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.

Copyright © 2015 by ASME
Your Session has timed out. Please sign back in to continue.


Bicak, M., and Rao, M. D., 2012, “Coupled Squeeze Film Analysis by Reissner–Mindlin Plate Elements,” J. Vib. Control, 18(5), pp. 632–640. [CrossRef]
Dege, M. M., Dogan, M., and Holmes, R., 1985, “The Damping Capacity of a Sealed Squeeze Film Bearing,” ASME J. Tribol., 107(3), pp. 411–418. [CrossRef]
Zhang, J. X., and Roberts, J. B., 1996, “Solutions for the Combined Motion of Finite Length Squeeze Film Dampers Around the Bearing Center,” ASME J. Tribol., 118(3), pp. 617–622. [CrossRef]
Adams, M. J., Aydin, I., Briscoe, B. J., and Sinha, S. K., 1997, “A Finite Element Analysis of the Squeeze Flow of an Elasto-Viscoplastic Paste Material,” J. Non-Newtonian Fluid Mech., 71(1-2), pp. 41–57. [CrossRef]
Yang, J. G., Guo, R., and Tian, Y. W., 2008, “Hybrid Radial Basis Function/Finite Element Modelling of Journal Bearing,” Tribol. Int., 41(12), pp. 1169–1175. [CrossRef]
Manivasakan, V., and Sumathi, G., 2011, “Theoretical Investigation of Couple Stress Squeeze Films in a Curved Circular Geometry,” ASME J. Tribol., 133(4), p. 0417014. [CrossRef]
Ahmad, N., and Singh, J. P., 2007, “A Model for Couple-Stress Fluid Film Mechanism With Reference to Human Joints,” Proc. Inst. Mech. Eng., Part J, 221(6), pp. 755–759. [CrossRef]
Stokes, V. K., 2004, “Couple Stresses in Fluids,” Phys. Fluids, 9(9), pp. 1709–1715. [CrossRef]
Lin, J. R., 2013, “Inertia Force Effects in the Non-Newtonian Couple Stress Squeeze Film Between a Sphere and a Flat Plate,” Tribol. Int., 67(11), pp. 81–89. [CrossRef]
Lin, J., 2000, “Squeeze Film Characteristics Between a Sphere and a Flat Plate: Couple Stress Fluid Model,” Comput. Struct., 75(1), pp. 73–80. [CrossRef]
Delgado, A., and San Andres, L., 2010, “A Model for Improved Prediction of Force Coefficients in Grooved Squeeze Film Dampers and Oil Seal Rings,” ASME J. Tribol., 132(3), p. 0322023. [CrossRef]
San Andres, L., and Delgado, A., 2012, “A Novel Bulk-Flow Model for Improved Predictions of Force Coefficients in Grooved Oil Seals Operating Eccentrically,” Proceedings of The ASME Turbo Expo 2011, Parts A and B, Vancouver, Canada, June 6–10, pp. 499–509.
Sanandres, L. A., and Vance, J. M., 1988, “Effect of Fluid Inertia on the Performance of Squeeze Film Damper Supported Rotors,” ASME J. Eng Gas Turbines Power, 110(1), pp. 51–57. [CrossRef]
Sanandres, L., and Vance, J. M., 1986, “Effects of Fluid Inertia and Turbulence on the Force Coefficients for Squeeze Film Dampers,” ASME J. Eng Gas Turbines Power, 108(2), pp. 332–339. [CrossRef]
El-Shafei, A., and Crandall, S. H., 1991, “Fluid Inertia Forces in Squeeze Film Dampers,” Rotating Mach. Veh. Dyn., 35, pp. 219–228.
Vishwanath, K. P., and Kandasamy, A., 2010, “Inertia Effects in Circular Squeeze Film Bearing Using Herschel-Bulkley Lubricants,” Appl. Math. Modell., 34(1), pp. 219–227. [CrossRef]
Zhang, J., Ellis, J., and Roberts, J. B., 1993, “Observations on the Nonlinear Fluid Forces in Short Cylindrical Squeeze Film Dampers,” ASME J. Tribol., 115(4), pp. 692–698. [CrossRef]
San Andres, L. A., and Vance, J. M., 1987, “Effect of Fluid Inertia on Squeeze-Film Damper Forces for Small-Amplitude Circular-Centered Motions,” ASLE Trans., 30(1), pp. 63–68. [CrossRef]
Ellis, J., Hosseini Sianaki, A., and Roberts, J. B., 1990, “The Complete Determination of Squeeze-Film Linear Dynamic Coefficients From Experimental Data,” ASME J. Tribol., 112(4), pp. 712–724. [CrossRef]
Diaz, S. E., and San Andrés, L. A., 1999, “A Method for Identification of Bearing Force Coefficients and Its Application to a Squeeze Film Damper With a Bubbly Lubricant,” Tribol. Trans., 42(4), pp. 739–746. [CrossRef]
Fritzen, C., 1986, “Identification of Mass, Damping, and Stiffness Matrices of Mechanical Systems,” ASME J. Vib. Acoust., 108(1), pp. 9–16. [CrossRef]
Ellis, J., Roberts, J. B., and Hosseini Sianaki, A., 1988, “A Comparison of Identification Methods for Estimating Squeeze-Film Damper Coefficients,” ASME J. Tribol., 110(1), pp. 119–127. [CrossRef]
Szeri, A. Z., 2011, Fluid Film Lubrication, Cambridge University Press, Cambridge, UK.
Chen, C. H., Kang, Y., Chang, Y., Wang, Y., and Lee, H., 2006, “Influence of Restrictor on Stability of the Rigid Rotor–Hybrid Bearing System,” J. Sound Vib., 297(3), pp. 635–648. [CrossRef]


Grahic Jump Location
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.

Grahic Jump Location
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.

Grahic Jump Location
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

Grahic Jump Location
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

Grahic Jump Location
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

Grahic Jump Location
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




Some tools below are only available to our subscribers or users with an online account.

Related Content

Customize your page view by dragging and repositioning the boxes below.

Related Journal Articles
Related eBook Content
Topic Collections

Sorry! You do not have access to this content. For assistance or to subscribe, please contact us:

  • TELEPHONE: 1-800-843-2763 (Toll-free in the USA)
  • EMAIL: asmedigitalcollection@asme.org
Sign In