,R.Monterisob-Thispaper
provides the reader with guidelines for the definition of
coarse but effective meshes on reduced computational
domains in order to accurately evaluate the drop curvesand
the NPSH3% of centrifugal pumps by means of CFD. The
procedure has been validated against experimental data,
carried out on single stages ofmulti-stagecentrifugal pumps,
and numerical data obtained by a mono-dimensional model.
Thanks to the proposed procedure,withoutanydetrimentto
the accuracy, a significant computational cost reduction has
been experienced with respect to simulations performed on
complete stages.
3. AIM & OBJECTIVE
 To determine the flow around the impeller.
 To determine the charachterstic of discharge v/s
head.
 To determine the pressure around the volute of the
casing.
 To determine the maximum pressure drop region.
 To achieve constant V×R Region.
4. MODELLING OF DIESEL ENGINE WATER
PUMP COMPONENTS
For carrying out 3D CFD simulation of diesel engine
water pump the modelling of its parts is required which is
done by using the Creo Parametric Version 2.0. Creo
Parametric developed by PTC in year 2012isoneofthemost
widely used modelling software in various design Firms.
Following are the components of diesel engine water pump
modelled by Creo Parametric 2.0 are :
4.1 Water Pump Assembly
The impeller is mounted on a shaft coupled to
driving unit which may be an electric motor or IC Engine.
The impeller used is of semi-open type having Radial vanes
.The impeller modelled consists of 7 radial vanes. The
impeller is used in water pump of diesel engine to increase
pressure of the fluid.
Fig. 4.1 Isometric view of assembly of pump
4.2 Water Core/ Domain
Fig. 4.2 Isometric view of Water core/Domain
The above figure shows the solid geometry of the water
core present in the volute casing of the centrifugal pump.
This water core domain is use for simulation purpose by
using the software STAR CCM+.
5. CFD SIMULATION OF CENTRIFUGAL PUMP
5.1 Process of CFD Analysis
CFD Simulation of centrifugal pump is carried in three
main stages:
1. Pre-processing
2. Solving
3. Post-processing

5.2 Pre Processing
Fig.5.2 Water core with Impeller
5.3 Working Parameters
Working Parameter Consists of Mesh Modelling,
Physics Modelling and defining Boundary Conditions :-
5.3.1 Mesh Modelling –
Polyhedral Mesh
Volume level Mesh
5.3.2 Physics Modelling -
a. K-Epsilon Turbulence.
b. Fluid Used – Mixture of water & ethylene glycol
with 50% conc. each.
5.3.3 Properties of fluid used -
a. Fluid mixture Specific heat – 3.558 KJ/ kg-K.
b. Fluid mixture Viscosity – 0.4152 Pascal-sec.
c. Fluid mixture Density -1051 kg/m3.
5.3.4 Boundary Conditions -
a. Impeller RPM -3000
b. Flowrate LPM at Inlet- 40-70
c. Pressure Outlet (Guage) - 0 Pa.
5.4 Solving
Solving of the flow equations requires less time as flow
equations are solved iteratively in grid cells. The solution
speed is increased by using multicore computer clustersfor
calculation purpose. The accurate solutions of the partial
differential equations are obtained by converging the
results.
5.5 Post-processing
Post-processing is the final step in CFD analysis. The various
graphs are plotted in this stages. It is used to visualize the
results which are obtained from the solver.
5.5.1 Velocity Distribution of Centrifugal
pump Impeller (3000 RPM)
Fig. 5.5.1 Front View of Velocity Distribution of
Centrifugal pump Impeller
Figureshows the overall velocity distribution of the impeller
when the speed of rotation was set at 3000 RPM. From the
observation of above figure the impeller has max. velocity of
22.361 m/s and min. velocity of 0.31691 m/s.
5.5.2 Velocity Distribution in Centrifugal
pump Casing
Fig. 5.5.2 Front View of Velocity Distribution in
Centrifugal pump Casing
Figure shows the overall velocity distribution in the pump
casing when the speed of rotation wassetat3000RPM.From
the observation of above figure the maximum velocity in
casing is 21.103 m/s and min. velocity is 0.0094459 m/s.
5.5.3 Pressure Distribution of Centrifugal pump
Impeller (3000 RPM)
Figure shows the Overall Pressure distribution of the
impeller when the speed of rotation was set at 3000 RPM.
From the observation of figure the impeller has a max.
pressure of 2.4638 bar and min. pressure of 0.051591 bar.

Fig. 5.5.3 Back side View of Pressure Distribution of
5.5.4 Pressure DistributioninCentrifugal
pump casing
Fig. 5.5.4 Front side View of Pressure Distribution of
Figure shows the Overall Pressure distribution in the
casing when the speed of rotation wassetat3000RPM.From
the observation of figure the impeller has a max. pressure of
2.2000 bar and min. pressure of 0.030584 bar.
5.5.5 Pressure Distribution Evaluation
Table indicate the value of head (bar) obtained by
varying flow rate (lpm) for the impeller. When the flow rate
was 40 lpm, head obtained was 0.7436 bar. And when flow
rate increases to 70 lpm the head decreases to 0.58 bar.
Therefore we conclude that as the flow rate increases the
head obtained decreases gradually.
Table 5.5.5 Pressure and the Flow rate properties
Flow rate (LPM) CFD Head (bar)
40 0.7436
50 0.7154
60 0.62
70 0.58
Head v/s Flow rate of Impeller
Fig. 5.5.5 Plot of head v/s flow rate
From the graph we conclude that as the flow rate
increases the head decreases gradually.
6. EXPERIMENTAL TESTING OF CENTRIFUGAL
PUMP
6.1 Experimental Setup
Experimental Setup of Centrifugal Pump consists of
Water Pump, Impeller, motor, water storage tank, belt,
Pressure sensor. Prime mover motor is connected to the
pump by using the belt drive to rotate the impeller. Water
storage tank is used to store the water and supply the inlet
water as well as collect water from the pump. Inlet and
outlet flow rate is measure by using the electro-magnetic
flow meter. Inlet and outlet pressure is measured by using
the pressure sensor.
6.2 Experimental Procedure
 Initially the sump tank was filledwithwater.Thewater
in the sump tank should be oil free.
 Motor is connected to pump by using the belt drive.
 All the outlets were closed and inspection was done to
find out if any leakages exist and if so corrections were
done to avoid leakages.
 Then the outlet of pump was opened to remove air
bubbles from connecting pipe.
 Water is then supplied to pump inlet from sump
storage by using connecting pipe which has a flow
measuring instrument and a pressure sensor.
 Now the Pump started running.

 The water flows through pump towards the cooling
arrangement of engine.
 After that outlet pressure is measured at the outlet of
engine by using pressure sensor at the discharge pipe.
 The water is again recollected into the sump tank and
this cycle continues.
Image-Experimental Setup
6.3 Experimental Observation
By keeping the RPM 3000 We have observe the value of
pressure head (bar) by changing the flow rate (LPM).
Flow rate
(LPM)
Experimental Head
(bar)
40 0.732
50 0.6912
60 0.63
70 0.5923
TABLE 2 Experimental Observations
Head v/s Flow rate of Impeller
From the graph we conclude that as the flow rate
increases the head decreases gradually.
7. RESULT AND DISCUSSION
The impeller geometry was constructed in the CREO
Parametric 2.0 and the flow simulationwascarriedoutusing
the STAR CCM+. To initialize andrunthesimulation,a hybrid
initialization was used to obtain the results. After the
analysis was carried out, the results were obtained from the
software once the simulation has converged. The simulation
iterations were set in 1000 times and all of the simulation
results were converged within the range. For the flow
simulation, various rotating speeds were selected to be the
variable factors in this project. The aim is to come out with
an impeller design whichhasa graduallyincreasingpressure
distribution in order to be chosen as the most efficient
impeller. This study focuses on the pressure distribution of
the centrifugal pump impeller by varying the rotation speed
at 3000 rpm. The results of the simulations were obtained
from the CFD software and compared with the experimental
results .The input and output pressures were calculated in
order to obtain the pressure head.
Graph- Head V/S Flow rate
The above plot shows variation of the head w.r.t to flow
rate for CFD and Experimental testing. From observation of
the curves in the above plot the curves are approximately
same with minimum error between CFD and Experimental
testing to obtain the desired head.
Graph - Error plot

Above plot indicates the error obtained during comparison
of the simulation results and the actual experimental testing
carried out for the centrifugal pump in diesel engine water
pump.
8. CONCLUSIONS
Experimental testing wascarriedoutatvarious flow rate
conditions and when the obtain results were compared with
the results obtained from simulation were approximately
same. This comparison validates the accuracy of CFD and
experimental approaches.
Thus we obtained that the higher head 0.74 bar at the
flow rate 40 Lpm. This can be selected for further analysisto
improve the performance of pump.
References
[1] R.Barrio,J. Fernandez b , E. Blancoa , J. Parrondoa
Estimation of radial load in centrifugal pumps using
computational fluid dynamics.
[2] Md. Abdul Raheem Junaidia , N.B.VLaksmi Kumari,Mohd
Abdul Samadc, G.M. Sayeed Ahmed CFD Simulation to
Enhance the Efficiency of Centrifugal PumpbyApplication
of Inner Guide Vanes.
[3] M. Lorussoa, T. Capursoa , M. Torresia , B. Fortunatoa , F.
Fornarellia , S.M.Camporealea,R.MonterisobEfficientCFD
evaluation of the NPSH for centrifugal pumps.
[4] Erik Dick, Jan Vierendeels, Sven Serbruyns And John
Vande Voorde Performance Prediction Of Centrifugal
Pumps With Cfd-tools.
BIOGRAPHIES
Mr. Rahul T. Dhanore
Asst. Professor
Department of Mechanical
Engineering
JSPM’S ICOER, Pune
Mr. Shubham L. Lilhare
Final Year Student
Bachelor of Engineering
Mr. Sandeep D. Jadhav
Final Year Student
Bachelor of
Engineering
Mr. Arvind P. Kaware
Final Year Student
Mr. Amit R. Karkhile
Final Year Student

IRJET- Modelling, Simulation and Testing of Diesel Engine Water Pump

More Related Content

What's hot (19)

Similar to IRJET- Modelling, Simulation and Testing of Diesel Engine Water Pump (20)

More from IRJET Journal (20)

Recently uploaded (20)

IRJET- Modelling, Simulation and Testing of Diesel Engine Water Pump