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Research Papers: Hydrodynamic Lubrication

Analysis of Static and Dynamic Characteristic of Hydrostatic Spherical Hinge

[+] Author and Article Information
Chundong Xu

School of Mechanical Engineering,
Southeast University,
2 Southeast Road, JiangNing District,
Nanjing 210096, China

Shuyun Jiang

School of Mechanical Engineering,
Southeast University,
2 Southeast Road, JiangNing District,
Nanjing 210096, China
e-mail: jiangshy@seu.edu.cn

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received November 12, 2013; final manuscript received July 4, 2014; published online December 12, 2014. Assoc. Editor: J. Jeffrey Moore.

J. Tribol 137(2), 021701 (Apr 01, 2015) (7 pages) Paper No: TRIB-13-1231; doi: 10.1115/1.4028910 History: Received November 12, 2013; Revised July 04, 2014; Online December 12, 2014

A new hydrostatic spherical hinge is developed in this paper to provide a large load capacity. The static and dynamic Reynolds equations in spherical coordinate system for incompressible Newtonian fluid were established using the perturbation method. Finite difference method was employed to solve the load capacity, power loss, oil flow rate, dynamic stiffness, and damping coefficients. This paper provides a new perspective for analysis on the dynamic characteristics of the spherical hinge.

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Figures

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Fig. 1

(a) Structure of the hydrostatic spherical hinge—hydrostatic spherical hinge, (b) structure of the hydrostatic spherical hinge—ball socket, and (c) structure of the hydrostatic spherical hinge—ball head and connected rod. 1-connecting rod, 2-upper oil outlet, 3-orifice restrictor, 4-oil outlets, 5-oil-returning slot, 6-lower oil recess, 7-hole for mounting the restrictor, 8-ball head, 9-lower part of ball socket, 10-upper part of ball socket, 11-upper oil recess, 12-oil inlet, 13-lower film land, 14 and 15-upper film land.

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Fig. 2

The spherical coordinate system of hydrostatic spherical hinge. φ1-angle of oil outlet, φ2, φ3-angles of both edges of the upper oil recess, φ4-angle of outer edge of the film land, and φ5-angle of edge of the lower oil recess.

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Fig. 3

(a) Plots of the load capacity of the hinge—diameter of the orifice d0 = 0.4 × 10−3 m and (b) plots of the load capacity of the hinge—viscosity of the lubricating oil ν = 32 × 10−6 m2/s

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Fig. 4

(a) Flow rate—diameter of the orifice d0 = 0.4 × 10−3 m and (b) flow rate—viscosity of the lubricating oil ν = 32 × 10−6 m2/s

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Fig. 5

(a) Plots of power loss—diameter of the orifice d0 = 0.4 × 10−3 m and (b) plots of power loss—viscosity of the lubricating oil ν = 32 × 10−6 m2/s

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Fig. 6

(a) Plots of dynamic coefficients—direct stiffness coefficients, (b) plots of dynamic coefficients—cross-coupled stiffness coefficients, (c) plots of dynamic coefficients—direct damping coefficients, and (d) plots of dynamic coefficients—cross-coupled damping coefficients

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