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Technical Briefs

Influence of Blade Number on the Performance and Pressure Pulsations in a Pump Used as a Turbine

[+] Author and Article Information
Sun-Sheng Yang

e-mail: yangsunsheng@126.com

Fan-Yu Kong

Professor
e-mail: kongm@ujs.edu.cn

Xiao-Yun Qu

Graduate Student

Wan-Ming Jiang

Graduate Student
Research Center of Fluid Machinery Engineering and Technology,
Jiangsu University,
Zhenjiang, Jiangsu, 212013, PRC

1Corresponding author.

Contributed by the Fluids Engineering Division of ASME for publication in the Journal of Fluids Engineering. Manuscript received October 29, 2011; final manuscript received September 10, 2012; published online November 20, 2012. Assoc. Editor: Bart van Esch.

J. Fluids Eng 134(12), 124503 (Nov 20, 2012) (10 pages) doi:10.1115/1.4007810 History: Received October 29, 2011; Revised September 10, 2012

The rotor-stator interaction of a rotating impeller and a stationary volute could cause strong pressure pulsations and generate flow induced noise and vibration in a pump used as a turbine (PAT). Blade number is one of the main geometric parameters of the impeller. In this paper, a numerical investigation of the PAT’s unsteady pressure field with different blade numbers was performed. The accuracy of global performance prediction by computational fluid dynamics (CFD) was first verified through comparison between numerical and experimental results. Unsteady pressure fields of the PAT with different blade numbers were simulated, and the pulsations were extracted at various locations covering the PAT’s three main hydraulic parts. A detailed analysis of the unsteady pressure field distributions within the PAT’s control volume and comparison of unsteady pressure difference caused by the increase of blade number were performed. The transient flow results provided the unsteady pressure distribution within PAT and showed that increasing the blade number could effectively reduce the amplitude of pressure pulsations. Finally, unsteady pressure field tests were performed and some unsteady results obtained by unsteady field analysis were validated.

Copyright © 2012 by ASME
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References

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Figures

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Fig. 2

(a) Mesh assembly, (b) mesh of a cut plane, (c) mesh in wear ring

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Fig. 3

Locations of pressure monitoring points

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Fig. 4

Pressure pulsation at the volute tongue at design operating condition

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Fig. 5

Comparison between the PAT’s experimental and numerical results

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Fig. 6

Performance curves of the PAT with different blade numbers

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Fig. 7

Unsteady pressure distributions in the volute for the six-bladed impeller

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Fig. 8

Unsteady pressure distributions within volute for impeller with different blade numbers

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Fig. 9

Frequency domain of unsteady pressure distributions within volute for impeller with different blade numbers

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Fig. 10

Unsteady pressure distributions in the impeller for the six-bladed impeller

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Fig. 11

Time domain of unsteady pressure distributions within the impellers for different blade numbers

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Fig. 12

Frequency domain of unsteady pressure distributions within the impeller for different blade numbers

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Fig. 17

Unsteady pressure field distribution at the PAT’s volute monitoring points

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Fig. 13

Unsteady pressure distribution in the outlet pipe for the six-bladed impeller

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Fig. 14

Time domain of unsteady pressure distributions within the outlet pipe for different blade numbers

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Fig. 15

Frequency domain of unsteady pressure distributions within the outlet pipe for different blade numbers

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Fig. 16

The PAT’s unsteady pressure field test

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Fig. 1

An open PAT test rig established at Jiangsu University

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Fig. 18

(a) Complete domain, (b) no leakage, (c) no chamber

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Fig. 19

(a) Q-η curve, (b) Q-H curve, (c) Q-P shaft curve

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Fig. 20

(a) Q-η curve, (b) Q-H curve, (c) Q-P shaft curve

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