0
Research Papers: Elastohydrodynamic Lubrication

Influence of Lubricant Traction Coefficient on Cage's Nonlinear Dynamic Behavior in High-Speed Cylindrical Roller Bearing

[+] Author and Article Information
Wenhu Zhang

School of Mechatronics Engineering,
Northwestern Polytechnical University,
Xi'an 710071, China
e-mail: 526916105@qq.com

Sier Deng

Professor
School of Mechatronics Engineering,
Henan University of Science and Technology,
Luoyang 471003, China
e-mail: dse@haust.edu.cn

Guoding Chen

Professor
School of Mechatronics Engineering,
Northwestern Polytechnical University,
Xi'an 710071, China
e-mail: gdchen@nwpu.edu.cn

Yongcun Cui

School of Mechatronics Engineering,
Northwestern Polytechnical University,
Xi'an 710071, China
e-mail: 372865368@qq.com

1Corresponding author.

Contributed by the Tribology Division of ASME for publication in the JOURNAL OF TRIBOLOGY. Manuscript received July 12, 2016; final manuscript received March 1, 2017; published online June 30, 2017. Assoc. Editor: Xiaolan Ai.

J. Tribol 139(6), 061502 (Jun 30, 2017) (11 pages) Paper No: TRIB-16-1216; doi: 10.1115/1.4036274 History: Received July 12, 2016; Revised March 01, 2017

In this paper, the formulas of elastohydrodynamic traction coefficients of four Chinese aviation lubricating oils, namely, 4109, 4106, 4050, and 4010, were obtained by a great number of elastohydrodynamic traction tests. The nonlinear dynamics differential equations of high-speed cylindrical roller bearing were built on the basis of dynamic theory of rolling bearings and solved by Hilber–Hughes–Taylor (HHT) integer algorithm with variable step. The influence of lubricant traction coefficient on cage's nonlinear dynamic behavior was investigated, and Poincaré map was used to analyze the influence of four types of aviation lubricating oils on the nonlinear dynamic response of cage's mass center. The period of nonlinear dynamic response of cage's mass center was used to assess cage's stability. The results of this paper provide the theoretical basis for selection of aviation lubricating oil.

Copyright © 2017 by ASME
Your Session has timed out. Please sign back in to continue.

References

Gupta, P. K. , 1990, “ On the Frictional Instabilities in a Cylindrical Roller Bearing,” Tribol. Trans., 33(3), pp. 395–401. [CrossRef]
Gupta, P. K. , 1991, “ Modeling of Instabilities Induced by Cage Clearances in Cylindrical Roller Bearings,” Tribol. Trans., 34(1), pp. 1–8. [CrossRef]
Ghaisas, N. , Wassgren, C. R. , and Sadeghi, F. , 2004, “ Cage Instabilities in Cylindrical Roller Bearing,” ASME J. Tribol., 126(4), pp. 681–689. [CrossRef]
Tomoya, S. , and Kaoru, U. , 2004, “ Dynamic Analysis of Cage Behavior in a Cylindrical Roller Bearing,” NTN Tech. Rev., 71, pp. 8–17.
Yoshida, T. , Tozaki, Y. , Miyake, H. , and Shibata, M., 2008, “ Analysis of Cage Slip in Cylindrical Roller Bearings Considering Non-Newtonian Behavior and Temperature Rise of Lubricating Oil,” J. JAST, 53(11), pp. 752–761.
Ye, Z. H. , Wang, L. , Gu, L. , and Zheng, D., 2010, “ Cage Instabilities in High-Speed Cylindrical Roller Bearings,” ASME Paper No. IJTC2010-41118.
Yang, H. S. , Chen, G. D. , Deng, S. E. , and Li, S., 2010, “ Rigid-Flexible Coupled Dynamic Simulation of Aeroengine Main-Shaft High Speed Cylindrical Roller Bearing,” 3rd International Conference on Advanced Computer Theory and Engineering (ICACTE), Chengdu, China, Aug. 20–22, Vol. 4, pp. 31–35.
Selvaraj, A. , and Marappan, R. , 2011, “ Experimental Analysis of Factors Influencing the Cage Slip in Cylindrical Roller Bearing,” Int. J. Adv. Manuf. Technol., 53(5), pp. 635–644. [CrossRef]
Yang, H. S. , Deng, S. E. , Li, S. , and Chen G. D., 2011, “ Flexible Dynamic Simulation on Cage of Aeroengine High Speed Cylindrical Roller Bearings,” Bearing, 2, pp. 7–11.
Liu, X. H. , Deng, S. E. , and Teng, H. F. , 2013, “ Kinematics Analysis of High-Speed Cylindrical Roller Bearing Cage,” Aeroengine, 39(2), pp. 31–38.
Leblanc, A. , Nelias, D. , and Defaye, C. , 2013, “ Nonlinear Dynamic Analysis of Cylindrical Roller Bearing With Flexible Rings,” J. Sound Vib., 325(7), pp. 145–160.
Takabi, J. , and Khonsari, M. M. , 2014, “ On the Influence of Traction Coefficient on the Cage Angular Velocity in Roller Bearings,” Tribol. Trans., 57(5), pp. 793–805. [CrossRef]
Deng, S. E. , Gu, J. F. , Cui, Y. C. , and Sun C. Y., 2014, “ Analysis of Dynamic Characteristics of High-Speed Cylindrical Roller Bearing Cage,” J Aerosp. Power, 29(1), pp. 207–215.
Chen, L. , Xia, X. , Zheng, H. , and Qiu, M., 2016, “ Chaotic Dynamics of Cage Behavior in a High-Speed Cylindrical Roller Bearing,” Shock Vib., 3, pp. 1–12.
Ye, Z. H. , and Wang, L. Q. , 2015, “ Effects of Axial Misalignment of Rings on the Dynamic Characteristics of Cylindrical Roller Bearings,” Proc. Inst. Mech. Eng., Part J, 230(5), pp. 525–540.
Liu, Q. Z. , 1996, “ Thermal Analysis and Oil-Film Measurement of High Speed Roller Bearing,” Ph.D. thesis, Harbin Institute of Technology, Harbin, China, pp. 35–36.
Rumbarger, J. H. , Filetti, E. G. , and Gubernick, D. , 1973, “ Gas Turbine Engine Mainshaft Roller Bearing-System Analysis,” ASME J. Tribol., 95(4), pp. 401–416.
Hilber, H. M. , Hughes, T. J. R. , and Taylor, R. L. , 1977, “ Improved Numerical Dissipation for Time Integration Algorithms in Structure Dynamics,” Earthquake Eng. Struct. Dyn., 5(3), pp. 283–292. [CrossRef]
Harsha, S. P. , Sandeep, K. , and Prakash, R. , 2003, “ The Effect of Speed of Balanced Rotor on Nonlinear Vibrations Associated With Ball Bearings,” Int. J. Mech. Sci., 45(4), pp. 725–740. [CrossRef]
Sankaravelu, A. , Noah, S. T. , and Burger, C. P. , 1994, “ Bifurcation and Chaos in Ball Bearings,” Nonlinear Stochastic Dyn., 192, pp. 313–318.
Riccardo, R. , 1988, “ Chaos Theory and Some Practical Applications in Technical Analysis,” 11th Annual Conference of the International Federation of Technical Analysts (IFTA), Tokyo, Japan, pp. 1–24.
Deng, S. E. , Yang, H. S. , and Sun, C. Y. , 2013, “ The Test Device for Cage's Dynamic Performance of Cylindrical Roller Bearings,” China Patent No. CN202916093U.
Yang, H. S. , and Chen, G. D. , 2011, “ Analysis of the Roller-Race Contact Deformation of Cylindrical Roller Bearing Using a Improved Slice Method,” International Conference on Mechatronic Science, Electric Engineering and Computer (MEC), Jilin, China, Aug. 19–22, pp. 711–714.
Gupta, P. K. , 1984, Advanced Dynamics of Rolling Elements, Springer-Verlag, Berlin.
Deng, S. E. , Jia, Q. Y. , and Xue, J. X. , 2014, Design Principle of Rolling Bearings, China Standard Press, Beijing, China, pp. 225–237.

Figures

Grahic Jump Location
Fig. 1

Construction of the test rig

Grahic Jump Location
Fig. 2

Traction coefficient μ under different slide to roll ratio: (a) W = 20 N, U = 15 m/s, T = 80 °C and (b) W = 135 N, U = 15 m/s, T = 27 °C

Grahic Jump Location
Fig. 3

Coordinate systems of cylindrical roller bearing

Grahic Jump Location
Fig. 4

Schematic diagram of cylindrical roller bearing: (a) unloaded bearing and (b) loaded bearing

Grahic Jump Location
Fig. 5

Schematic diagram of roller forces

Grahic Jump Location
Fig. 6

Schematic diagram of cage forces

Grahic Jump Location
Fig. 7

Solution procedure of dynamics differential equations

Grahic Jump Location
Fig. 8

Trajectory and Poincaré map under different bearing speeds (4109): (a) ω = 20,000 r/min, (b) ω = 30,000 r/min, and (c) ω = 40,000 r/min

Grahic Jump Location
Fig. 10

Trajectory and Poincaré map under different bearing speeds (4050 and 4010): (a) 4050, ω = 20,000–40,000 r/min and (b) 4010, ω = 20,000–40,000 r/min

Grahic Jump Location
Fig. 9

Trajectory and Poincaré map under different speeds (4106): (a) ω = 20,000 r/min, (b) ω = 30,000 r/min, and (c) ω = 40,000 r/min

Grahic Jump Location
Fig. 11

Trajectory and Poincaré map under different radial forces (4109 and 4106): (a) 4109, Fr = 1000–8000 N and (b) 4106, Fr = 1000–8000 N

Grahic Jump Location
Fig. 12

Trajectory and Poincaré map under different radial forces (4050): (a) Fr = 1000 N, (b) Fr = 4000 N, and (c) Fr = 8000 N

Grahic Jump Location
Fig. 13

Trajectory and Poincaré map under different radial forces (4010): (a) Fr = 1000 N, (b) Fr = 4000 N, and (c) Fr = 8000 N

Grahic Jump Location
Fig. 14

Trajectory and Poincaré map under different lubricant temperatures (4109): (a) T = 80 °C, Fr = 1000 N, (b) T = 130 °C, Fr = 1000 N, (c) T = 180 °C, Fr = 1000 N, and (d) T = 80–180 °C, Fr = 8000 N

Grahic Jump Location
Fig. 15

Trajectory and Poincaré map under different lubricant temperatures (4106): (a) T = 80 °C, Fr = 1000 N, (b) T = 130 °C, Fr = 1000 N, (c) T = 180 °C, Fr = 1000 N, (d) T = 80 °C, Fr = 8000 N, (e) T = 130 °C, Fr = 8000 N, and (f) T = 180 °C, Fr = 8000 N

Grahic Jump Location
Fig. 16

Trajectory and Poincaré map under different lubricant temperatures (4050): (a) T = 80–180 °C, Fr = 1000 N, (b) T = 80 °C, Fr = 8000 N, (c) T = 130 °C, Fr = 8000 N, and (d) T = 180 °C, Fr = 8000 N

Grahic Jump Location
Fig. 17

Trajectory and Poincaré map under different lubricant temperatures (4010): (a) T = 80 °C, Fr = 1000 N, (b) T = 130–180 °C, Fr = 1000 N, and (c) T = 80–180 °C, Fr = 8000 N

Grahic Jump Location
Fig. 18

Cage dynamic performance test rig for aerobearing

Grahic Jump Location
Fig. 19

Whirl orbit of cage detected by test rig: (a) 4109, (b) 4106, (c) 4050, and (d) 4010

Grahic Jump Location
Fig. 20

Whirl orbit of cage detected by test rig: (a) 4109, (b) 4106, (c) 4050, and (d) 4010

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