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Flows in Complex Systems

Numerical Prediction of Unsteady Pressure Field Within the Whole Flow Passage of a Radial Single-Blade Pump

[+] Author and Article Information
Ji Pei1

Research Center of Fluid Machinery Engineering and Technology, Jiangsu University, Zhenjiang 212013, Chinacraig.j.pei@gmail.com

Shouqi Yuan

Research Center of Fluid Machinery Engineering and Technology, Jiangsu University, Zhenjiang 212013, Chinashouqiy@ujs.edu.cn

Friedrich-Karl Benra

Department of Mechanical Engineering, Faculty of Engineering, University of Duisburg-Essen, 47048 Duisburg, Germanyfriedrich.benra@uni-due.de

Hans Josef Dohmen

Department of Mechanical Engineering, Faculty of Engineering, University of Duisburg-Essen, 47048 Duisburg, Germanyhans-josef.dohmen@uni-due.de

1

Corresponding author.

J. Fluids Eng. 134(10), 101103 (Sep 28, 2012) (11 pages) doi:10.1115/1.4007382 History: Received June 24, 2012; Revised August 12, 2012; Published September 24, 2012; Online September 28, 2012

In this paper, the periodically unsteady pressure field caused by rotor-stator interaction has been investigated numerically by computational fluid dynamics (CFD) calculation to evaluate the transient pressure variation in a single-blade pump for multiconditions. Side chamber flow effect is also considered for the simulation to accurately predict the flow in a whole-flow passage. The strength of the pressure fluctuation is analyzed quantitatively by defining the standard deviation of the pressure fluctuation of a revolution period. The analysis of the results shows that higher pressure fluctuation magnitudes can be observed near the blade pressure side and high gradients of fluctuation magnitudes can be obtained at the trailing edge near the pressure side of the blade. An asymmetrical distribution of fluctuation magnitudes in the volute domain can be clearly obtained. On the cylindrical surface around the impeller outlet, although the absolute pressure value is higher for the Q = 11 l/s condition, the magnitude distribution of fluctuations is lower, and a relatively symmetrical fluctuation distribution is obtained for the Q = 22 l/s condition when clearly asymmetrical distributions of fluctuation magnitude can be observed for the design point and for large flow rates. Obvious periodicity can be observed for the pressure fluctuation magnitude distribution on the circumference with different radii in the volute domain, and some subpeaks and subvalleys can be found. The effects of unsteady flow in the side chambers on the entire passage flow cannot be neglected for accurately predicting the inner flow of the pump. The results of unsteady pressure fluctuation magnitude can be used to guide the optimum design of the single-blade pump to decrease the hydrodynamic unbalance and to obtain more stable performance of the pump.

Copyright © 2012 by American Society of Mechanical Engineers
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References

Figures

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Figure 1

Overview of the model pump rotor and the test stand

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Figure 2

Grid details in the rotating domain

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Figure 3

Grid view in a meridional plane

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Figure 4

Coordinate system and angle definitions

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Figure 5

Head curves of the test pump

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Figure 6

Comparisons of CFD calculated and measured transient pressure results: (a) Q = 42 l/s; (b) Q = 33 l/s; (c) Q = 22 l/s; (d) Q = 11 l/s

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Figure 7

Pressure distributions on the circumference around the impeller outlet for multi-impeller rotating positions and multiconditions at midspan, r = 0.1275 mm: (a) numerical results for φ = 0 deg; (b) numerical results for φ = 90 deg; (c) numerical results for φ = 180 deg; (d) numerical results for φ = 270 deg

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Figure 8

Pressure distributions on the cylindrical surface around the impeller outlet for multi-impeller rotating positions, Q = 33 l/s, r = 0.1275 mm: (a) numerical results for φ = 0 deg; (b) numerical results for φ = 90 deg; (c) numerical results for φ = 180 deg; (d) numerical results for φ = 270 deg

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Figure 9

Pressure distributions on the cylindrical surface around the impeller outlet for multiconditions, φ = 0 deg, r = 0.1275 mm: (a) numerical results for Q = 42 l/s; (b) numerical results for Q = 33 l/s; (c) numerical results for Q = 22 l/s; (d) numerical results for Q = 11 l/s

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Figure 10

Calculated magnitude distributions of pressure fluctuations in the rotor domain, Q = 33 l/s at midspan

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Figure 11

Calculated magnitude distributions of pressure fluctuations in the stator domain, Q = 33 l/s at midspan

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Figure 12

Magnitude distributions of pressure fluctuations on the cylindrical surface around the impeller outlet for multiconditions: (a) numerical results for Q = 42 l/s; (b) numerical results for Q = 33 l/s; (c) numerical results for Q = 22 l/s; (d) numerical results for Q = 11 l/s

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Figure 13

Calculated magnitude distributions of pressure fluctuations on the circumference with different radii in the stator domain at midspan, Q = 42 l/s

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Figure 14

Calculated magnitude distributions of pressure fluctuations on the circumference with different radii in the stator domain at midspan, Q = 33 l/s

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Figure 15

Calculated magnitude distributions of pressure fluctuations on the circumference with different radii in the stator domain at midspan, Q = 22 l/s

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Figure 16

Calculated magnitude distributions of pressure fluctuations on the circumference with different radii in the stator domain at midspan, Q = 11 l/s

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Figure 17

Calculated magnitude distributions of pressure fluctuations on the cross sections of the side chambers, Q = 33 l/s: (a) a cross section of the back side chamber; (b) a cross section of the front side chamber

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