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TECHNICAL PAPERS

Effect of Surface Finish on Gear Tooth Friction

[+] Author and Article Information
R. D. Britton, C. D. Elcoate, M. P. Alanou, H. P. Evans, R. W. Snidle

School of Engineering, Cardiff University, Cardiff CF23TA, Wales, United Kingdom

J. Tribol 122(1), 354-360 (May 21, 1999) (7 pages) doi:10.1115/1.555367 History: Received January 21, 1999; Revised May 21, 1999
Copyright © 2000 by ASME
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References

Dowson, D., and Higginson, G. R., 1966, Elastohydrodynamic Lubrication, Pergamon Press, Oxford.
Chang,  L., Webster,  M. N., and Jackson,  A., 1993, “On the Pressure Rippling and Roughness Deformation in Elastohydrodynamic Lubrication of Rough Surfaces,” ASME J. Tribol., 115, pp. 439–444.
Elcoate,  C. D., Hughes,  T. G., and Evans,  H. P., 1998, “On the Coupling of the Elastohydrodynamic Problem,” Proc. Instn. Mech. Engnrs., 212C, pp. 307–318.
Patching,  M. J., Kweh,  C. C., Evans,  H. P., and Snidle,  R. W., 1995, “Conditions for Scuffing Failure of Ground and Superfinished Steel Discs at High Sliding Speeds Using a Gas Turbine Engine Oil,” ASME J. Tribol., 117, pp. 482–489.
Johnson,  K. L., and Spence,  D. I., 1991, “Determination of Gear Tooth Friction by Disc Machine,” Tribol. Int., 24, pp. 269–275.
Mobil Oil Corporation, 1979, Mobil EHL Guidebook, Mobil, New York.
Elcoate, C. D., Evans, H. P., and Hughes, T. G., 1997, “Fully Coupled Elastohydrodynamic Solution Techniques for the Analysis of Real Rough Line Contacts Using Finite Element and Finite Difference Models,” Proc. 23 Leeds/Lyon Symposium on Tribology, Elsevier, pp. 27–36.
Johnson,  K. L., and Tevaalwerk,  J. L., “The Shear Behavior of Elastohydrodynamic Oil Films,” Proc. R. Soc. London, A356, p. 217.
Conry,  T. F., Wang,  S., and Cusano,  C. A., “Reynolds-Eyring Equation for Elastohydrodynamic Lubrication in Line Contacts,” ASME J. Lubr. Technol., 109, p. 648.
Elcoate, C. D., Evans, H. P., Hughes, T. G., and Snidle, R. W., 1999, “Thin Film. Time Dependent Micro-EHL Solutions With Real Surface Roughness,” Proc. Leeds/Lyon Symp. Tribol. (in press).
Evans,  C. R., and Johnson,  K. L., “The Rheological Properties of Elastohydrodynamic Lubricants,” Proc. Instn. Mech. Engnrs., 200C, pp. 303–312.

Figures

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Arrangement of the gear friction rig
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Comparison of surface profiles from ground and superfinished gear tooth surfaces. (a) Ground surface, Ra=0.38 μm; (b) superfinished surface, Ra=0.06 μm. Profiles are taken in direction up/down tooth and filtered at 0.08 mm cut-off. Metal is shown below the profile.
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Highly polished surface of test gear teeth
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Typical chart of total gearbox friction and gear tooth bulk temperatures during an experiment. Ground surfaces; imposed torque=48.74 Nm; oil feed temperature=75°C.
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Driving torque and gear tooth temperatures with ground teeth. Imposed torque=67.7 Nm with oil feed at 75°C.
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Driving torque and gear tooth temperatures with superfinished teeth. Imposed torque=67.7 Nm with oil feed at 75°C.
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Comparison of measured power losses for ground and superfinished gears as a function of pinion speed. Imposed torque=48.74 Nm with oil feed at 50°C.
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Comparison of measured power losses for ground and superfinished gears as a function of pinion speed. Imposed torque=48.74 Nm with oil feed at 75°C.
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Comparison of measured power losses for ground and superfinished gears as a function of pinion speed. Imposed torque=48.74 Nm with oil feed at 100°C.
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Combined surface roughness profile (Ra=0.16 μm) used in micro-EHL simulations of tooth contact. Metal is shown below the profile.
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Typical pressure and film profiles obtained from the micro-EHL simulation of tooth contact at two points on the path of contact. Imposed torque=48.74 Nm; pinion speed=1500 rpm; inlet temperature=50°C, (a) Start of engagement (two pairs of teeth in contact); (b) point “2” (one pair of teeth in contact).
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Typical pressure and film profiles obtained from the micro-EHL simulation of tooth contact at two points on the path of contact. Imposed torque=48.74 Nm; pinion speed=5000 rpm; inlet temperature=50°C. (a) Start of engagement (two pairs of teeth in contact); (b) point “2” (one pair of teeth in contact.
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Typical variation of calculated frictional power loss at various points in the meshing cycle. Imposed torque=48.74 Nm; inlet temperature=50°C; pinion speed=500 rpm; assumed Eyring stress=3.5 MPa.
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Comparison of measured power losses and theoretical prediction from micro-EHL model for three assumed values of the Eyring stress over a range of pinion speeds. Imposed torque=48.74 Nm; inlet temperature=50°C.

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