Coupling Fault Dynamics of Rotor System Supported by Rolling Bearing

doi:10.19596/j.cnki.1001-246x.8503

Abstract

Abstract:

Dynamic characteristics of a cracked rotor system supported by corrugated rolling bearing is studied. A ripple model of inner and outer ring surface of rolling bearing is established, in which the respiratory crack of rotor shaft system is described with a comprehensive model. The nonlinear dynamic characteristics of rub impact between rotor system and stator is studied. With Lagrange equation, dynamic equation of crack rub impact rotor system supported by four degree of freedom rolling bearing with waviness is established. A fourth-order Runge Kutta method is used to solve the equation numerically. Effects of parameters such as waviness amplitude, waviness number, bearing clearance and eccentricity on nonlinear characteristics of the system are studied. It shows that in low speed range, with the increase of the maximum amplitude of waviness, the vibration response of the system is gradually chaotic, the number and amplitude of interharmonics increase, and the continuous characteristic spectrum appears gradually. The lateral displacement decreases with the increase of bearing clearance and increases with the increase of eccentricity after reaching a critical speed. After reaching the supercritical speed, the rotor system presents strong nonlinear characteristics. The lateral displacement increases gradually with the increase of the maximum amplitude, and the vibration response changes from chaotic motion to periodic 1 motion and quasi periodic motion with the increase of eccentricity. Under the condition of large bearing clearance, the system tends to be stable with the increase of bearing clearance in a low speed region, while it is in chaotic motion in the ultra-high speed region. Compared with a system with same number of corrugations and balls, a inconsistent system is more stable in the low speed region and more chaotic in the supercritical speed region.

Key words: waviness rolling bearing, rotor, nonlinear dynamics, crackle, rubbing

Dengliang YU, Guofang NAN, Shan JIANG, Chuanchong SONG. Coupling Fault Dynamics of Rotor System Supported by Rolling Bearing[J]. Chinese Journal of Computational Physics, 2022, 39(6): 733-743.

Figures/Tables 16

Fig.1 A schematic of rolling bearing with internal and external ripple fault

Fig.2 A schematic of rub impact force model

Fig.3 A cross section of crack shaft

Fig.4 A schematic of coupling fault rotor system

Table 1 Main parameters of the system

参数	值
轴承处集中质量m₁/kg	4
轮盘处集中质量m₂/kg	32.1
无裂纹转轴刚度k/(N·m^-1)	2.5 × 10⁷
轴承阻尼c₁/(N·m·s^-1)	1 050
圆盘阻尼c₂/(N·m·s^-1)	2 100
摩擦系数f	0.1
定子径向刚度k_r/(N·m^-1)	3.5 × 10⁷
转定子间隙δ/m	2 × 10^-5
偏心量e/m	1 × 10^-5
最大幅值A/m	1 × 10^-6
波纹数N_w	8

Fig.5 Bifurcation diagrams of system vibration response under different maximum amplitudes (a) A=1 × 10-6 m; (b) A=3 × 10-6 m; (c) A=4 × 10-6 m

Fig.6 Spectrum waterfalls of system vibration response under different maximum amplitudes (a) A=1 × 10-6 m; (b) A=3 × 10-6 m; (c) A=4 × 10-6 m

Fig.7 (a) Time history, (b) spectrum and (c) Poincaré section of coupled fault system at ω = 1350 rad ·s-1, A = 1 × 10-6 m

Fig.8 Spectrum diagrams of a coupled fault rotor system with different maximum amplitudes at ω = 350 rad ·s-1 (a) A = 1 × 10-6 m; (b) A = 3 × 10-6 m; (c) A = 4 × 10-6 m

Fig.9 Bifurcation diagrams of system vibration response under ripple numbers (a) Nw = 7; (b) Nw = 9; (c) Nw = 10

Fig.10 Waterfalls of system vibration response spectrum under ripple numbers (a) Nw = 7; (b) Nw = 9; (c) Nw = 10

Fig.11 Time history, (b) axis trajectory, (c) spectrum and (d) Poincaré section diagram of coupled fault rotor system at ω = 1 450 rad ·s-1 and Nw = 10

Fig.12 Bifurcation diagrams of system vibration response under different bearing clearance (a) r = 20 × 10-6 m; (b) r = 30 × 10-6 m; (c) r = 40 × 10-6 m

Fig.13 Spectrum waterfalls of system vibration response under different bearing clearances (a) r = 20 × 10-6 m; (b) r = 30 × 10-6 m; (c) r = 40 × 10-6 m

Fig.14 Bifurcation diagrams of system vibration response under different eccentricity (a) e = 2 × 10-5 m; (b) e = 3 × 10-5 m; (c) e = 5 × 10-5 m

Fig.15 Spectrum waterfalls of system vibration response under different eccentricity (a) e = 2 × 10-5 m; (b) e = 3 × 10-5 m; (c) e = 5 × 10-5 m

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