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Article

Modeling Gas-Liquid Head Performance of Electrical Submersible Pumps

[+] Author and Article Information
Datong Sun

Baker Atlas, 2001 Rankin Road, Houston, Texas 77073

Mauricio Prado

University of Tulsa, 600 South College Avenue, Tulsa, Oklahoma 74104

J. Pressure Vessel Technol 127(1), 31-38 (Mar 15, 2005) (8 pages) doi:10.1115/1.1845473 History: Received August 16, 2004; Revised September 09, 2004; Online March 15, 2005
Copyright © 2005 by ASME
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References

Beltur, R., 2003, “Experimental Investigation of Performance of Electrical Submersible Pumps in Two-Phase Flow Condition,” M.S. thesis, The University of Tulsa, Oklahoma.
Lea,  J. F., and Bearden,  J. L., 1982, “Effect of Gaseous Fluids on Submersible Pump Performance,” paper SPE 9218, Journal of Petroleum Technology, 34, pp. 2922–2930.
Pessoa, R., 2001, “Experimental Investigation of Two-Phase Flow Performance of Electrical Submersible Pump Stages,” M.S. thesis, The University of Tulsa, Oklahoma.
Sachdeva, R., Doty, D. R., and Schmidt, Z., 1988, Two-Phase Flow Through Electrical Submersible Pumps, Ph.D. dissertation, The University of Tulsa, Oklahoma.
Sachdeva,  R., Doty,  D. R., and Schmidt,  Z., 1994, “Performance of Electric Submersible Pumps in Gassy Wells,” SPE Prod. Facil., 9, pp. 55–60.
Minemura,  K., Uchiyama,  T., Shoda,  S., and Kazuyuki,  E., 1998, “Prediction of Air-Water Two-Phase Flow Performance of a Centrifugal Pump Based on One-Dimensional Two-Fluid Model,” ASME J. Fluids Eng., 120, pp. 327–334.
Sun, D., and Prado, M. G., 2003, “Modeling Gas-Liquid Head Performance of Electrical Submersible Pumps,” Ph.D. dissertation, The University of Tulsa, Oklahoma.
Ishii, M., 1975, Thermo-Fluid Dynamic Theory of Two-Phase Flow, Eyrolles, Paris.
Prado, M. G., 1995, “A Block Implicit Numerical Solution Technique for Two-Phase Multidimensional Steady State Flow,” Ph.D. dissertation, The University of Tulsa, Oklahoma.
Shoham, O., 2001, “Two-Phase Flow Modeling,” The University of Tulsa, Oklahoma.
Sun, D., and Prado, M. G., 2003, “Single-Phase Model for ESP’s Head Performance,” SPE 80925, Oklahoma City, OK.
Chisholm, D., and Sutherland, L. A., 1969, “Prediction of Pressure Changes in Pipeline Systems During Two-Phase Flow,” Institution of Mechanical Engineers/Institution of Mechanical Engineers Joint Symposium on Fluid Mechanics and Measurements in Two-Phase System, Paper No. 4.
Bird, R. B., Stewart, W. E., and Lightfoot, E. N., 1960, Transport Phenomenon, Wiley, New York.
Centrilift, 1994, Submersible Pump Handbook, 5th ed., Claremore, Oklahoma.
Stepanoff, A. J., 1957, Centrifugal and Axial Flow Pumps, Wiley, New York.

Figures

Grahic Jump Location
Gas void fraction distribution along impeller and diffuser channels with pump intake 790,829 Pa (100 psig)
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The gas and liquid distribution inside an impeller channel
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A pump stage of the pump
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Streamline geometric relationships
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Head performance comparison for the fourth stage of pump at gas flow rate 142 SCM/D (5000 SCF/D) and pump intake pressure 446,091 Pa (50 psig)
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Head performance comparison for the fourth stage of pump at gas flow rate 142 SCM/D (5000 SCF/D) and pump intake pressure 790,829 Pa (100 psig)
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Head performance comparison for the fourth stage of pump at gas flow rate 1133 SCM/D (40,000 SCF/D) and pump intake pressure 1,135,566 Pa (150 psig)
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Head performance comparison for the fourth stage of pump at gas flow rate 1699 SCM/D (60,000 SCF/D) and pump intake pressure 1,480,304 Pa (200 psig)
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Head performance comparison for the fourth stage of pump at gas flow rate 2265 SCM/D (80,000 SCF/D) and pump intake pressure 1,825,042 Pa (250 psig)
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All data comparison between predicted pressure increments and measured pressure increments
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Pressure distribution along impeller channel and diffuser channel [intake gas void fraction 20% at pump intake 790,829 Pa (100 psig)]
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Pressure distribution along impeller channel and diffuser channel [intake gas void fraction 20% at pump intake 790,829 Pa (100 psig)]
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Head performance comparison for the fourth stage of pump at gas flow rate 566 SCM/D (20,000 SCF/D) and pump intake pressure 790,829 Pa (100 psig)

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