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Technical Briefs

Numerical Simulation of Low Specific Speed American Petroleum Institute Pumps in Part-Load Operation and Comparison With Test Rig Results

[+] Author and Article Information
Helmut Benigni

 Institute for Hydraulic Fluidmachinery,University of Technology, Graz 8010, Austriahelmut.benigni@hfm.tugraz.at

Helmut Jaberg

 Institute for Hydraulic Fluidmachinery,University of Technology, Graz 8010, Austria

Hoi Yeung

 Department of Offshore, Process and Energy Engineering,Process Systems Engineering Group, Cranfield University, Bedfordshire MK 43 0AL, United Kingdom

Tony Salisbury, Owen Berry, Tim Collins

 Amarinth Ltd.,Bentwater Parks,Rendelesham, Woodbridge, Suffolk IP12 2TW, United Kingdom

J. Fluids Eng 134(2), 024501 (Mar 06, 2012) (9 pages) doi:10.1115/1.4005769 History: Received December 22, 2010; Revised December 02, 2011; Published March 06, 2012; Online March 06, 2012

A low specific speed centrifugal pump is investigated by means of numerical simulation, especially in deep part-load operation. The 3D computational fluid dynamics (CFD) model includes the front and back cavities, a 360 deg impeller and a double volute, as well as suction and pressure pipes. Stationary calculations show a strong clocking effect and lead to an overprediction of the head close to zero flow rate. A one-dimensional estimation of the head at the closed valve operation point is compared to the 3D CFD results and also a series of test rig results. In a second step, the whole head curve is calculated by a fully transient calculation using the shear stress transport–scale-adaptive simulation (SST–SAS) turbulence model. For the net positive suction head (NPSH) estimation, the histogram method is applied providing good correlation to the test rig measurement—as do the head curve and the efficiency.

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Copyright © 2012 by American Society of Mechanical Engineers
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Figures

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Figure 1

Schematic overview of the test rig

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Figure 2

CFD model of the investigated API pump

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Figure 3

Head curves as a result of different post-processing and sub-flowrates through front cavity and balancing holes

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Figure 5

Results of the steady-state calculation

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Figure 6

Detail of flow distribution near the cutwater at different operation points and impeller positions (stationary calculations)

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Figure 7

Transient results in comparison to stationary results

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Figure 8

Fluctuations of the transient values

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Figure 9

Flow in the volute at different time steps (0 deg, 12 deg, 24 deg, 36 deg, 48 deg, and 60 deg) at strong part-load operation

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Figure 10

Comparison of the complex with a simpler setup

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