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TECHNICAL PAPERS: Gas Turbines: Heat Transfer and Turbomachinery

Disintegration of Oil Jets Emerging From Axial Passages at the Face of a Rotating Cylinder

[+] Author and Article Information
A. Glahn, M. F. Blair

United Technologies Research Center, 411 Silver Lane, M/S 129-19, East Hartford, CT 06108

K. L. Allard

Pratt & Whitney, 400 Main Street, East Hartford, CT 06108

S. Busam, O. Schäfer, S. Wittig

Institut für Thermische Strömungsmaschinen, Universität Karlsruhe, Kaiserstrasse 12, Karlsruhe 76128, Germany

J. Eng. Gas Turbines Power 125(4), 1003-1010 (Nov 18, 2003) (8 pages) doi:10.1115/1.1586310 History: Received December 01, 2000; Revised March 01, 2001; Online November 18, 2003
Copyright © 2003 by ASME
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References

Glahn, A., Busam, S., Blair, M. F., Allard, K. L., and Wittig, S., 2000, “Droplet Generation by Disintegration of Oil Films at the Rim of a Rotating Disk,” ASME Paper No. 2000-GT-279.
Wittig,  S., Glahn,  A., and Himmelsbach,  J., 1994, “Influence of High Rotational Speeds on Heat Transfer and Oil Film Thickness in Aero Engine Bearing Chambers,” ASME J. Eng. Gas Turbines Power, 116(2), pp. 395–401.
Chew, J., 1996, “Analysis of the Oil Film on the Inside Surface of an Aero-Engine Bearing Chamber Housing,” ASME Paper No. 96-GT-300.
Glahn,  A., and Wittig,  S., 1996, “Two-Phase Air Oil Flow in Aero Engine Bearing Chambers—Characterization of Oil Film Flows,” ASME J. Eng. Gas Turbines Power, 118(3), pp. 578–583.
Glahn,  A., and Wittig,  S., 1999, “Two-Phase Air Oil Flow in Aero Engine Bearing Chambers—Assessment of an Analytical Prediction Method for the Internal Wall Heat Transfer,” Int. J. Rotating Mach., 5(3), pp. 155–165.
Glahn, A., Busam, S., and Wittig, S., 1997, “Local and Mean Heat Transfer Coefficients Along the Internal Housing Walls of Aero Engine Bearing Chambers,” ASME Paper No. 97-GT-261.
Zaidi, S. H., Ishaq G., Aroussi A., Azzopardi, B. J., 1998, “Two-Phase Flow Study Around a Rotating Liquid Film Using Laser Techniques,” Proceedings of the VSJ-SPIE98, Dec. 6–9, Yokohama, Japan.
Busam, S., Glahn, A., and Wittig, S., 1999, “Internal Bearing Chamber Wall Heat Transfer as a Function of Operating Conditions and Chamber Geometry,” ASME J. Eng. Gas Turbines Power, accepted for publication.
Glahn,  A., Kurreck,  M., Willmann,  M., and Wittig,  S., 1996, “Feasibility Study on Oil Droplet Flow Investigations Inside Aero Engine Bearing Chambers—PDPA Techniques in Combination with Numerical Approaches,” ASME J. Eng. Gas Turbines Power, 118, pp. 749–755.
Glahn, A., Blair, M. F., Allard, K. L., Busam, S., Schäfer, O., and Wittig, S., 2001, “Disintegration of Oil Films Emerging From Radial Holes Inside a Rotating Cylinder,” ASME Paper No. 2001-GT-0202.
Bachalo,  W. D., and Houser,  M. J., 1984, “Phase Doppler Spray Analyzer for Simultaneous Measurements of Drop Size and Velocity Distributions,” Opt. Eng., 23, pp. 583–590.
Willmann,  M., Glahn,  A., and Wittig,  S., 1997, “Phase-Doppler Particle Sizing with Off-Axis Angles in Alexander’s Darkband,” Part. Part. Syst. Charact., 14(3), pp. 122–128.
Hinze,  J. O., and Milborn,  H., 1950, “Atomization of Liquids by Means of a Rotating Cup,” ASME J. Appl. Mech., 17, pp. 145–153.
Lefebvre, A. H., 1989, Atomization and Sprays, Hemisphere, Washington, DC.

Figures

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Average spray diameters compared with those generated at the rim of a rotating disk
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Standard deviation of droplet diameter distribution
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Rotating Cylinder test rig
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Test matrix for droplet size and velocity measurements. (a) Configuration 3: Deq=2.6⋅10−3 m,L/Deq=10,q=1.67⋅10−5 m3/s. (b) Configuration 3: Deq=2.6⋅10−3 m,L/Deq=10,q=2.50⋅10−5 m3/s. (c) Nomenclature.
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Full-access visualization of axial jet disintegration. (a) ω=105 rad/s,q=1.67⋅10−5 m3/s,νL=5⋅10−6 m2/s. (b) ω=524 rad/s,q=1.67⋅10−5 m3/s,νL=5⋅10−6 m2/s.
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Endoscope visualization of axial jet disintegration. (a) ω=314 rad/s , q=2.50⋅10−5 m3/s,νL=5⋅10−6 m2/s. (b) ω=890 rad/s , q=2.50⋅10−5 m3/s,νL=5⋅10−6 m2/s. (c) ω=1047 rad/s , q=2.50⋅10−5 m3/s,νL=5⋅10−6 m2/s.
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N=3000 rpm,q=1.67⋅10−5 m3/s,L/Deq=10,ΔR/DP=0.145. Axial profiles of (a) Mean diameters, (b) Cumulative diameters.
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N=3000 rpm,q=1.67⋅10−5 m3/s,L/Deq=10,ΔR/DP=0.145. Axial profiles of (a) Droplet and spray velocities, (b) Droplet and spray flow angles.
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N=8500 rpm,q=1.67⋅10−5 m3/s,L/Deq=10,ΔZ/DP=0.0. Radial profiles of (a) Mean diameters, (b) Cumulative diameters.
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N=8500 rpm,q=1.67⋅10−5 m3/s,L/Deq=10,ΔZ/DP=0.0. Radial profiles of (a) Droplet and spray velocities, (b) Droplet and spray flow angles.
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Arithmetic mean droplet diameter versus operating conditions
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Spray characteristics compared with those of droplet flows emerging from the rim of a rotating disk. (a) Initial droplet velocity. (b) Initial droplet flow angle.

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