掘进机主轴承疲劳磨损竞争失效机制的寿命分析

doi:10.16183/j.cnki.jsjtu.2023.319

摘要/Abstract

摘要：

掘进机主轴承服役时在磨损、疲劳等多因素影响下容易发生提前失效,寿命难以预测.为准确计算主轴承寿命,从失效形式出发,建立疲劳磨损竞争失效机制的主轴承寿命模型.首先,提出基于连续损伤力学理论和表面粗糙度修正的磨损理论的轴承寿命模型,定义了轴承疲劳与磨损竞争失效机制;其次,通过APDL程序建立滚子与滚道接触有限元模型,确定了轴承最先失效的滚子滚道并实现了寿命模型的数值求解;最后,通过分析接触应力及切应力的变化,发现在前9个循环周期,磨损引起接触应力降低,抑制了疲劳失效的发生,延长了轴承寿命,在第10个循环周期开始,接触应力增高,磨损促进了疲劳失效的发生.寿命模型综合考虑疲劳磨损的相互作用,更符合实际情况.

关键词: 主轴承, 损伤力学, 磨损理论, 有限元仿真

Abstract:

The main bearing of a tunneling machine is prone to premature failure under the influence of multiple factors such as wear and fatigue during service, making it difficult to predict its lifetime. In order to calculate the lifespan of the main bearing accurately, a life model is proposed that incorporates a fatigue-wear competition failure mechanism from the failure form. First, a bearing life model based on the continuous damage mechanics theory and the wear theory with surface roughness modification is proposed, and the competitive failure mechanism of bearing fatigue and wear is defined. Then, a finite element model is established by using the APDL software to simulate the contact between rollers and raceways, which helps identify the roller raceway where the bearing experiences initial failure, enabling the numerical solution of the life model. Finally, the analysis of the changes in contact stress and shear stress reveals that, during the first nine cycles, wear causes a decrease in contact stress, which suppresses fatigue failure, and extendes the bearing life. However, starting from the tenth cycle, contact stress increases, and wear accelerates the occurrence of fatigue failure. By considering the interaction of fatigue and wear, the proposed life model better reflects the actual situation.

Key words: main bearing, damage mechanics, theory of wear, finite element simulation

中图分类号:

U455.31

那鹏越, 毋振, 刘奇, 霍军周. 掘进机主轴承疲劳磨损竞争失效机制的寿命分析[J]. 上海交通大学学报, 2025, 59(5): 675-683.

NA Pengyue, WU Zhen, LIU Qi, HUO Junzhou. Life Analysis of Wear Fatigue Competition Failure Mechanism of Main Bearing of Boring Machine[J]. Journal of Shanghai Jiao Tong University, 2025, 59(5): 675-683.

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参数	取值
k	1×10^-7
H/(N·mm^-2)	620
τ_R/MPa	6 113
m	10.1
弹性模量,E/MPa	2.1×10⁵
泊松比,ν	0.3

结构	滚子直径/mm	滚子长度/mm	滚子数量/个	节圆半径/mm	δ
主推滚子	120	120	104	2 134	0.1
径向滚子	50	88	220	2 268	0.07
止推滚子	70	72	156	2 198	0.075

参数	取值
轴向力/MN	12
径向力/kN	4 500
力矩/(MN·m)	20
转速/(r·min^-1)	2

参数	赫兹理论	有限元法	相对误差/%
主推接触应力/MPa	1 331	1 370.88	2.91
径向接触应力/MPa	1 170	1 186.55	1.39
止推接触应力/MPa	741.10	762.04	2.75

方法	寿命/h	变化率/%
本文寿命模型	26 287	-12.51
损伤力学模型	22 177	-26.19
文献[25]寿命模型	30 046	-