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Research Papers: Friction and Wear

Wear Modeling of Nanometer Thick Protective Coatings

[+] Author and Article Information
Jungkyu Lee

Department of Mechanical Science
and Engineering,
University of Illinois at Urbana Champaign,
Urbana, IL 61801

Youfeng Zhang

Department of Mechanical Engineering,
Texas A&M University,
College Station, TX 77843

Robert M. Crone, Narayanan Ramakrishnan

Seagate Technology LLC,
Minneapolis, MN 55416

Andreas A. Polycarpou

Department of Mechanical Science and Engineering,
University of Illinois at Urbana Champaign,
Urbana, IL 61801;
Department of Mechanical Engineering,
Texas A&M University,
College Station, TX 77843
e-mail: apolycarpou@tamu.edu

1Present address: Seagate Technology LLC, Minneapolis, MN 55416.

2Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received August 23, 2015; final manuscript received April 22, 2016; published online August 11, 2016. Assoc. Editor: Min Zou.

J. Tribol 139(2), 021601 (Aug 11, 2016) (9 pages) Paper No: TRIB-15-1305; doi: 10.1115/1.4033492 History: Received August 23, 2015; Revised April 22, 2016

Use of nanometer thin films has received significant attention in recent years because of their advantages in controlling friction and wear. There have been significant advances in applications such as magnetic storage devices, and there is a need to explore new materials and develop experimental and theoretical frameworks to better understand nanometer thick coating systems, especially wear characteristics. In this work, a finite element model is developed to simulate the sliding wear between the protruded pole tip in a recording head (modeled as submicrometer radius cylinder) and a rigid asperity on the disk surface. Wear is defined as plastically deformed asperity and material yielding. Parametric studies reveal the effect of the cylindrical asperity geometry, material properties, and contact severity on wear. An Archard-type wear model is proposed, where the wear coefficients are directly obtained through curve fitting of the finite element model, without the use of an empirical coefficient. Limitations of such a model are also discussed.

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References

Figures

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Fig. 1

Finite element model used for sliding contact analysis of two asperities, with 2 nm thick DLC

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Fig. 2

Comparison of FEA and analytical/Hertzian results for normalized mean contact pressure versus normalized interference

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Fig. 3

Typical undeformed and deformed shapes of the pole tip after sliding interception with a rigid asperity

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Fig. 4

PEEQ contour plots of the pole tip under normal contact ((a) and (c)) and sliding contact conditions ((b) and (d)), using material properties in Table 1. The pole tip is uncoated for (a) and (b), and coated with a 2 nm thick DLC for (c) and (d) (interference = 2 nm).

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Fig. 5

Typical PEEQ contour of the pole tip showing plastically deformed area. The area shown in gray color in (a) plastically yielded from sliding contact with a disk asperity. The area shown in (b) of plastically deformed zone is extracted from (a).

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Fig. 6

(a) Shear and (b) normal reaction forces as a function of sliding distance for various interference values (RTA = 1.5 μm, E = 200 GPa, μ = 0)

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Fig. 7

(a) Shear and (b) normal reaction forces as a function of sliding distance for various friction coefficient values (RTA = 1.5 μm, E = 200 GPa, interference = 3 nm)

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Fig. 8

(a) Wear depth as a function of sliding distance for various interference values, and (b) mean contact pressure (RTA = 1.5 μm, E = 200 GPa, μ = 0.1)

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Fig. 9

Dimensionless (a) deformed area and (b) substrate plastically deformed area (potential wear area) for different sphere radii with a substrate elastic modulus of 250 GPa and an interference value of 1 nm

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Fig. 10

Dimensionless (a) deformed area and (b) substrate yielded area (potential wear area) versus dimensionless normal load, P*, for different values of E/Y0, solid lines are fitted curves

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Fig. 11

Wear coefficient of (a) deformed area and (b) substrate yielded area (potential wear area) versus dimensionless normal load, P*, for different values of E/Y0, solid lines are fitted curves

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