CFD Simulation of Industrial Centrifugal Pump

By

Bilal Waseem

ME-04

Report submitted to the faculty of PIEAS in partial fulfillment of

requirements for the degree of MS Mechanical Engineering

Department of Mechanical Engineering

Pakistan Institute of Engineering and Applied Sciences,

Nilore, Islamabad, Pakistan

March, 2014

i

Abstract

Centrifugal pumps are very important component of any industrial setup. These pumps

must be operated carefully because issues such as cavitation have the potential to put

these turbo machines out of order. The work conducted in this research comprises of the

use of CFD tools to analyze the flow characteristics inside a centrifugal pump. ANSYS

CFX has been used to carry out the CFD simulations of the pump impeller under

different flow rates and pressure and velocity profiles have been determined inside the

impeller. These profiles will provide information about phenomena such as flow

separation and flow recirculation. Using the pressure profile, the head to flow rate

characteristic curve will be developed and compared with the data provided by the actual

impeller that has been modeled. Afterwards, the blade length will be shortened and its

effects on the characteristic curves will be studied. The results obtained from this

research are then planned to be carried on to a separate research work in the future, where

cavitation phenomena will be studied in detail and it will be investigated how the

shortening of blades affects the pump performance with reference to cavitation.

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Table of Contents

1 Introduction ................................................................................................................. 1

1.1 Components of Centrifugal Pump ........................................................................ 1

1.1.1 Inlet (suction eye) ......................................................................................... 2

1.1.2 Impeller ......................................................................................................... 2

1.1.3 Volute ............................................................................................................ 2

1.1.4 Discharge ...................................................................................................... 2

2 Literature Review........................................................................................................ 3

3 Problem Statement ...................................................................................................... 5

4 Modeling of Impeller Geometry ................................................................................. 7

4.1 Solid Model of Impeller ....................................................................................... 7

4.2 Fluid Model ........................................................................................................ 12

5 Meshing..................................................................................................................... 14

5.1 Element Size ....................................................................................................... 14

5.2 Inflation Layers .................................................................................................. 14

5.3 Named Selections ............................................................................................... 17

6 CFD Simulation Setup .............................................................................................. 19

6.1 Operating Conditions ......................................................................................... 19

6.2 Analysis Type ..................................................................................................... 19

6.3 Basic Simulation Settings .................................................................................. 19

6.4 Fluid Model ........................................................................................................ 20

6.4.1 Heat transfer ................................................................................................ 20

6.4.2 Turbulence Model ....................................................................................... 20

6.5 Initialization ....................................................................................................... 21

6.6 Boundary Conditions.......................................................................................... 21

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6.6.1 Inlet ............................................................................................................. 21

6.6.2 Outlet........................................................................................................... 21

6.6.3 Wall ............................................................................................................. 21

7 Results ....................................................................................................................... 23

7.1 Mesh Independence Study ................................................................................. 23

7.2 Pressure Contours ............................................................................................... 24

7.3 Velocity Results ................................................................................................. 26

8 References ................................................................................................................. 27

9 Vita ............................................................................................................................ 28

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LIST OF FIGURES Figure 1: Components of centrifugal pump ........................................................................ 1

Figure 2: Views of actual impeller ...................................................................................... 6

Figure 3: Sketch for hub geometry ..................................................................................... 8

Figure 4: Developing the blade geometry ........................................................................... 9

Figure 5: 3D blade profile ................................................................................................. 10

Figure 6: Blade profile of all 6 blades .............................................................................. 10

Figure 7: Isometric view of impeller ................................................................................ 11

Figure 8: Side view of impeller ........................................................................................ 11

Figure 9: Top view of Impeller ......................................................................................... 12

Figure 10: Isometric view of fluid domain ....................................................................... 13

Figure 11: Side view of fluid domain ............................................................................... 13

Figure 12: Mesh with 9 mm element size ......................................................................... 16

Figure 13: Mesh view from a slice plane .......................................................................... 16

Figure 14: Close up of inflation layers around blades ...................................................... 16

Figure 15: Inlet and outlet faces........................................................................................ 17

Figure 16: Hub face .......................................................................................................... 17

Figure 17: Blade and shroud faces .................................................................................... 18

Figure 18: Inlet and outlet boundaries .............................................................................. 22

Figure 19: Pressure contours - top and bottom view ........................................................ 25

Figure 20: Velocity streamlines ........................................................................................ 26

Figure 21: Velocity vectors ............................................................................................... 26

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LIST OF TABLES Table 1: Dimensions of impeller ......................................................................................... 5

Table 2: Operating conditions ........................................................................................... 19

Table 3: Basic settings ...................................................................................................... 20

Table 4: Mesh independence ............................................................................................ 24

1

1 Introduction

A centrifugal pump is a work consuming type of turbo machinery. It converts rotational

kinetic energy to hydrodynamic energy of fluid flow. An engine or electric motor

provides rotational energy. The fluid enters the inlet of a rotating impeller along its axis

of rotation, gets accelerated and then enters a volute where its kinetic energy is converted

into higher pressure as the fluid passes through the increasing area of volute.

1.1 Components of Centrifugal Pump

A centrifugal pump consists of the following major components as shown in figure 1:

1. Inlet (suction eye)

2. Impeller

3. Volute

4. Discharge

Figure 1: Components of centrifugal pump

2

1.1.1 Inlet (suction eye)

This is the component that takes fluid to the impeller. It is a stationary part which is of

cylindrical shape.

1.1.2 Impeller

The impeller is the main rotating component of centrifugal pump. Fluid enters through its

eye, gets caught up in its blades and is whirled tangentially and radially outward. It can

be classified in multiple ways:

1. Based on flow direction

a. Radial flow

b. Axial flow

c. Mixed flow

2. Based on suction type

a. Single-suction: Liquid inlet on one side.

b. Double-suction: Liquid inlet to the impeller symmetrically from both sides

3. Based on mechanical construction

a. Closed: Shrouds or sidewall enclosing the vanes.

b. Open: No shrouds or wall to enclose the vanes.

c. Semi-open or vortex type

1.1.3 Volute

This is the stationary component. It receives the fluid being pumped by the impeller. It

reduces the velocity of fluid because its area keeps increasing from the point where fluid

enters it to the point where it leaves. This reduced velocity results in conversion of kinetic

energy into potential energy thus increasing the pressure of the fluid.

1.1.4 Discharge

This component is basically the ending part of the volute. From here onward, the fluid is

not further pressurized. It connects the pump to the piping system.

3

2 Literature Review

S. Rajendran and Dr. K. Purushothaman analyzed centrifugal pump impeller using

Ansys CFX. The impeller was six blade closed type impeller, rotating at 925 rpm with a

flow rate of 12.5 litres per second. Unstructured tetrahedral mesh was used for

simulation, using k-epsilon turbulence model with 5% turbulence intensity. CFD

simulation predicted the discharge head of 9.4528 m at design point (1).

Neelambika and Veerbhadrappa used CFD to analyze the effect of varying the inlet

and outlet blade angles on the efficiency of a mixed flow pump impeller. They concluded

that by increasing the blade exit angle and decreasing the inlet angle, efficiency increased

by about 18%. Variation in exit angle improved the efficiency more significantly that the

variation in inlet angle (2).

Kiran Patel and N. Ramakrishnan investigated the flow in a mixed flow pump. The

original geometry was simulated using steady state conditions. Performance curves

obtained from the simulation matched the original curves with only 5 to 10 % difference.

The recirculation at design point was reduced by matching stator blade angle with respect

to flow angle and changing hub curve profile. This improved the efficiency by 1% (3).

S. C. Chaudhari, C. O. Yadav and A. B. Damor studied the effect of change in inlet

and outlet blade angle and number of blades on the discharge head of the mixed flow

pump impeller. CFD simulation was carried out using k-epsilon turbulence model with

5% intensity. Several different blade angles and different blade numbers were simulated

and the best geometry showed an improvement of 10.29 m in discharge head (4).

Liu Houlin, Wang Yong, Yuan Shouqi, Tan Minggao, and Wang Kai studied the

effect of blade number on characteristics of centrifugal pumps. Impellers with 4, 5, 6 and

7 blades were simulated and it was found that discharge head increased with increasing

number of blades. The low pressure region at the inlet of impeller increased with the

number of blades (5).

K.M. Pandey, A.P. Singh and Sujoy Chakraborty investigated the effect of blade

number on performance of centrifugal pump at 2500 rpm. It was found that discharge

head increased while efficiency decreased with increase in blade number (6).

4

Miguel Asuaje, Farid Bakir, Smaine Kouidri, Frank Kenyery and Robert Rey

carried out numerical simulation of centrifugal pump. Three different turbulence models

were compared, namely k-epsilon, k-omega and sst models. It was found that discharge

head was almost same with a difference of less than 0.02%. Further simulations were

done under quasi-unsteady case with k-epsilon model. Frozen rotor interface was used

between inlet-impeller domains and impeller- volute domains (7).

Lamloumi Hedi, Kanfoudi Hatem and Zgolli Ridha studied the three dimensional

flow in centrifugal pump using k-epsilon turbulence model with structured grid. Frozen

rotor interface was used to model the inlet-impeller interface and impeller-volute

interface (8).

Suthep Kaewnai, Manuspong Chamaoot and Somchai Wongwises used CFD

simulation to compare the effect of different turbulence models (k-epsilon, k-omega and

RNG k-epsilon) and turbulence intensities (1%, 5% and 10%) using structured grid.

Different turbulence models gave very similar values of discharge head and variation of

turbulence intensity also did not have any significant effect on the result. The increase in

surface roughness increased the pressure loss (9).

H. L. Liu, M. M. Liu, L. Dong, Y. Renand H. Du studied the effect of turbulence

models and computational grids on numerical simulation of centrifugal pump. K-epsilon

EARSM model was found to give the best results (10).

5

3 Problem Statement

This thesis is based on an industrial centrifugal pump of mixed flow type. The pump

under consideration has been facing cavitation issues at the suction of impeller and also at

the surface of blades near the trailing edge. The objectives of this thesis are:

1. Modeling CAD geometry of impeller from the actual impeller in use.

2. Using CFD simulation to visualize the flow inside the impeller. These simulations

will show the variation of pressure and velocity under different flow rate

conditions.

3. The results of CFD simulation will be compared with the data provided by the

vendors of the actual pump.

4. Characteristic curves will be developed and compared with those provided by

vendor.

5. The blade length will be reduced and its effect on the performance of pump will

be studied.

The pump under consideration has a best efficiency point at 508 litres per second with

efficiency of 88%. At this flow rate, the discharge head produced by the pump is about 51

m.

Physical dimensions shown in table 1 were taken from the actual impeller but blade

angles could only be measured approximately because the impeller was of closed type.

Table 1: Dimensions of impeller

Entity Value

Inlet diameter 29.7 cm

Outlet diameter 48.1 cm

Inlet blade width 16 cm

Outlet blade width 9 cm

Exit blade angle 25 degrees (approx.)

Shaft diameter 7.8 cm

6

The purpose of this research is to study the flow in the impeller with the existing

conditions and then to investigate the effects of shortening the length of blades.

Figures show the different views of the actual impeller.

Figure 2: Views of actual impeller

7

4 Modeling of Impeller Geometry

The first step in CFD simulation is to develop a model that can be used for simulation by

applying appropriate boundary conditions. In this thesis, the impeller is of closed type

and so without the availability of advanced technology, it is a tough task to replicate the

impeller to its exact specifications. Dimensions were taken manually. External

dimensions were easily and accurately taken, but as the impeller is of closed type, it was

impossible to measure the blade dimensions accurately. A small portion of blades is

visible only from the inlet and so the leading edge was dimensioned with good accuracy.

Similarly the trailing edge was also measured quite accurately. But the profile of blade

that was not visible could not be measured and that had to be modeled with relatively

poor accuracy.

4.1 Solid Model of Impeller

ANSYS Workbench was used to develop the geometry. The first step in modeling was to

sketch the geometry in XY plane and XZ plane. The length unit used in modeling is

centimeter. Figure 2 shows the sketch for hub geometry.

8

Figure 3: Sketch for hub geometry

Figure 3 shows the sketching procedure employed for the development of blades. The

yellow curve is lower edge of blade. This is the edge that is attached to the hub. The

black dots are 3D points from where the upper edge of the blade will be passed. This

edge will be attached to the shroud.

9

Figure 4: Developing the blade geometry

From the 3D curve and 3D points shown in figure 3, the complete blade profile was

generated and it is shown in figure 4.

10

Figure 5: 3D blade profile

As this is a six blade impeller, each blade covers an angle of 150o. Finally the impeller

geometry was replicated six times to finally obtain the complete blade geometry as

shown in figure 5.

Figure 6: Blade profile of all 6 blades

11

After the development of hub and blade profile, shroud was developed and the figure 6, 7

and 8 show the final geometry of impeller.

Figure 7: Isometric view of impeller

Figure 8: Side view of impeller

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Figure 9: Top view of Impeller

4.2 Fluid Model

As this thesis is about the CFD simulation, a solid impeller is of use only to extract the

fluid volume i.e. the volume occupied by fluid as it passes through the impeller. In

ANSYS Workbench, there is an option named Boolean which was used to extract the

fluid region from the solid geometry. We are not concerned with structural analysis of

impeller and there is not heat transfer between impeller and fluid. So there is no need to

include the solid part in the analysis, because it will only increase the computational

effort required to simulate our case.

Figures 9 and 10 show the different views of the fluid domain. It is visible from these

figures that only the region that is occupied by fluid is included in this geometry. The

space occupied by the blades is looking empty now.

13

Figure 10: Isometric view of fluid domain

Figure 11: Side view of fluid domain

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5 Meshing

A fine mesh is important for CFD simulation. Mesh should be fine enough to be able to

capture all the details in critical areas. As the mesh grows finer, the number of cells

where computation is to be done, increases. Thus the computational effort increases and

simulation takes longer time to find a converged solution.

In complex geometries such as the impeller under consideration, it is a general practice to

use tetrahedral elements. The most critical area in the impeller is the area occupied by

blades and so it is necessary to refine the mesh in these regions. In this work,

unstructured grid has been used to generate a free mesh and then inflation layers have

been added on the blade surfaces.

5.1 Element Size

Increasing the element size makes the mesh coarse and reduces the number of elements

and vice versa. In this work, a number of different element sizes have been used to

generate meshes of varying fineness. Each mesh has been used to find the solution and

then mesh independence study has been conducted to find a mesh that will be suitable for

all the flow conditions.

5.2 Inflation Layers

It is necessary to have a sufficiently fine mesh to adequately capture regions where the

flow will experience rapid change in key variables such as pressure, velocity or

temperature. In case of flow over the blades, boundary layer flow takes place and in this

region, important changes occur which must be captured to have a good solution. If the

mesh is not fine enough in the boundary layer region, results of simulation cannot be

trusted. Thus inflation layers have been added in the region surrounding the blade

surfaces.

The question is what should the thickness of inflation layer be and what should be the

height of first cell next to the surface. In boundary layer flows, this is where the concept

of y+ becomes important. It is a non-dimensional wall distance for a wall-bounded flow.

The y+ value is a non-dimensional distance (based on local cell fluid velocity) from the

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wall to the first mesh node. To use a wall function approach for a particular turbulence

model with confidence, we need to ensure that our y+ values are within a certain range.

For good approximation of wall effects, it is advisable to use y+ of less than 2 (11). In

this thesis, desired value of y+ has been set to 2 and then from this dimensionless

number, the actual distance of the first node away from the wall has been estimated. The

procedure employed is as follows:

1. Compute the Reynold number Re:

=. .

For the design point of 417 litres per second, using inlet velocity of fluid as the

and diameter of inlet as , Reynold number comes out to be

2.1e+06. This means that the flow is fully turbulent.

2. Estimate the skin friction using Schlichting skin-friction correlation:

= [2 log 0.65].

3. Compute the wall shear stress:

= .1

2.

4. Compute the friction velocity:

=

5. Compute the wall distance

= .

.

Setting y+ equal to 2 yields y = 6.1e-03 mm (12).

Inflation layers were then added by using the value of y to be the height of first cell from

the wall. 10 inflation layers were added with a growth rate of 1.2 to ensure that the

boundary layer stays within the inflation layers. This is the refinement that leads to better

results near the wall.

Figure 11 shows the mesh generated by using a 9 mm element size and inflation layers

according to the above calculations.

16

Figure 12: Mesh with 9 mm element size

Figure 12 and 13 shows a close up of the inflation layers.

Figure 13: Mesh view from a slice plane

Figure 14: Close up of inflation layers around blades

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5.3 Named Selections

Named selections have been used to indicate the inlet, outlet, blades, hub and shroud.

These regions will then automatically be detected by CFX software as regions where

boundary conditions are to be applied. Figures 14, 15 and 16 show the named selections.

Figure 15: Inlet and outlet faces

Figure 16: Hub face

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Figure 17: Blade and shroud faces

19

6 CFD Simulation Setup

The next step in this thesis is to set up the conditions for the flow. These conditions

involve the initial and boundary conditions as well as the turbulence model suitable for

this case. This is a very crucial step in the field of computational fluid dynamics because

a wrong setup will give unrealistic results and the required information will not be

obtained or it will be misleading. ANSYS CFX has been used to simulate the flow.

6.1 Operating Conditions

The operating conditions that will be used in this thesis work are shown in table 2:

Table 2: Operating conditions

Entity Value

Rpm of impeller 1480 rpm

Inlet pressure head 10 m

Flow rate 417 litres per second (lps)

Inlet temperature of water 20oC

It is to be mentioned here that uptill now, only a flow rate of 417 lps has been used for

simulations. The future work will consist of simulation done on flow rates ranging from

zero to 660 lps.

6.2 Analysis Type

The flow inside a centrifugal pump is quite complex and while steady state simulations

can give good results, the real physics is only involved when a transient simulation is

carried out. In this simulation work, a transient type of analysis has been done with a total

time of 100 seconds and 5 time steps.

6.3 Basic Simulation Settings

In the analysis done so far, only the impeller domain has been used. This is a rotating

domain with a rotational speed of 1480 rpm. Table 3 shows the basic settings.

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Table 3: Basic settings

Entity Characteristic or Value

Domain type Fluid

Fluid Water

Morphology Continuous fluid

Reference pressure 0 kPa

Domain motion Rotating

Angular velocity 1480 rpm

6.4 Fluid Model

6.4.1 Heat transfer

For this research, it has been assumed that no heat transfer takes place between the solid

impeller and the fluid flowing inside it.

6.4.2 Turbulence Model

A lot of research has been done to find the best turbulence model for turbo machineries

like the centrifugal pump being studied. The three main candidates are:

1. K-epsilon model

2. K-omega model

3. Shear stress transport (SST) model

According to the research conducted by [7] and [9], these three models yield very similar

values of discharge head.

K-epsilon model provides good convergence and its memory requirements are low and it

gives good results in regions that are far from walls but its accuracy is compromised near

the walls.

K-omega model does not converge as easily as k-epsilon model but it gives good results

in case of internal flows and is better at predicting the flow separation near the walls.

However its accuracy is compromised away from the walls.

SST model combines the k-epsilon model in free stream and k-omega model near the

walls. In this way, its accuracy is better than the other two models throughout the domain.

21

As this research is being conducted primarily to predict the regions where the flow

separates from the blades and accurate results are also required in the free stream, so the

turbulence model chosen for this research is the SST model.

6.5 Initialization

To reduce the computational efforts and to obtain convergence as quickly as possible, it

is essential to initialize the solution properly. If the initial conditions are poor, the solver

takes a long time in finding a converged solution. In this step, an initial guess value is

given for the velocity of flow. The better the guess, the lesser are the computational

efforts. When the simulation work was started, initialization was left to the solver itself

using automatic option. This resulted in severe problems at the inlet and many a time, the

solver returned an error and did not solve the case. Finally the inlet velocity was

initialized using the velocity at inlet and this solved the problem.

6.6 Boundary Conditions

6.6.1 Inlet

The inlet boundary condition has been set using a total pressure inlet condition. The total

pressure of 199 kPa has been applied. This is the absolute pressure at the inlet as

reference pressure has been chosen to be 0 kPa. This condition has been applied on the

inlet face and a turbulence intensity of 5% has been chosen.

6.6.2 Outlet

Mass flow rate has been applied as the outlet boundary condition. For the simulation that

has been done thus far, a mass flow rate of 415 kg/s has been used.

6.6.3 Wall

All the six blades, the hub and shroud have been included as wall boundary condition.

The walls have been modeled as smooth walls with no slip condition.

Figure 14 shows the regions where inlet and outlet boundary conditions have been set.

22

Figure 18: Inlet and outlet boundaries

23

7 Results

The simulation setup that was set up in the previous chapter, was solved using CFX

solver. The importance of correct setup cannot be denied but it is equally important to

present the results of an analysis. One must have a clear idea of what the purpose of

simulation is and what physics is aimed to be studied. At the end of the day, it is the

results that are presented and these results give the information needed from the analysis.

As already mentioned, the purpose of these simulations is to obtain the characteristic

curves of the concerned impeller. Uptill now, the pressure curve is under development.

For this curve, it is required to run the simulations at various flow rates and determine the

pressure at the putlet face of impeller. This means that the primary output parameter in

the analysis is the outlet pressure. Pressure is presented in the form of contours in CFX.

These contours show regions of different pressure ranges. From these contour, one can

get the idea about where the pressure gradients are high or low, and where the pressures

are critically low or high.

At the same time, the velocity of water is also needed. From the velocity results, CFX can

produce the streamlines to show the path along which the fluid moves inside the fluid

domain. This fluid path is of importance as it gives an idea of the various phenomena

occuring inside the impeller e.g flow separation along blade surfaces, flow recirculation

etc. These phenomena must be predicted because the ultimate goal of this research work

is to find possible measures to reduce the issue of cavitation and these phenomena have a

close relation to cavitation.

The results presented in this report are only for a flow rate of 417 lps. The pressure at the

inlet of the impeller has been taken as 199 kPa (absolute).

7.1 Mesh Independence Study

As already mentioned in the chapter about meshing, a mesh used for simulation must be

capable enough to capture all the necessary details in critical regions and at the same time

time, it should ensure computational economics as well. When the mesh is too coarse, it

will give erroneous results, but as the mesh grows finer, important information that was

not being captured by the coarse mesh, starts getting included and the results move

toward accuracy. But there comes a level beyond which the fineness of mesh does not

24

affect the results. If the mesh is grown finer beyond this point, it will only increase the

computational time but the results will not be affected.

For this study, pressure at the outlet of impeller was set as the parameter of interest and

different mesh sizes were simulated under identical boundary conditions and turbulence

model.

Table 4: Mesh independence

Serial no. Element size (mm) No. of elements Pressure (bar)

1 15 110516 6.73428

2 10.2 204715 6.80756

3 9.8 225176 6.77522

4 9 251497 6.77470

From this analysis, it was found that the mesh size does not affect the results by much.

This is because inflation layers have already been added in the critical area around the

blade surface. The mesh in the remaining domain does not affect the result significantly.

7.2 Pressure Contours

Pressure contours have been shown in the following figures. It is evident that the pressure

is rising from the point the fluid enters the impeller to the point where it leaves. A low

pressure region is generated near the inlet. Here the pressure is lower than the inlet

pressure. The maximum pressure at the outlet is about 8 bar but the area averaged

pressure at outlet comes out to be 6.73428 bar. From this pressure, the inlet pressure is to

be subtracted which gives a differential pressure of 5.7 bar. The actual value provided by

the vendor is 5.5 bar which means that the results are quite satisfactory. Figure 19 shows

the contours of pressure as viewed from top and bottom of impeller.

25

Figure 19: Pressure contours - top and bottom view

26

7.3 Velocity Results

The velocity streamlines shown in figure 20 depict the way the fluid flows inside the

impeller and they also show the manner in which the velocity is changing.

Figure 20: Velocity streamlines

Figure 21 shows the vectors of velocity in the fluid domain.

Figure 21: Velocity vectors

27

8 References

1. Analysis of Centrifugal Pump Impeller Using Ansys-CFX. Purushothaman, S.

Rajendran and Dr. K. Purushothaman. ISSN:2278-0181.

2. CFD Analysis of Mixed Flow Impeller. Neelambika, Veerbhadrappa. ISSN: 2321-

7308.

3. CFD Analysis of Mixed Flow Pump. Kiran Patel, N. Ramakrishnan.

4. A comparative study of mix flow pump impeller CFD analysis and experimental data

of submersible. S. C. Chaudhari, C. O. Yadav and A. B. Damor. ISSN 2321-8843.

5. Effect of blade number on characteristics of centrifugal pumps. Liu Houlin, Wang

Yong, Yuan Shouqi, Tan Minggao, and Wang Kai. s.l. : Chinese Journal of

Mechanical Engineering, 2010, Vol. 23.

6. Numerical studies on effects of blade number variation on performance of centrifugal

pumps at 2500 rpm. K.M. Pandey, A.P. Singh and Sujoy Chakraborty. s.l. : Journal of

Environmental Research And Development, 2012, Vols. 6, No. 3A.

7. Numerical modelization of the flow in centrifugal pump: Volute influence in velocity

and pressure fields. Miguel Asuaje, Farid Bakir, Smaine Kouidri, Frank Kenyery

and Robert Rey. s.l. : International Journal of Rotating Machinery, 2005.

8. Simulation study and Three-Dimensional Numerical Flow in a Centrifugal Pump.

Lamloumi Hedi, Kanfoudi Hatem and Zgolli Ridha. s.l. : International Journal of

Thermal Technologies, 2012, Vols. 2, No.4. ISSN 2277 - 4114.

9. Predicting performance of radial flow type impeller of centrifugal pump using CFD.

Suthep Kaewnai, Manuspong Chamaoot and Somchai Wongwises. s.l. : Journal of

Mechanical Science and Technology, 2008.

10. Effects of computational grids and turbulence models on numerical simulation of

centrifugal pump with CFD. H. L. Liu, M. M. Liu, L. Dong, Y. Renand H. Du. s.l. :

IAHR Symposium on Hydraulic Machinery and Systems, 2012.

28

9 Vita

The author of this report was born on May 07, 1990 in the city of Sahiwal, Pakistan.

He received his early education, Matriculation (2006) and Intermediate - Pre Engineering

Group (2008) from Divisional Public School and Inter College, Sahiwal. In 2008, he

went to National University of Sciences and Technology (NUST), Islamabad for

professional education in the field of Mechanical Engineering. After graduating from

NUST in 2012, he joined Pakistan Atomic Energy Commission (PAEC) as a

postgraduate fellow and is currently completing his course work in the field of

Mechanical Engineering at Pakistan Institute of Engineering and Applied Sciences

(PIEAS).