Hydrodynamic Design of Rotodynamic Pump Impeller for Multiphase Pumping by Combined Approach of Inverse Design and CFD Analysis

[+] Author and Article Information
Shuliang Cao

Department of Thermal Engineering,  Tsinghua University, Beijing 100084, P. R. China caoshl@mail.tsinghua.edu.cn

Guoyi Peng1

Department of Mechanical Systems Engineering,  Toyama Prefectural University, 5180 Kurokawa, Kosugi-machi, Toyama 939-0398, Japan Peng@pu-toyama.ac.jp

Zhiyi Yu

Department of Thermal Engineering,  Tsinghua University, Beijing 100084, P. R. China


Corresponding author.

J. Fluids Eng 127(2), 330-338 (Oct 01, 2004) (9 pages) doi:10.1115/1.1881697 History: Received May 18, 2004; Revised October 01, 2004

A combined approach of inverse method and direct flow analysis is presented for the hydrodynamic design of gas-liquid two-phase flow rotodynamic pump impeller. The geometry of impeller blades is designed for a specified velocity torque distribution by treating the two-phase mixture as a homogeneous fluid under the design condition. The three-dimensional flow in the designed impeller is verified by direct turbulent flow analysis, and the design specification is further modified to optimize the flow distribution. A helical axial pump of high specific speed has been developed. To obtain a favorable pressure distribution the impeller blade was back-loaded at the hub side compared to the tip side. Experimental results demonstrate that the designed pump works in a wide flow rate range until the gas volume fraction increases to over 50% and its optimum hydraulic efficiency reaches to 44.0% when the gas volume fraction of two-phase flow is about 15.6%. The validity of design computation has been proved.

Copyright © 2005 by American Society of Mechanical Engineers
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Figure 1

Schematic diagram of helical axial pump stage

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Figure 2

Velocity torque distribution along streamlines

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Figure 3

Computation domain and body-fitted computational grid (203×41×15) for flow analysis

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Figure 4

Distributions of pressure contour (left) and velocity vector (right) in sections parallel to the blade surface between two adjacent blades: (a) in section close to the pressure surface (ξ2=5%), (b) in section at ξ2=25% (c) in section at the middle of blade passage (ξ2=50%), (d) in section at ξ2=75%, and (e) in section close to the suction surface (ξ2=95%)

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Figure 5

Distributions of pressure contour (left) and velocity vector (right) in circumferential sections: (a) In section close to the hub wall (ξ3=7%), (b) In section at the middle span (ξ3=50%), and (c) In section close to the tip wall (ξ3=93%)

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Figure 6

Schematic diagram of gas-liquid two-phase flow pump performance test apparatus: (1) water tank, (2) regulating valve, (3) turbine flowmeter, (4) pressure gauge, (5) air bubble dispersion device, (6) regulating valve, (7) air compressor, (8) float flowmeter, (9) multiphase flow pump, (10) composite torque detector, (11) motor, (12) pressure gage, and (13) regulating valve

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Figure 7

Hydraulic performance curves in pumping single-phase flow of water (φg=0)

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Figure 8

Hydraulic performance in pumping gas-liquid two-phase flow under a certain liquid flow rate: (a) φl=0.068, (b) φl=0.081, and (c) φl=0.101

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Figure 9

Hydraulic performance in pumping gas-liquid two-phase flow under a certain gas volume fraction: (a) GVF=15.0%, (b) GVF=25.0%, and (c) GVF=35.0%




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