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TECHNICAL PAPERS

A Comparison of Rotordynamic-Coefficient Predictions for Annular Honeycomb Gas Seals Using Three Different Friction-Factor Models

[+] Author and Article Information
Rohan J. D’Souza, Dara W. Childs

Turbomachinery Laboratory, Texas A&M University, College Station, TX 77843

J. Tribol 124(3), 524-529 (May 31, 2002) (6 pages) doi:10.1115/1.1456086 History: Received February 20, 2001; Revised August 15, 2001; Online May 31, 2002
Copyright © 2002 by ASME
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References

Childs, D., 1993, Turbomachinery Rotordynamics: Phenomena, Modeling, and Analysis, John Wiley & Sons, Inc., New York, NY, pp. 293.
Childs,  D., and Moyer,  D., 1985, “Vibration Characteristics of the HPOTP (High-Pressure Oxygen Turbopump) of the SSME (Space Shuttle Main Engine),” ASME J. Eng. Gas Turbines Power, 107, No. 1, pp. 152–159.
Zedian, F., Perez, R., and Stephenson, M., 1993, “The Use of Honeycomb Seals in Stabilizing Two Centrifugal Compressors,” Proceedings of the Twenty-Second Turbomachinery Symposium, Turbomachinery Laboratory, Texas A&M University, College Station, TX, pp. 3–15.
Armstrong, J., and Perricone, F., 1996, “Turbine Instability Solution-Honeycomb Seals,” Proceedings of the Twenty-Fifth Turbomachinery Symposium, Turbomachinery Laboratory, Texas A&M University, College Station, TX, pp. 47–56.
Nelson,  C., 1985, “Rotordynamic Coefficients for Compressible Flow in Tapered Annular Seals,” ASME J. Tribol., 107, pp. 318–325.
Hirs,  G., 1973, “A Bulk-Flow Theory for Turbulence in Lubricating Films,” ASME J. Lubr. Technol., pp. 137–146.
Blasius, H., 1913, “Das Ähnlichkeitsgesetz bei Reibungsvorgängen in Flüssigkeiten,” Forschg. Arb Ing.-Wes., Heft 131, Berlin.
Elrod,  D., Nelson,  C., and Childs,  D., 1989, “An Entrance Region Friction Factor Model Applied to Annular Seals Analysis: Theory Versus Experiment for Smooth and Honeycomb Seals,” ASME J. Tribol., 111, pp. 337–343.
Elrod,  D., Childs,  D., and Nelson,  C., 1990, “An Annular Gas Seal Analysis Using Empirical Entrance and Exit Region Friction Factors,” ASME J. Tribol., 112, No. 2, pp. 196–204.
Ha,  T., and Childs,  D., 1994, “Annular Honeycomb-Stator Turbulent Gas Seal Analysis Using New Friction-Factor Model Based on Flat Plate Tests,” ASME J. Tribol., 116, pp. 352–360.
Pelletti, J., and Childs, D., 1991, “A Comparison of Experimental Results and Theoretical Predictions for the Rotordynamic Coefficients of Short (L/D=1/6) Labyrinth Seals,” Proceedings, 1991 ASME Design Technical Conference, September, DE-Vol-35, pp. 69–76.
Kleynhans,  G., and Childs,  D., 1997, “The Acoustic Influence of Cell Depth on the Rotordynamic Characteristics of Smooth-Rotor/Honeycomb-Stator Annular Gas Seals,” ASME J. Eng. Gas Turbines Power, 119, pp. 949–957.
Moody,  L. F., 1944, “Friction Factors for Pipe Flow,” Trans. ASME, 66, pp. 671–684.
Childs,  D., and Fayolle,  P., 1999, “Test Results for Liquid ‘Damper’ Seals Using a Round-Hole Roughness Pattern for the Stators,” ASME J. Tribol., 121, No. 1, pp. 42–49.
Ha, T. H., and Childs, D., 1991, “Friction Factor Data for Flat-Plate Tests of Smooth and Honeycomb Surfaces (Including Extended Test data),” Texas A&M University, Turbomachinery Laboratory Reports, TL-SEAL-1-91.
Al-Qutub,  A., Elrod,  D., and Coleman,  H., 1999, “A New Friction Factor Model and Entrance Loss Coefficient For Honeycomb Annular Gas Seals,” ASME J. Tribol., 22, No. 3, pp. 622–627.

Figures

Grahic Jump Location
Honeycomb-Stator/Smooth-Rotor seal configuration, Childs 1
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Friction-factor versus Reynolds number at varying clearances, cell width 1.57 mm, and cell depth 2.29 mm; friction-factor data, Ha and Childs 15
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Comparisons of computed rotordynamic coefficients with different friction-factor models at 10, 200 rpm, 6.89 bar inlet pressure, 0.5 pressure ratio, and clearance 0.19 mm (b=1.57 mm,d=2.29 mm)
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Comparisons of the k and c rotodynamic coefficients using reduced (constant exponent) friction-factor models at 10, 200 rpm, 6.89 bar inlet pressure, 0.5 pressure ratio, and clearance 0.19 mm (b=1.57 mm,d=2.29 mm)
Grahic Jump Location
Comparisons of the k and c rotodynamic coefficients using reduced (constant coefficient and exponent) friction-factor models at 10, 200 rpm, 6.89 bar inlet pressure, 0.5 pressure ratio, and clearance 0.19 mm (b=1.57 mm,d=2.29 mm)

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