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TECHNICAL PAPERS

Impeller–Diffuser Interaction in a Centrifugal Compressor

[+] Author and Article Information
Y. K. P. Shum, C. S. Tan

Gas Turbine Laboratory, Massachusetts Institute of Technology, Cambridge, MA 02139

N. A. Cumpsty

Whittle Laboratory, University of Cambridge, Cambridge, England CB3 0DY

J. Turbomach 122(4), 777-786 (Feb 01, 2000) (10 pages) doi:10.1115/1.1308570 History: Received February 01, 2000
Copyright © 2000 by ASME
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References

Dean,  R., and Senoo,  Y., 1960, “Rotating Wakes in Vaneless Diffusers,” ASME J. Basic Eng., 82, pp. 563–574.
Johnston,  R., and Dean,  R., 1966, “Losses in Vaneless Diffusers of Centrifugal Compressors and Pumps,” ASME J. Basic Eng., 88, pp. 49–60.
Cumpsty, N., 1989, Compressor Aerodynamics, Longman Scientific and Technical, Essex, England.
Filipenco,  V., Deniz,  S., Johnston,  J., Greitzer,  E., and Cumpsty,  N., 2000, “Effects of Inlet Flow Field Conditions on the Performance of Centrifugal Compressor Diffusers: Part 1—Discrete-Passage Diffuser,” ASME J. Turbomach., 122, pp. 1–10.
Deniz,  S., Greitzer,  E., and Cumpsty,  N., 2000, “Effects of Inlet Flow Field Conditions on the Performance of Centrifugal Compressor Diffusers: Part 2—Straight-Channel Diffuser,” ASME J. Turbomach., 122, pp. 11–21.
Phillips, M., 1997, “Role of Flow Alignment and Inlet Blockage on Vaned Diffuser Performance,” Report No. 229, Gas Turbine Laboratory, Massachusetts Institute of Technology.
Kirtley,  K., and Beach,  T., 1992, “Deterministic Blade Row Interactions in a Centrifugal Compressor Stage,” ASME J. Turbomach., 114, pp. 304–311.
Dawes,  W., 1995, “A Simulation of the Unsteady Interaction of a Centrifugal Impeller with its Vaned Diffuser: Flows Analysis,” ASME J. Turbomach., 117, pp. 213–222.
Domercq, O., and Thomas, R., 1997, “Unsteady Flow Investigation in a Transonic Centrifugal Compressor Stage,” AIAA Paper No. 97-2877.
Rodgers, C., 1982, “The Performance of Centrifugal Compressor Channel Diffusers,” ASME Paper No. 82-GT-10.
Clements, W., and Artt, D., 1989, “The Influence of Diffuser Vane Leading Edge Geometry on the Performance of a Centrifugal Compressor,” ASME Paper No. 89-GT-163.
Storer,  J., and Cumpsty,  N., 1991, “Tip Leakage Flow in Axial Compressors,” ASME J. Turbomach., 113, pp. 252–259.
Van Zante,  D., Strazisar,  A., Wood,  J., Hathaway,  M., and Okiishi,  T., 2000, “Recommendations for Achieving Accurate Numerical Simulation of Tip Clearance Flows in Transonic Compressor Rotors,” ASME J. Turbomach., 122, this issue, pp. 733–742.
Shapiro, A., 1953, The Dynamics and Thermodynamics of Compressible Fluid Flow, The Ronald Press Company, New York.
Khalid,  S. A., Khalsa,  A., Waitz,  I., Tan,  C., Greitzer,  E., Cumpsty,  N., Adamczyk,  J., and Marble,  F., 1999, “Endwall Blockage in Axial Compressors,” ASME J. Turbomach., 121, pp. 499–509.
McDougall, N., and Dawes, W., 1987, “Numerical Simulation of the Strong Interaction Between a Compressor Blade Clearance Jet and Stalled Passage Flow,” presented at Seventh GAMM Conference on Numerical Methods in Fluid Mechanics, Louvain, Belgium.

Figures

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Unstructured mesh used for the r2/r2=1.092 configuration with the casings of both impeller and diffuser removed
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Impeller total-to-total pressure ratio for the three different radial gap sizes, with the compete characteristic of r2/r2=1.092 case shown
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Mass and time-averaged total pressure distribution along the impeller passage for the three different radial gas sizes
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Effect of radial gap size on impeller total pressure ratio and static pressure ratio, expressed in incremental change from vaneless configuration
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Contours of entropy production ρDs/Dt at impeller exit for the vaneless configuration
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Contours of instantaneous entropy production ρDs/Dt at impeller exit collected at 0.25T time interval for the r2/r2=1.092 configuration
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Incremental entropy production Δ(ρDs/Dt) for the two vaned configurations when compared to the vaneless configuration
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Comparison of main blade clearance periodic tip leakage mass flux at 90, 95, and 99 percent meridional stations
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Comparison of periodic main blade tip loading (pps−pss)/(p02p2) at 90, 95, and 99 percent meridional stations
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Comparisons of pressure recovery Cp and loss Closs for calculations 2, 4, and 5
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Effect of unsteadiness on the swirl angle at midpitch of the diffuser inlet plane

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