Design of Centrifugal Pump – Impeller

7/28/2019 Design of Centrifugal Pump Impeller

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DESIGNOF CENTRIFUGAL PUMP IMPELLER

Submitted by:

Supriya Naha Biswas (09259007044)

Sweta Sarkar (09259007049)

Sandip Agarwal (09259007038)

Under the Guidance of:

Prof. Abhijit Chakrabarty.Deb Dulal Ganguly.


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WORKING PRINCIPLE


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PUMP ELEMENTS

Stationary Elements

Casing

Stuffing box Bearings

Packing

Rotating Elements Impeller

Impeller shaft


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PUMP IMPELLER

Rotating Component.

Consists of a disc with blades mounted

perpendicularly on its surface.

Vanes may be of three different orientations,

Radial

Backward curved

Forward curved


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TYPESOF IMPELLER

Impellers can be classified in terms of so many

parameters, i.e. direction, stage, head, inlet angle,

speed, position of shaft etc.

In the axial flow impellers, the head is developed by

the propelling or lift action of the vanes on the liquid

which enters the impeller axially and discharges

axially.

In the radial flow impellers, the head is developed

by the action of centrifugal force upon the liquid

which enters the impeller axially at the centre and

flows radially to the periphery.


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BASIC PERSPECTIVESOF DESIGN

Practical design

Economical design

Development of existing technology

Consideration of manufacturing issues


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DESIGN DATAAND FORMULAE

Head = 60 ft.

Discharge = 2500 gal / min

Speed = 1500 rpm

Important formula

Water horsepower,

Break horsepower,


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DESIGN CONSIDERATIONS

Specific Speed,

Classification of specific speed


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Speed ratio = 1.15

Flow ratio = 0.170

Diameter ratio = 0.65

Width ratio = 0.25


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The selection of outlet vane angle (2) depends on the type of

head capacity characteristics desired. For optimum efficiency,

usually a value of about 25 is taken for all specific speeds.

The inlet vane angle is selected so that inlet absolute velocity

may be radial. The radius of curvature of vanes is selected

depending on the inlet and outlet blade angles, so that a

smooth, separation free flow is obtained in the impeller

passage.

The number of vanes in an impeller depends on the pump

size, the speed ratio, the vane load and the outlet blade angle.

With low values of outlet blade angle, usually six or eight

vanes are adopted.


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CALCULATEDVALUE

Impeller outlet diameter, D2 = 0.91 ft

Impeller inlet diameter, D1 = 0.59 ft

Impeller outlet width, B2 = 0.23ft

Impeller inlet width, B1= 0.35 ft

Impeller outlet blade angle = 22.71

Impeller inlet blade angle = 14.01


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CENTRIFUGAL PUMP PERFORMANCE CURVE


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INLET VELOCITY TRIANGLE


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OUTLET VELOCITY TRIANGLE


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IMPELLER DIMENSION


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CONCLUSION

Energyefficientdesign ofany machineis the

ultimatesuccess ofthis era.

We remainthankful to

our Guide,HOD andeveryonewho arehelping us inthis project.


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REFERENCES1. Ahuja, V., Hosangadi, A., Ungewitter, R. and Dash, S. M., A Hybrid Unstructured Mesh Solver for Multi-Fluid Mixtures, AIAA 99-3330,

14th Computational Fluid Dynamics Conference, Norfolk, VA, June, 1999.

2. Chen, Y., Heister, S.D. (1994) Two-Phase Modeling of Cavitated Flows,ASME FED-Vol. 190, pp.299-307.

3. Gridgen User Manual, Version 13.3, Pointwise, 1999.

4. Hirschi, R., Dupont, Ph., Avellan, F., Favre, J.-N., Guelich, J.-

F., Parkinson, E. (1998) Centrifugal Pump Performance Drop Due to Leading Edge Cavitation: Numerical Predictions Compared With Model

Tests,ASME Journal of Fluids Engineering, Vol. 120, No. 4, pp. 705-711,

5. Jorgenson, P.C.E., Chima, R.V. (1989) "Explicit Runge-Kutta Method for Unsteady Rotor-Stator Interaction," AIAA Journal, Vol. 27, No. 6, pp.

743-749.

6. Kunz, R.F., Boger, D.A., Stinebring, D.R., Chyczewski, T.S., Gibeling, H.J., Govindan, T.R. (1999) "Multi-phase CFD Analysis of Natural and

Ventilated Cavitation About Submerged Bodies,ASME Paper FEDSM99-7364.

7. Kunz, R.F., Boger, D.A., Stinebring, D.R., Chyczewski, T.S., Lindau, J.W., Gibeling, H.J., Venkateswaran, S., Govindan, T.R. (2000) APreconditioned Navier-Stokes Method for Two-Phase Flows with Application to Cavitation Predication,Computers and Fluids, Vol. 29, No.

8, pp. 849-875.

8. Kunz, R.F., Lindau, J.W., Billet, M.L., Stinebring, D.R. (2001) Multiphase CFD Modeling of Developed and Supercavitating Flows, VKI

Special Course on Supercavitating Flows, February.

9. Lindau, J.W., Kunz, R.F., Gibeling, H.J. (2000) Validation of High Reynolds Number, Unsteady Multi-Phase CFD Modeling for Naval

Applications, presented at the 23rd Symposium on Naval Hydrodynamics, Val de Reuil, France.

10. Merkle, C.L., Feng, J.Z. and Buelow, P.E.O. (1998) Computational Modeling of the Dynamics of Sheet Cavitation, 3rd

InternationalSymposium on Cavitation, Grenoble, France.

11. Meyer, R.S., Yocum, A.M. (1993) Pump Impeller Performance Evaluation Tests for a Parametric Variation of Geometric Variables, ARL

Technical Memorandum 93-125.

12. Nakamura, S., Ding, W., Yano, K. (1998) A 2.5D Single Passage CFD Model for Centrifugal Pumps,ASME Paper FEDSM98-4858.

13. Song, C., He, J. (1998) "Numerical Simulation of Cavitating Flows by Single-phase Flow Approach, 3rd International Symposium on

Cavitation, Grenoble, France.

14. Taylor, L.K., Arabshahi, A., Whitfield, D.L. (1995) Unsteady Three-Dimensional Incompressible Navier-Stokes Computations for a ProlateSpheroid Undergoing Time-Dependent Maneuvers,AIAA Paper 95-0313.


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Design of Centrifugal Pump – Impeller

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