Research Papers: Friction & Wear

A Novel Elastic Squeeze Film Total Hip Replacement

[+] Author and Article Information
S. Boedo

Department of Mechanical Engineering,
Rochester Institute of Technology,
Rochester, NY 14623

J. F. Booker

Sibley School of Mechanical
and Aerospace Engineering,
Cornell University,
Ithaca, NY 14853

Contributed by the Tribology Division of ASME for publication in the Journal of Tribology. Manuscript received September 15, 2012; final manuscript received June 25, 2013; published online August 6, 2013. Assoc. Editor: Mihai Arghir.

J. Tribol 136(1), 011101 (Aug 16, 2013) (12 pages) Paper No: TRIB-12-1150; doi: 10.1115/1.4024968 History: Received September 15, 2012; Revised June 25, 2013

This paper describes a new approach to the design of total hip replacements with the goal of enhancing lubrication and reducing wear. Elastic elements and ellipsoidal cup surface geometry are incorporated into the new design to promote and enhance ‘squeeze-film’ action over ‘wedge-film’ action employed in conventional artificial hip joints. Employing an established finite element lubrication model with a realistic gait cycle and realistic ball-to-cup clearance specifications, it is found that significantly larger minimum film thicknesses and significantly smaller maximum film pressures are predicted over the stance-phase portion of the gait cycle when compared with conventional designs.

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Fig. 1

Sample embodiment of squeeze film artificial hip joint

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Fig. 2

Surface geometry of rigid cup portion

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Fig. 3

ISO 14242 duty cycle

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Fig. 4

Spatial view of lubricant film mesh

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Fig. 5

Projected view of lubricant film mesh

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Fig. 15

Planar fluid film element

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Fig. 14

Effect of ellipticity on periodic time histories of minimum film thickness and maximum film pressure: complete hemispherical cup

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Fig. 13

Bearing performance comparison: R1 = 14 mm, C0 = 30 μm

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Fig. 12

Effect of wide slot on bearing performance

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Fig. 11

Film mesh: cup design with wide slot excluded

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Fig. 10

Effect of initial conditions: R1 = 16 mm, μ = 2.5 mPa-s, C0 = 30 μm, δ = 40 μm

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Fig. 9

Effect of ellipticity on bearing performance: R1 = 25 μm, μ = 2.5 mPa-s

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Fig. 8

Effect of ellipticity on bearing performance: R1 = 16 μm, μ = 2.5 mPa-s

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Fig. 7

Pressure distributions at t = 0.5 s: R1 = 16 mm, μ = 2.5 mPa-s

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Fig. 6

Effect of ellipticity on time histories of minimum film thickness and maximum film pressure

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Fig. 16

Hemispherical bearing under axisymmetric pure squeeze

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Fig. 17

Mesh refinement study: hemispherical bearing under pure squeeze

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Fig. 19

Column diameter required for elastic load of 350 N at eZ= 0



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