热力耦合作用的航空发动机主轴球轴承动力学分析

曹赛赛; 杨海生; 罗斌; 唐瑞; 邓四二

doi:10.13224/j.cnki.jasp.20220890

热力耦合作用的航空发动机主轴球轴承动力学分析

doi: 10.13224/j.cnki.jasp.20220890

曹赛赛^1,,
杨海生¹,
罗斌²,
唐瑞²,
邓四二^1,*, ,

1.
河南科技大学机电工程学院，河南洛阳 471003
2.
中国航发四川燃气涡轮研究院，成都 610500

基金项目: 国家自然科学基金（52005158）

详细信息

作者简介:
曹赛赛（1997-），男，硕士生，研究方向为滚动轴承设计及理论。E-mail：1416233809@qq.com

通讯作者:
邓四二（1963-），男，教授、博士生导师，博士，研究方向为滚动轴承设计及理论。E-mail：sedeng@haust.edu.cn

中图分类号: V233.4⁺5
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出版历程
- 收稿日期: 2022-11-20
- 网络出版日期: 2024-05-06

Dynamic analysis of aero-engine spindle ball bearings with thermal-mechanical coupling

CAO Saisai^1
,,
YANG Haisheng¹,
LUO Bin²,
TANG Rui²,
DENG Sier^{1,*
, ,}

1.
School of Mechatronics Engineering，Henan University of Science and Technology，Luoyang Henan 471003，China
2.
Sichuan Gas Turbine Establishment，Aero Engine Corporation of China，Chengdu 610500，China

摘要

摘要:
为更准确分析航空发动机轴承动态特性，基于滚动轴承动力学理论和传热学理论，建立了一种航空发动机主轴球轴承热力耦合的动力学模型。采用预估-校正的GSTIFF变步长积分算法求解动力学微分方程组，分析了轴承供油体积流量和供油温度对轴承温度及轴承动力学影响。研究结果表明：球轴承高速运行时轴承动力学特性受轴承生热影响较大；增大供油体积流量有助于降低轴承温度以及减小钢球与保持架之间碰撞力，但过大的供油体积流量会导致轴承保持架振动增大；供油温度主要影响轴承温度以及润滑油黏度，保持架与引导套圈间的作用力随着供油温度的升高而降低。当供油温度在120 ℃时轴承保持架振动最小。
- 热力耦合 /
- 角接触球轴承 /
- 热网格法 /
- 动力学 /
- 保持架碰撞力
Abstract:
In order to analyze the dynamic characteristics of aero-engine bearings more accurately, a thermal-mechanical coupling dynamic model of aero-engine spindle ball bearings was established based on the dynamic theory of rolling bearings and heat transfer theory. Then, the dynamic differential equations were solved using the GSTIFF variable step size integral algorithm, and the effects of bearing oil supply and temperature on bearing temperature and bearing dynamics were analyzed. The results showed that the dynamic characteristics of ball bearings were greatly affected by bearing heat generation when ball bearings were running at high speeds. When the oil supply increased, the bearing temperature and the collision force between the ball and the cage were reduced. However, too much oil supply could lead to an increase in bearing cage vibration. The oil supply temperature mainly affected the bearing temperature and lubricating oil viscosity. The acting force between the cage and the guide ring decreased with the increase of the oil supply temperature. The bearing cage vibration was minimal when the oil supply temperature was 120 ℃.
- thermal-mechanical coupling /
- angular contact ball bearing /
- thermal network /
- dynamics /
- cage collision force

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图 1 热力耦合作用的钢球与内外沟曲率中心的相对位置示意图

Figure 1. Schematic diagram of relative position of thermal-mechanical coupling steel ball and center of curvature of inner and outer groove

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图 2 轴承坐标系

Figure 2. Coordinate system of bearing

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图 3 钢球受力示意图

Figure 3. Schematic diagram of forces on steel ball

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图 4 热网格节点划分

Figure 4. Thermal network node division

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图 5 热平衡网格

Figure 5. Thermal balance network

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图 6 热力耦合流程图

Figure 6. Thermal-mechanical coupling flow chart

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图 7 转速对轴承温度的影响

Figure 7. Effect of rotational speed on bearing temperature

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图 8 考虑热力耦合转速对保持架打滑率的影响

Figure 8. Effect of considering thermal-mechanical coupling speed on cage sliprate

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图 9 考虑热力耦合对钢球与内圈接触处滑动速度的影响

Figure 9. Effect of considering thermal-mechanical coupling on sliding velocity of steel ball in contact with inner ring

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图 10 考虑热力耦合对轴承刚度的影响

Figure 10. Effect of considering thermal-mechanical coupling on bearing stiffness

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图 11 供油量对轴承内外圈温度的影响

Figure 11. Effect of oil supply on temperature of inner and outer rings of bearings

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图 12 供油量对油气混合物作用于单个钢球阻力的影响

Figure 12. Effect of oil supply on resistance of oil-gas mixture to individual steel ball

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图 13 保持架振动加速度级随供油量变化规律

Figure 13. Change law of cage vibration acceleration level with oil supply

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图 14 供油量对钢球与保持架碰撞力的影响

Figure 14. Effect of oil supply on collision force between steel ball and cage

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图 15 不同供油温度下摩擦功耗

Figure 15. Frictional power consumption at different oil supply temperatures

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图 16 供油温度对保持架与引导套圈间作用力的影响

Figure 16. Effect of oil supply temperature on force between cage and guide ring

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图 17 不同供油温度下内外圈温度

Figure 17. Inner and outer ring temperatures at different oil supply temperatures

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图 18 保持架振动加速度级随供油温度变化规律

Figure 18. Change law of cage vibration acceleration level with oil supply temperature

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图 19 不同供油温度对钢球与保持架碰撞力的影响

Figure 19. Effect of different oil supply temperature on collision force between steel ball and cage

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表 1 各节点名称

Table 1. Name of each node

节点	节点名称
1	滚动体
2	钢球与内滚道接触点
3	轴承内圈
4	轴
5	钢球与外滚道接触点
6	轴承外圈
7	轴承座
8	环境温度
a	入油口润滑油
a₁	轴承腔内润滑油
Q₁	外圈滚道处热源
Q₂	内圈滚道处热源

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表 2 轴承主要参数

Table 2. Main bearing parameters

参数	数值
轴承外径/mm	180
轴承内径/mm	100
钢球直径/mm	22.225
初始接触角/（°）	33
钢球个数	17

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表 3 试验轴承主要参数

Table 3. Main parameters of test bearings

参数	数值
轴承外径/mm	220
轴承内径/mm	150
钢球直径/mm	22.225
初始接触角/（°）	30
钢球个数	22

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表 4 试验工况

Table 4. Test conditions

工况序号	转速/ （r/min）	轴向力/N	径向力/N	供油温度/℃
1	10000	3300	1800	135
2	10000	3300	1800	155
3	14000	9800	2800	135
4	14000	9800	2800	165
5	16000	2900	3700	145
6	16000	2900	3700	165

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表 5 试验结果对比

Table 5. Comparison of test results

工况序号	试验结果/℃	仿真结果（1）/℃	仿真结果（2）/℃	误差（1）/ %	误差（2）/ %
1	141.46	156.52	160.13	10.65	13.19
2	173.98	175.16	181.49	0.68	4.3
3	154.89	174.32	179.43	12.54	15.84
4	182.98	199.81	208.94	9.20	14.18
5	179.85	178.57	184.59	0.71	2.64
6	186.58	192.93	202.89	3.40	8.74

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