0
Research Papers

Gear Dynamics Analysis With Turbulent Journal Bearings Mounted Hybrid Squeeze Film Damper—Chaos and Active Control Analysis

[+] Author and Article Information
Cai-Wan Chang-Jian

Department of Mechanical and
Automation Engineering,
I-Shou University,
1, Section 1, Hsueh-Cheng Rd.,
Ta-Hsu District,
Kaohsiung City,
Taiwan 84001, China

Contributed by the Design Engineering Division of ASME for publication in the JOURNAL OF COMPUTATIONAL AND NONLINEAR DYNAMICS. Manuscript received June 26, 2013; final manuscript received January 10, 2014; published online September 12, 2014. Assoc. Editor: Stefano Lenci.

J. Comput. Nonlinear Dynam 10(1), 011011 (Sep 12, 2014) (11 pages) Paper No: CND-13-1160; doi: 10.1115/1.4026568 History: Received June 26, 2013; Revised January 10, 2014

The hybrid squeeze film damper mounted turbulent journal bearing–gear system is proposed in this paper. The nonlinear dynamics of a gear pair supported by such bearing is studied. Numerical results show that, due to the nonlinear factors of lubricant film force, the trajectory of the pinion demonstrates a complex dynamics with dimensionless unbalance parameters. Poincaré maps and bifurcation diagrams are used to analyze the behavior of the pinion trajectory in the horizontal direction. The maximum Lyapunov exponent is used to determine if the system is in a state of chaotic motion. In order to avoid the nonsynchronous chaotic vibrations, an increased proportional gain kp = 0.1 is applied to control this system. It is shown that the pinion trajectory will leave chaotic motion to periodic motion in the steady state under control action.

FIGURES IN THIS ARTICLE
<>
Copyright © 2015 by ASME
Your Session has timed out. Please sign back in to continue.

References

Nikolajsent, J. I., and Holmes, R., 1979, “Investigation of Squeeze-Film Isolators for the Vibration Control of a Flexible Rotor,” J. Mech. Eng. Sci., 21(4), pp. 247–252. [CrossRef]
Sykes, J. E. H., and Holmes, R., 1990, “The Effect of Bearing Misalignment on the Non-Linear Vibration of Aero-Engine Rotor-Damper Assemblies,” Proc. Inst. Mech., 204, pp. 83–99. [CrossRef]
Zhao, J. Y., Linnett, I. W., and Mclean, L. J., 1994, “Subharmonic and Quasi-Periodic Motion of an Eccentric Squeeze Film Damper-Mounted Rigid Rotor,” ASME J. Vib. Acoust., 116(3), pp. 357–363. [CrossRef]
Morgan, V. T., and Cameron, A., 1957, “Mechanism of Lubrication in Porous Metal Bearings,” Proceedings of the Conference on Lubrication and Wear, Institution of Mechanical Engineers, London, pp. 151–157.
Arghir, M., Lez, L. S., and Frene, J., 2006, “Finite-Volume Solution of the Compressible Reynolds Equation: Linear and Non-Linear Analysis of Gas Bearings,” Proc. Inst. Mech. Part J, J. Eng. Tribol., 220, pp. 599–617. [CrossRef]
San Andrés, L., and Ryu, K., 2008, “Flexure Pivot Tilting Pad Hybrid Gas Bearings: Operation With Worn Clearances and Two Load-Pad Configurations,” ASME J. Eng. Gas Turbines Power, 130(4), p. 042506. [CrossRef]
San Andrés, L., and Ryu, K., 2008, “Hybrid Gas Bearings With Controlled Supply Pressure to Eliminate Rotor Vibrations While Crossing System Critical Speeds,” ASME J. Eng. Gas Turbines Power, 130(6), p. 062505. [CrossRef]
Savoulides, N., and Breuer, K. S., 2001, “Low-Order Models for Very Short Hybrid Gas Bearings,” ASME J. Tribol., 123(2), pp. 368–375. [CrossRef]
Zirkelback, N., and Andrés, L. S., 1998, “Finite Element Analysis of Herringbone Groove Journal Bearings: A Parametric Study,” ASME J. Tribol., 120(2), pp. 234–240. [CrossRef]
Mittwollen, N., and GlienickeJ., 1990, “Operating Conditions of Multi-Lobe Journal Bearings Under High Thermal Loads,” ASME J. Tribol., 112(2), pp. 330–338. [CrossRef]
Hashimoto, H., Wada, S., and Nojima, K., 1986, “Performance Characteristics of Worn Journal Bearings in Both Laminar and Turbulent Regimes, Part I: Steady State Characteristics,” ASLE Trans., 29(4), pp. 565–571. [CrossRef]
Hashimoto, H., Wada, S., and Nojima, K., 1986, “Performance Characteristics of Worn Journal Bearings in Both Laminar and Turbulent Regimes, Part II: Dynamic Characteristics,” ASLE Trans., 29(4), pp. 572–577. [CrossRef]
Capone, G., Russo, M., and Russo, R., 1987, “Dynamic Characteristics and Stability of a Journal Bearing in a Non-Laminar Lubrication Regime,” Tribol. Int., 20, pp. 255–260. [CrossRef]
Kumar, A., and Mishra, S. S., 1996, “Stability of a Rigid Rotor in Turbulent Hydrodynamic Worn Journal Bearings,” Wear, 193, pp. 25–30. [CrossRef]
Lin, T. R., 1996, “The Effects of Three-Dimensional Irregularities on the Performance Characteristics of Turbulent Journal Bearing,” Wear, 196, pp. 126–132. [CrossRef]

Figures

Grahic Jump Location
Fig. 1

Schematic illustration of a hybrid squeeze film damper mounted the gear–bearing system under turbulent flow effect

Grahic Jump Location
Fig. 2

Model of force diagram between pinion and gear

Grahic Jump Location
Fig. 3

Bifurcation diagrams of gear–bearing system under turbulent flow effect using dimensionless unbalance parameter β as a bifurcation parameter

Grahic Jump Location
Fig. 4

Simulation results obtained for gear–bearing system with β = 0.56 (xp)

Grahic Jump Location
Fig. 5

Bifurcation diagrams of a gear–bearing system supported by HSFD under turbulent flow effect with active control using dimensionless unbalance parameter β as a bifurcation parameter with kp = 0.01

Grahic Jump Location
Fig. 6

Simulation results obtained for a gear–bearing system with β = 0.32 (xp)

Grahic Jump Location
Fig. 7

Simulation results obtained for a gear–bearing system with β = 0.40 (xp)

Grahic Jump Location
Fig. 8

Simulation results obtained for a gear–bearing system with β = 0.54 (xp)

Grahic Jump Location
Fig. 9

Simulation results obtained for a gear–bearing system with β = 0.56 (xp)

Grahic Jump Location
Fig. 10

The time response of u¯(1) and u¯(2) at β = 0.54 with kp = 0.01

Grahic Jump Location
Fig. 11

The time responses of pinion trajectories at β = 0.54 with kp = 0.01 changes to kp = 0.1 from nondimensional time ϕ = 1570

Grahic Jump Location
Fig. 12

The time responses of u¯(1) and u¯(2) at β = 0.54 with kp = 0.01 changes to kp = 0.1 from nondimensional time ϕ = 1570

Tables

Errata

Discussions

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