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Research Papers: Friction & Wear

An Investigation of the Impacts of Contact Parameters on Wear Coefficient

[+] Author and Article Information
V. Janakiraman, A. Kahraman

The Ohio State University,
201 West 19th Avenue,
Columbus, OH 43210

S. Li

Wright State University,
3640 Colonel Glenn Highway,
Dayton, OH 45435
e-mail: sheng.li@wright.edu

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received January 22, 2014; final manuscript received April 11, 2014; published online May 6, 2014. Assoc. Editor: Xiaolan Ai.

J. Tribol 136(3), 031602 (May 06, 2014) (7 pages) Paper No: TRIB-14-1026; doi: 10.1115/1.4027440 History: Received January 22, 2014; Revised April 11, 2014

In this study, the wear depths under different loads, speeds, lubricant temperatures, and surface roughness amplitudes are experimentally determined using a twin-disk rolling contact setup. A point contact wear model combining a contact formulation and Archard's wear equation in an iterative manner is developed to simulate the wear process of the experiments. By matching the measured and predicted wear profiles, the wear coefficients under different operating and surface conditions are determined. It is found that the wear coefficient increases when either the load or the surface roughness amplitude increases and decreases as the lubricant pressure-viscosity coefficient increases. Within the operating ranges considered, it is observed that the lubricant pressure-viscosity coefficient is the most influential parameter on wear, the load has the least impact, and the surface roughness amplitude is in between. Lastly, a regression formula is given for the estimation of Archard's wear coefficient.

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References

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Figures

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Fig. 1

(a) Front view and (b) top view schematics of the dual head twin-disk rolling contact test setup

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Fig. 2

Open test compartment with specimens in the unloaded condition

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Fig. 3

Specimens showing the axially ground roughness texture

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Fig. 4

Comparisons of the worn surface profiles measured at three circumferential positions that are positioned 120 deg away from each other for (a) a specimen pair with relatively large wear and (b) a specimen pair with relatively small wear. The upper row corresponds to the rollers and the lower row corresponds to the disks. The solid line, dashed line, and dotted line correspond to the 0 deg, 120 deg, and 240 deg measurement positions, respectively. The gray lines represent the initial profiles.

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Fig. 5

Iterative computational algorithm for wear prediction

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Fig. 6

Comparisons between the measured (solid lines) and predicted (dashed lines) wear profiles of roller specimens under the test conditions of the (a) baseline (test 3), (b) medium speed (test 4), (c) low speed (test 8), (d) low temperature (test 11), (e) high roughness amplitude (test 16), and (f) low roughness amplitude (test 18) as defined in Table 2. Here, the dotted line represents the initial profile.

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Fig. 7

Comparisons between the measured (solid lines) and predicted (dashed lines) wear profiles of disk specimens under the test conditions of the (a) baseline (test 3), (b) medium speed (test 4), (c) low speed (test 8), (d) low temperature (test 11), (e) high roughness amplitude (test 16), and (f) low roughness amplitude (test 18), as defined in Table 2. Here, the dotted line represents the initial profile.

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Fig. 8

Comparison of the measured k to the predicted k∧ (regression fit) for as-carburized SAE 4620M with the operating and surface conditions considered

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