基于动态子结构的轴承动力学及摩擦学耦合分析

杨欣; 顾根香; 孙思聪; 周建明; 李赛力

doi:10.19693/j.issn.1673-3185.02265

基于动态子结构的轴承动力学及摩擦学耦合分析

doi: 10.19693/j.issn.1673-3185.02265

1.
上海船用柴油机研究所，上海 200090
2.
武汉理工大学能源与动力工程学院，湖北武汉 430063

基金项目: 国家部委基金资助项目

详细信息

作者简介:
杨欣，男，1986年生，博士生，工程师

通信作者:
杨欣

中图分类号: U664.21
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- 文章访问数: 218
- HTML全文浏览量: 91
- PDF下载量: 17
- 被引次数: 0
出版历程
- 收稿日期: 2021-01-14
- 修回日期: 2021-02-24
- 网络出版日期: 2021-11-20
- 刊出日期: 2021-12-20

Dynamic and tribological coupling analysis of journal bearing based on dynamic substructure

1.
Shanghai Marine Diesel Engine Research Institute, Shanghai 200090
2.
School of Energy and Power Engineering, Wuhan University of Technology, Wuhan 430063, China

基于动态子结构的轴承动力学及摩擦学耦合分析由杨欣，等创作，采用知识共享署名4.0国际许可协议进行许可。

摘要

摘要: 目的分析主轴承的动力学与摩擦学特性以及其相互耦合关系。方法首先，利用子结构法建立轴承磨损试验台耦合摩擦特性的动力学模型；然后，通过该动力学模型计算得到轴承摩擦耗功和轴心轨迹并与实测结果进行比较，验证模型的正确性；最后，在该模型的基础上进行主轴承摩擦学和动力学的耦合分析。结果结果显示，试验台的4个支撑轴承均处于液动润滑状态，被测轴承在上止点处于混合润滑状态；随着轴承间隙的增大，轴承试验台被测轴承最小油膜厚度先增大后减小，当间隙在20 μm左右时可以得到最佳润滑状态；相比非线性弹簧的油膜模型，采用EHD模型可得到精度更高的轴承载荷和摩擦功耗。结论研究结果可为轴承副的润滑性能设计和高精度建模提供理论指导。
- 滑动轴承 /
- 动力特性 /
- 子结构 /
- 摩擦学 /
- 耦合
Abstract: Objectives This paper studies the dynamic and tribological characteristics of the main journal bearing, and the coupling relationship between them. Methods First, a dynamic model of the coupling tribological properties of a bearing wear test bed is established using the substructure method. The friction power consumption and orbital paths of the bearing are then calculated and compared with the measured results to verify the accuracy of the model. Finally, based on the model, the dynamic and tribological coupling analyses of the bearing are carried out. Results The results show that the four support bearings of the test bed are in a state of hydrodynamic lubrication, while the tested bearing is in a state of mixed lubrication at the top dead center. With the increase in radial clearance, the minimum oil film thickness of the tested bearing increases first and then decreases, and the most optimal lubrication state can be obtained when the tested bearing clearance is about 20 μm. Compared with the oil film model of a nonlinear spring, the elastohydrodynamic model can provide bearing load and friction power consumption results with higher accuracy. Conclusions The results of this study can provide theoretical guidance for the lubrication performance design and high-precision modeling of bearing pairs.
- journal bearing /
- dynamic property /
- substructure /
- tribology /
- coupling

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图 1 EHD仿真计算流程图

Figure 1. Flow chart of EHD simulation

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图 2 轴承磨损试验台的三维结构

Figure 2. Three-dimensional structure of bearing wear test bed

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图 3 轴承磨损试验台动力学模型

Figure 3. Dynamic model of bearing wear test bed

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图 4 轴承磨损试验台动力学模型

Figure 4. Dynamic model of bearing wear test bed

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图 5 轴承磨损试验台计算结果验证

Figure 5. Verification of calculation results of bearing wear test bed

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图 6 各轴承油膜总压分布彩图

Figure 6. Oil film total pressure distribution of different bearing

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图 7 各轴承油膜粗糙接触压力分布彩图

Figure 7. Oil film asperity contact pressure distribution of different bearings

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图 8 润滑特性随间隙变化的趋势

Figure 8. Variation of lubrication characteristics with clearance

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图 9 一周期内摩擦功耗和载荷

Figure 9. Friction power consumption and load in one cycle

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图 10 2种建模方式下载荷频域力的对比

Figure 10. Comparison of load force between two modeling methods in frequency domain

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表 1 轴承磨损试验台主要参数

Table 1. Main parameters of bearing wear test bed

参数	数值	参数	数值
轴承宽度b/mm	29	油孔位置/(°)	45
轴颈直径/mm	52.68	油孔直径/mm	4
径向（半径）间隙c/μm	250	进油温度/℃	55
支撑轴瓦1（半径）间隙c₁/μm	50	进油压力/bar	9
支撑轴瓦2（半径）间隙c₂/μm	50	轴颈表面粗糙度/μm	0.4
润滑油牌号	10W-30	轴瓦表面粗糙度/μm	0.5

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表 2 主要零部件有限元模型与缩减模型

Table 2. Finite element model and condensed model of main parts

零部件	有限元模型	缩减模型
偏心轴
支撑轴承座
连杆

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表 3 偏心轴有限元模型与缩减模型模态对比

Table 3. Comparison of modal frequency between finite element models and condensed model of eccentric shaft

阶数	频率/Hz		误差/%	振型
阶数	有限元模型	缩减模型	误差/%	振型
1	1 708.5	1 710.5	0.117	YZ 面内弯曲模态
2	1 718.7	1 721.7	0.175	XZ 面内弯曲模态
3	4 021.6	4 020.4	−0.030	扭转模态
4	4 332.6	4 344.5	0.275	YZ 面内弯曲模态
5	4 360.8	4 362.9	0.048	XZ 面内弯曲模态

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表 4 连杆有限元模型与缩减模型模态对比

Table 4. Comparison of modal frequency between finite element model and condensed model of connecting rod

阶数	频率/Hz		误差/%	振型
阶数	有限元模型	缩减模型	误差/%	振型
1	963.5	963.23	−0.03	XZ 面内弯曲模态
2	1 213.6	1 212.4	−0.10	扭转模态
3	1 558.6	1 554.6	−0.26	YZ 面内弯曲模态
4	1 816.4	1 814.4	−0.11	小端局部模态
5	2 644.1	2 645.1	0.038	扭转模态

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表 5 轴承磨损试验台主要测试参数

Table 5. Main test parameters of bearing wear test bed

传感器	信号类型	被测对象
位移传感器	位移	轴心轨迹
扭矩仪	扭矩	摩擦功耗
温度传感器	温度	瓦背温度
压力传感器	压力	供油压力

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表 6 各轴承EHD润滑计算结果

Table 6. EHD calculation results of diffrent bearings of the test bed

轴承号	性能参数
轴承号	p_max/MPa	h_min/μm	λ	γ/%	W_m/W
1	2.87	20.87	32.61	0	241.74
2	16.51	8.07	12.61	0	318.92
3	106.78	1.38	2.03	1.42	486.89
4	16.49	8.07	12.61	0	319.03
5	2.68	20.89	32.64	0	248.67

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