三点接触球轴承多点接触形成机制与临界条件界定

张屹立; 邱明; 周大威; 毕明龙

doi:10.13224/j.cnki.jasp.20250179

三点接触球轴承多点接触形成机制与临界条件界定

doi: 10.13224/j.cnki.jasp.20250179

张屹立^1,,
邱明^1,*, ,,
周大威²,
毕明龙²

1.
河南科技大学机电工程学院，河南洛阳，471003
2.
中国航发哈尔滨轴承有限公司，哈尔滨，150025

基金项目: 国家自然科学基金（52275186）；中原学者资助项目（项目号244000510001）

详细信息

作者简介:
张屹立（2001-），男，硕士，主要从事轴承设计及理论研究。E-mail：z2868333919@163.com

通讯作者:
邱明（1969-），女，教授，博士，主要从事轴承设计及理论研究。E-mail：qiuming@haust.edu.cn

中图分类号: V232；TH133.3
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- 文章访问数: 73
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- 被引次数: 0
出版历程
- 收稿日期: 2025-04-15
- 网络出版日期: 2026-08-28

Production mechanism and critical conditions definition of multi-point contact for three-point contact ball bearings

Zhang Yili^1
,,
Qiu Ming^{1,*
, ,},
Zhou Dawei²,
Bi Minglong²

1.
School of Mechatronics Engineering，Henan University of Science and Technology，Luoyang Henan 471003，China
2.
Harbin Bearing Company Limited，Aero Engine Corporation of China，Harbin 150025，China

摘要

摘要:
针对三点接触球轴承因钢球与沟道多点接触引发的失效问题，选取某型号三点接触球轴承为研究对象，运用动力学模型分析了结构参数与工况条件变化时钢球-沟道发生多点接触的形成机制，得到了钢球与副承载内圈接触点数量的变化规律。这些规律揭示：基础工况下，内圈沟曲率系数小于0.5058、或外圈沟曲率系数大于0.5134、或垫片厚度大于0.60 mm时，轴承发生多点接触；非基础工况下，载荷比大于等于0.35 时轴承脱离多点接触，高转速和大径向载荷需更高的载荷比以避免发生多点接触。另外，构建了多因素下多点接触状态临界条件的量化图谱，界定了不同垫片厚度下发生多点接触的内、外圈沟曲率系数临界值，以及不同径向载荷下发生多点接触的载荷比和转速临界值。该研究从设计和服役角度为避免三点接触球轴承发生多点接触与磨损失效提供了指导。
- 三点接触球轴承 /
- 多点接触 /
- 磨损失效 /
- 结构参数 /
- 工况参数 /
- 临界条件
Abstract:
To address the failure caused by multi-point contact between steel balls and raceways in three-point contact ball bearings, this study took a specific model of three-point contact ball bearing as the research object, and a dynamic model was adopted to analyze the production mechanisms of multi-point contact under variations in structural and operating parameters. And then change rule of the number of contact points between steel balls and the non-main loading inner-half ring (NMLIHR) was obtained. The results reveal that under the basic working conditions, multi-point contact occurs when the inner ring groove curvature coefficient drops below 0.5058 or the outer ring groove curvature coefficient rises above 0.5134, or the gasket thickness exceeds 0.60 mm. Under non-basic working conditions, the multi-point contact phenomenon can disappear when the load ratio is more than 0.35. Further, higher load ratios are required to prevent multi-point contact under conditions of elevated rotational speeds and large radial loads. In addition, the quantitative maps of critical conditions under multi-parameter influences were developed, which could determine the critical threshold values of inner and outer groove curvature coefficients corresponding to different gasket thicknesses, and the critical threshold values of load ratio and rotational speed corresponding to different radial loads. The research findings provide the guidance for avoiding multi-point contact and wear failure in three-point contact ball bearings from both design and service perspectives.
- three-point contact ball bearing /
- multi-point contact /
- wear failure /
- structural parameters /
- working condition parameters /
- critical conditions

HTML

图 1 三点接触球轴承钢球-沟道接触状态示意图

Figure 1. Schematic diagram of ball-raceway contact state in three-point contact ball bearing

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图 2 三点接触球轴承几何结构示意图

Figure 2. Schematic diagram of three-point contact ball bearing geometric structure

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图 3 打滑率随轴向载荷变化曲线

Figure 3. Variation curves of skidding rate with axial load

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图 4 不同内圈沟曲率系数下钢球-沟道接触应力分布（单位：MPa）

Figure 4. Ball-raceway contact stress distribution under varying inner ring groove curvature coefficients （unit: MPa）

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图 5 副承载内圈钢球-沟道接触点数量随内圈沟曲率系数变化曲线

Figure 5. Variation curves of ball-raceway contact points in NMLIHR with inner ring groove curvature coefficients

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图 6 不同外圈沟曲率系数下钢球-沟道接触应力分布（单位：MPa）

Figure 6. Ball-raceway contact stress distribution under varying outer ring groove curvature coefficients （unit: MPa）

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图 7 副承载内圈钢球-沟道接触点数量随外圈沟曲率系数变化曲线

Figure 7. Variation curves of ball-raceway contact points in NMLIHR with outer ring groove curvature coefficient

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图 8 不同垫片厚度下钢球-沟道接触应力分布（单位：MPa）

Figure 8. Ball-raceway contact stress distribution under varying gasket thickness （unit: MPa）

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图 9 副承载内圈钢球-沟道接触点数量随垫片厚度变化曲线

Figure 9. Variation curves of ball-raceway contact points in NMLIHR with gasket thickness

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图 10 内、外圈沟曲率系数与垫片厚度作用下副承载内圈钢球-沟道接触点数量

Figure 10. Number of ball-raceway contact points in NMLIHR under the influence of inner and outer ring groove curvature coefficient and gasket thickness

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图 11 垫片厚度对不发生多点接触的临界内、外圈沟曲率系数的影响

Figure 11. Influence of gasket thickness on critical inner and outer ring groove curvature coefficient for avoiding multi-point contact

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图 12 不同载荷比下钢球-沟道接触应力分布（单位：MPa）

Figure 12. Ball-raceway contact stress distribution under varying load ratios （unit：MPa）

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图 13 副承载内圈钢球-沟道接触点数量随载荷比变化曲线

Figure 13. Variation curves of number of ball-raceway contact points in NMLIHR with load ratio

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图 14 不同径向载荷下载荷比对副承载内圈钢球-沟道接触点数量的影响

Figure 14. Influence of load ratio on number of ball-raceway contact points in NMLIHR under different radial loads

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图 15 不同转速下载荷比对副承载内圈钢球-沟道接触点数量的影响

Figure 15. Influence of load ratio on number of ball-raceway contact points in NMLIHR under different rotational speeds

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图 16 转速、径向载荷和载荷比作用下副承载内圈钢球-沟道接触点数量

Figure 16. Number of ball-raceway contact points in NMLIHR under the influence of rotational speed, radial load and load ratio

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图 17 径向载荷对不发生多点接触的临界转速和载荷比的影响

Figure 17. Influence of radial load on critical rotational speed and load ratio for avoiding multi-point contact

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表 1 轴承结构参数

Table 1. Structural parameters of bearing

结构参数	参数数值
滚动体数量Z	19
轴承内径d/mm	130
轴承外径D/mm	200
轴承宽度B/mm	33
滚动体直径D_w/mm	22.225
节圆直径d_m/mm	165
初始接触角α⁰/（°）	30
垫片厚度h/mm	0.18
外圈沟曲率系数f_e	0.5129
内圈沟曲率系数f_i	0.5179

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