On the Theory of Thermal Elastohydrodynamic Lubrication at High Slide-Roll Ratios—Circular Glass-Steel Contact Solution at Opposite Sliding

Feng Guo; Peiran Yang; Shiyue Qu

doi:10.1115/1.1330739

Journal of Tribology | Volume 123 | Issue 4 | TECHNICAL PAPERS

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On the Theory of Thermal Elastohydrodynamic Lubrication at High Slide-Roll Ratios—Circular Glass-Steel Contact Solution at Opposite Sliding

Feng Guo, Peiran Yang and Shiyue Qu

[+] Author and Article Information

Feng Guo

Department of MEEM, City University of Hong Kong, Tat Chee Avenue, Kowloon, Hong Kong

Peiran Yang, Shiyue Qu

Department of Mechanical Engineering, Qingdao Institute of Architecture and Engineering, Qingdao, 266033, People’s Republic of China

J. Tribol 123(4), 816-821 (Sep 14, 2000) (6 pages) doi:10.1115/1.1330739 History: Received October 28, 1999; Revised September 14, 2000

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References

Gohar, R., and Cameron, A., 1967, “The Mapping of Elastohydrodynamic Contacts,” ASLE Trans., 10, pp. 215–225.

Ranger, A. P., Ettles, C. M. M., and Cameron, A., 1975, “The Solution of the Point Contact Elastohydrodynamic Problem,” Proc. R. Soc. London, Ser. A, 346, pp. 227–244.

Hamrock, B. J., and Dowson, D., 1977, “Isothermal Elastohydrodynamic Lubrication of Point Contact: Part III—Full Flooded Results,” ASME J. Lubr. Technol., 99, pp. 264–276.

Venner, C. H., 1991, “Multilevel Solution of the EHL Line and Point Contact Problems,” Ph.D. thesis, Twente University, Enschede, Netherland.

Zhu, D., and Wen, S., 1984, “A Full Numerical Solution for the Thermal Elastohydrodynamic Problem in Elliptical Contacts,” ASME J. Tribol., 106, pp. 246–254.

Kim, K. H., and Sadeghi, F., 1993, “Three-Dimensional Temperature Distribution in EHD Lubrication: Part II—Point Contact and Numerical Formulation,” ASME J. Tribol., 115, pp. 36–45.

Kim, K. H., and Sadeghi, F., 1991, “Non-Newtonian Elastohydrodynamic Lubrication of Point Contact,” ASME J. Tribol., 113, pp. 703–711.

Lee, R. T., Hsu, C. H., and Kuo, W. F., 1995, “Multilevel Solution for Thermal Elastohydrodynamic Lubrication of Rolling/Sliding Circular Contacts,” Tribol. Int., 28, No. 8, pp. 541–552.

Chiu, Y. P., and Sibley, L. B., 1972, “Contact Shape and Non-Newtonian Effects in Elastohydrodynamic Point Contacts,” ASLE Lubr. Eng., 28, pp. 48–60.

Kaneta, M., Nishikawa, H., Kanada, T., and Matsuda, K., 1996, “Abnormal Phenomena Appearing in EHL Contacts,” ASME J. Tribol., 118, pp. 886–892.

Kaneta, M., Nishikawa, H., Kameishi, K., Sakai, T., and Ohno, N., 1992, “Effects of Elastic Moduli of Contact Surfaces in Elastohydrodynamic Lubrication,” ASME J. Tribol., 114, pp. 75–80.

Cermark, J., 1998, “Discussion (Abnormal Phenomena Appearing in EHL Contacts),” ASME J. Tribol., 120, pp. 143–144.

Ehret, P., Dowson, D., and Taylor, M., 1998, “On the Lubricant Transport Conditions in Elastohydrodynamic Conjunctions,” Proc. R. Soc. London, Ser. A, 454, pp. 763–787.

Kudish, I. I., 1999, Analysis of Abnormal Phenomena in EHL Contacts, in The Advancing Frontier of Engineering Tribology, Proceedings of the 1999 STLE/ASME, H. S. Cheng Tribology Surveillance, Orlando, FL, pp. 188–196.

Yang, P., and Chang, Q., 2000, “Analysis of Thermoelastohydrodynamic Lubrication of Sliding Surfaces with Zero Entrainment Velocity,” Tribology, 20, pp. 207–210 (in Chinese).

Dyson, A., and Wilson, A. R., 1968–1969, “Film Thickness in Elastohydrodynamic Lubrication at High Slide/Roll Ratios,” Proc. Instn. Mech. Engrs., London, UK, 183 , No. 3P, pp. 81–97.

Cameron, A., 1958, “The Viscosity Wedge,” ASLE Trans., 1, pp. 248–253.

Yang, P., and Wen, S., 1990, “A Generalized Reynolds Equation for Non-Newtonian Thermal Elastohydrodynamic Lubrication,” ASME J. Tribol., 112, pp. 631–636.

Hsiao, H. S., and Hamrock, B. J., 1992, “A Complete Solution for Thermal-Elastohydrodynamic Lubrication of Line Contacts Using Circular Non-Newtonian Fluid Model,” ASME J. Tribol., 114, pp. 540–552.

Yang, P., and Rodkiewicz, C. M., 1992, “On the Numerical Analysis to the Thermal Elastohydrodynamic Lubrication of a Tilting Pad Inclusive of Side Leakage,” STLE Tribol. Trans., 40, pp. 259–266.

Guo, F., and Yang, P., 1999, “Influence of a Ring Flat Zone in the Point Contact Surface on Thermal Elastohydrodynamic Lubrication,” Tribol. Int., 32, No. 3, pp. 167–175.

Figures

Opposite sliding EHL formed by a glass-steel point contact

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Thermal EHL solution of the glass-steel conjunction at opposite sliding in the fast disk case (W=1.61×10⁻⁶,U_e=4.4×10⁻¹¹,α=2.8×10⁻⁸ m2 /N, ξ=2.55): (a) Pressure distribution; (b) film thickness distribution; (c) temperature distribution in the midfilm; and (d) pressure and film thickness on the plane of Y=0

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Film profiles for different U_b,W=2.14×10⁻⁶,U_a=1.0×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

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Effects of U_b on the dimple and traction behavior, U_a=1.0×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

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Pressure and film profiles on the plane of Y=0 under inverse kinematic conditions, W=8.26×10⁻⁷,U_a=1.0×10⁻¹⁰,U_b=−1.4×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

View Large | Save Figure | Download Slide (.ppt)

Temperature distributions within the film on the plane of Y=0 under inverse kinematic conditions (W=8.26×10⁻⁷,U_a=1.0×10⁻¹⁰,U_b=−1.4×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N): (a) The fast disk case; and (b) the fast ball case.

View Large | Save Figure | Download Slide (.ppt)

Film profiles on the plane of Y=0 for different pressure-viscosity coefficients in the fast disk case, W=1.61×10⁻⁶,U_e=4.4×10⁻¹¹,ξ=2.55

View Large | Save Figure | Download Slide (.ppt)

Film profiles on the plane of Y=0 for different loads in the fast disk case, U_e=4.0×10⁻¹¹,α=2.8×10⁻⁸ m2 /N, ξ=3.0

View Large | Save Figure | Download Slide (.ppt)

Film profiles on the plane of Y=0 for different entrainment velocities in the fast disk case, W=1.61×10⁻⁶,α=2.8×10⁻⁸ m2 /N, ξ=3.0

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Guo F, Yang P, Qu S. On the Theory of Thermal Elastohydrodynamic Lubrication at High Slide-Roll Ratios—Circular Glass-Steel Contact Solution at Opposite Sliding. ASME. J. Tribol. 2000;123(4):816-821. doi:10.1115/1.1330739.

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On the Theory of Thermal Elastohydrodynamic Lubrication at High Slide-Roll Ratios—Circular Glass-Steel Contact Solution at Opposite Sliding

References

Figures

Opposite sliding EHL formed by a glass-steel point contact

Film profiles for different U_b,W=2.14×10⁻⁶,U_a=1.0×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

Effects of U_b on the dimple and traction behavior, U_a=1.0×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

Pressure and film profiles on the plane of Y=0 under inverse kinematic conditions, W=8.26×10⁻⁷,U_a=1.0×10⁻¹⁰,U_b=−1.4×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

Temperature distributions within the film on the plane of Y=0 under inverse kinematic conditions (W=8.26×10⁻⁷,U_a=1.0×10⁻¹⁰,U_b=−1.4×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N): (a) The fast disk case; and (b) the fast ball case.

Film profiles on the plane of Y=0 for different pressure-viscosity coefficients in the fast disk case, W=1.61×10⁻⁶,U_e=4.4×10⁻¹¹,ξ=2.55

Film profiles on the plane of Y=0 for different loads in the fast disk case, U_e=4.0×10⁻¹¹,α=2.8×10⁻⁸ m2 /N, ξ=3.0

Film profiles on the plane of Y=0 for different entrainment velocities in the fast disk case, W=1.61×10⁻⁶,α=2.8×10⁻⁸ m2 /N, ξ=3.0

Tables

Errata

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On the Theory of Thermal Elastohydrodynamic Lubrication at High Slide-Roll Ratios—Circular Glass-Steel Contact Solution at Opposite Sliding

References

Figures

Opposite sliding EHL formed by a glass-steel point contact

Film profiles for different Ub,W=2.14×10−6,Ua=1.0×10−10,α=2.8×10−8 m2 /N

Effects of Ub on the dimple and traction behavior, Ua=1.0×10−10,α=2.8×10−8 m2 /N

Pressure and film profiles on the plane of Y=0 under inverse kinematic conditions, W=8.26×10−7,Ua=1.0×10−10,Ub=−1.4×10−10,α=2.8×10−8 m2 /N

Temperature distributions within the film on the plane of Y=0 under inverse kinematic conditions (W=8.26×10−7,Ua=1.0×10−10,Ub=−1.4×10−10,α=2.8×10−8 m2 /N): (a) The fast disk case; and (b) the fast ball case.

Film profiles on the plane of Y=0 for different pressure-viscosity coefficients in the fast disk case, W=1.61×10−6,Ue=4.4×10−11,ξ=2.55

Film profiles on the plane of Y=0 for different loads in the fast disk case, Ue=4.0×10−11,α=2.8×10−8 m2 /N, ξ=3.0

Film profiles on the plane of Y=0 for different entrainment velocities in the fast disk case, W=1.61×10−6,α=2.8×10−8 m2 /N, ξ=3.0

Tables

Errata

Related Content

Journals

Conference Proceedings

eBooks

Film profiles for different U_b,W=2.14×10⁻⁶,U_a=1.0×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

Effects of U_b on the dimple and traction behavior, U_a=1.0×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

Pressure and film profiles on the plane of Y=0 under inverse kinematic conditions, W=8.26×10⁻⁷,U_a=1.0×10⁻¹⁰,U_b=−1.4×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N

Temperature distributions within the film on the plane of Y=0 under inverse kinematic conditions (W=8.26×10⁻⁷,U_a=1.0×10⁻¹⁰,U_b=−1.4×10⁻¹⁰,α=2.8×10⁻⁸ m2 /N): (a) The fast disk case; and (b) the fast ball case.

Film profiles on the plane of Y=0 for different pressure-viscosity coefficients in the fast disk case, W=1.61×10⁻⁶,U_e=4.4×10⁻¹¹,ξ=2.55

Film profiles on the plane of Y=0 for different loads in the fast disk case, U_e=4.0×10⁻¹¹,α=2.8×10⁻⁸ m2 /N, ξ=3.0

Film profiles on the plane of Y=0 for different entrainment velocities in the fast disk case, W=1.61×10⁻⁶,α=2.8×10⁻⁸ m2 /N, ξ=3.0