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Research Papers: Mixed and Boundary Lubrication

Modeling Sliding Contact Temperatures, Including Effects of Surface Roughness and Convection

[+] Author and Article Information
F. E. Kennedy

Thayer School of Engineering,
Dartmouth College,
Hanover, NH 03755
e-mail: francis.kennedy@dartmouth.edu

X. Tian

CDW Corp.,
Vernon Hills, IL 60061
e-mail: tiansteveng@gmail.com

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received June 2, 2015; final manuscript received August 4, 2015; published online June 21, 2016. Assoc. Editor: George K. Nikas.

J. Tribol 138(4), 042101 (Jun 21, 2016) (9 pages) Paper No: TRIB-15-1180; doi: 10.1115/1.4032841 History: Received June 02, 2015; Revised August 04, 2015

The ability to predict contact surface temperatures in rolling/sliding contacting bodies is important if failure of tribological components is to be avoided. Many works on surface temperature analysis and prediction have been published over the past 75 years or so, but most of the analytical solutions that are readily available do not include such important factors as finite body geometry, surface roughness, or convective cooling. Approaches for addressing these deficiencies are presented in this paper. This paper builds on previous analytical work by the authors and others, and presents models that are based on experimental observations of contact temperatures and factors that affect them. It is shown that the total surface temperature rise above ambient temperature is the sum of nominal temperature rise and flash temperature rise. Models are developed for calculating nominal surface temperature rise for sliding bodies of finite size, including effects of both convection and conduction. Flash temperature models are developed for both single and multiple contacts, as would be found with rough surfaces. Methods are presented that are valid for a variety of geometries and kinematic operating conditions, and techniques are also presented for partitioning the frictional heat between the two contacting surfaces. Examples of the use of the methodology are presented, along with experimental verification of the predictions.

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Figures

Grahic Jump Location
Fig. 1

Schematic diagrams of (a) a single square asperity on a stationary surface in sliding contact with a moving flat surface and (b) a square asperity on a stationary surface in sliding contact with a square asperity on a moving surface

Grahic Jump Location
Fig. 2

Schematic diagram of a nominal contact area on a sliding surface containing multiple contacting asperities

Grahic Jump Location
Fig. 3

(a) Schematic diagram of ring-on-disk tribotester, with TFTC on stationary disk; (b) contacting surface of rotating ring, showing real area of contact Ar; and (c) contacting surface of stationary disk, showing swept contact area Aswept and TFTC location

Grahic Jump Location
Fig. 4

Variation of measured surface temperature after 2 mins of sliding during unidirectional unlubricated test of UHMWPE ring against glass disk. Normal load 75 N. Background temperature Tb = 21.5 °C. Rotational speed = 300 rpm (5.0 Hz).

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