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TECHNICAL PAPERS

Influence of Inlet Conditions on the Thermohydrodynamic State of a Fully Circumferentially Grooved Journal Bearing

[+] Author and Article Information
P. S. Keogh

Department of Mechanical Engineering, University of Bath, Bath BA2 7AY, United Kingdome-mail: enspsk@bath.ac.uk

M. M. Khonsari

Mechanical Engineering Department, 2508 CEBA, Louisiana State University, Baton Rouge, LA 70803e-mail: khonsari@me.lsu.edu

J. Tribol 123(3), 525-532 (Jul 06, 2000) (8 pages) doi:10.1115/1.1308029 History: Received February 15, 2000; Revised July 06, 2000
Copyright © 2001 by ASME
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References

Pinkus,  O., 1956, “Experimental Investigation of Resonant Whip,” ASME J. Appl. Mech., 78, pp. 975–983.
Newkirk,  B. L., and Lewis,  J. F., 1956, “Oil-Film Whirl—An Investigation of Disturbances due to Oil Films in Journal Bearings,” Trans. ASME, 78, pp. 21–27.
Akkok, M., and Ettles, C. M., 1978, “The Effect of Loading Intensity and Feed Pressure on the Whirl Stability of a Circumferentially Grooved Journal Bearing,”ASLE Paper 78-LC-6B-3.
Akkok, M., and Ettles, C. M., 1979, “The Effect of Grooving and Bore Shape on the Stability of Journal Bearings,” ASLE Paper 79-AM-6D-3.
Ettles,  C. M., and Cameron,  A., 1968, “Considerations of Flow Across a Bearing Groove,” ASME J. Lubr. Technol., 90, pp. 313–319.
Mitsui,  J., Hori,  Y., and Tanaka,  M., 1983, “Thermohydrodynamic Analysis of Cooling Effect of Supply Oil in Circular Journal Bearing,” ASME J. Lubr. Technol., 105, pp. 414–421.
Heshmat,  H., and Pinkus,  O., 1986, “Mixing Inlet Temperatures in Hydrodynamic Bearings,” ASME J. Tribol., 108, pp. 231–248.
So,  H., and Shieh,  J. A., 1987, “The Cooling Effects of Supply Oil on Journal Bearings for Varying Inlet Conditions,” Tribol. Int., 20, pp. 79–89.
Ott,  H. H., and Paradissiadis,  G., 1988, “Thermohydrodynamic Analysis of Journal Bearings Considering Cavitation and Reverse Flow,” ASME J. Tribol., 110, pp. 439–447.
Roberts,  J. B., and Mason,  P. J., 1986, “An Experimental Investigation of Pressure Distributions in a Journal Bearing Operating in the Transition Regime,” J. Mech. Eng. Sci., 200, pp. 251–264.
Clayton,  G. A., and Taylor,  C. M., 1990, “Design Data for the Steadily Loaded Full Circumferentially Grooved Plain Journal Bearing,” J. Mech. Eng. Sci., 204, pp. 53–61.
Maki,  E. R., and Ezzat,  H. A., 1980, “Thermally Induced Whirl of a Rigid Rotor on Hydrodynamic Journal Bearings,” ASME J. Lubr. Technol., 102, pp. 8–14.
Dowson,  D., 1962, “A Generalized Reynolds Equation for Fluid-Film Lubrication,” Int. J. Mech. Sci., 4, pp. 159–170.
Taylor,  G. I., 1923, “Stability of a Viscous Liquid Contained Between Two Rotating Cylinders,” Trans. R. Soc. London, 223, pp. 289–343.
Kaye,  J., and Elgar,  E. C., 1958, “Modes of Adiabatic and Diabatic Fluid Flow in an Annulus with an Inner Rotating Cylinder,” Trans. ASME, 80, pp. 753–765.
Vohr,  J. H., 1968, “An Experimental Study of Taylor Vortices and Turbulence in Flow Between Eccentric Cylinders,” ASME J. Lubr. Technol., 90, pp. 285–296.
Wendt,  F., 1933, “Turbulente Stromungen Zwischen Zwei Rotierenden Konaxialen Zylindern,” Ingenieur-Archiv., 4, pp. 577–595.

Figures

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Schematic diagram of fully circumferentially grooved journal bearing
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(a) Axial profile of fully circumferentially grooved journal bearing showing groove supply and film entry temperatures; (b) Cross section of fully circumferentially grooved journal bearing through a bearing land
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Comparison of predicted temperatures T⁁B,T⁁f with those measured by Maki and Ezzat. The measured supply temperatures were used as the film inlet temperatures for the predictions with a 23°C ambient
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Comparison of predicted mean bearing temperatures T⁁B with those measured by Maki and Ezzat. The measured supply temperatures were used to evaluate the film inlet temperatures according to Eq. (29) with Φ=0 and a 23°C ambient. The α values range from 0 to 1 in steps of 0.1
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Comparison of predicted mean bearing temperatures T⁁B with those measured by Maki and Ezzat. The measured supply temperatures were used to evaluate the film inlet temperatures according to Eq. (29) with Φ=0 and a 30°C ambient. The α values range from 0 to 1 in steps of 0.1
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Comparison of predicted mean bearing temperatures T⁁B with those measured by Maki and Ezzat. The measured supply temperatures were used to evaluate the film inlet temperatures according to Eq. (29) with the source term included and a 30°C ambient. The α values range from 0 to 1 in steps of 0.1
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Contour plot showing variation of predicted maximum bearing temperature (°C) with eccentricity ratio and groove supply temperature. The running speed is 1047 rad/s with a 30°C ambient. The film inlet temperatures were evaluated with α=0.1
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Contour plot showing variation of predicted film inlet temperature T0 (°C) with eccentricity ratio and groove supply temperature. The running speed is 1047 rad/s with a 30°C ambient. The film inlet temperatures were evaluated with α=0.1
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Variation of predicted attitude angle with eccentricity ratio and groove supply temperature. The running speed is 1047 rad/s with a 30°C ambient. The film inlet temperatures were evaluated with α=0.1
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Dimensionless pressure contour plot with ε=0.5. The running speed is 1047 rad/s with a 30°C ambient. The groove supply temperature was 60°C

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