高压高剪切率下密封环缝隙流体动态润滑特性

张乐涛; 刘志奇; 李占龙; 徐彦; 高宇

doi:10.13700/j.bh.1001-5965.2020.0144

高压高剪切率下密封环缝隙流体动态润滑特性

doi: 10.13700/j.bh.1001-5965.2020.0144

太原科技大学机械工程学院, 太原 030024

基金项目:

国家自然科学基金 51975396

山西省自然科学基金 201701D121070

山西省科技重大专项国际合作项目 GJ2016-02-2

详细信息

通讯作者:
刘志奇, E-mail: liuzhiqi@tyust.edu.cn

中图分类号: TH322;TH137.51
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- 被引次数: 0
出版历程
- 收稿日期: 2020-04-16
- 录用日期: 2020-06-05
- 网络出版日期: 2021-06-20

Hydrodynamic lubrication characteristics of piston ring gap under high pressure and high shear rate

School of Mechanical Engineering, Taiyuan University of Science and Technology, Taiyuan 030024, China

Funds:

National Natural Science Foundation of China 51975396

Natural Science Foundation of Shanxi 201701D121070

International Cooperation Project of Science and Technology Major Program of Shanxi Province GJ2016-02-2

More Information

Corresponding author: LIU Zhiqi, E-mail: liuzhiqi@tyust.edu.cn

摘要

摘要:
为减少高压高剪切率下热效应对密封环缝隙流体润滑性能的影响，以密封环缝隙流体剪切速度梯度、壁面剪切应力和油膜温升表征摩擦副润滑性能，采用RNG k-ε湍流模型，通过Workbench建立流-固-热多场模型，计算得到不同主轴转角下缝隙流动形态变化规律和温升前后油膜厚度变化量、不同L型槽内外径比及长径比下流速流型分布规律、壁面剪切应力、温度分布和热变形量。研究结果表明：密封环L型槽黏性底层随剪切速度增大而增厚，油膜厚度随运动周期增加而变薄；当L型槽内外径比小于1.07时，随比值减小密封环壁面剪切应力不断增大，最大变化率为7%；密封环L型槽长径比在0.19时平均壁面剪切应力达到最大，当长径比继续增大时，油膜区剪切速度梯度逐渐减小，油膜温升和热变形亦随之减小。研究结果可为马达优化以减少能量损失和改善密封环润滑条件提供理论指导和依据。
- 高压高剪切率 /
- 剪切涡 /
- 密封环 /
- 热流体动态润滑 /
- 流-固-热多场耦合
Abstract:
In order to reduce the thermal effect on the lubrication performance of piston ring under high pressure and high shear rate, the friction pair lubrication performance is characterized by the shear velocity gradient, the wall shear stress and the oil film temperature rise. RNG k-ε turbulence model is used and the fluid-solid-thermal multi-physics model is established through Workbench to calculate the change rule of gap flow pattern, the film thickness change before and after temperature rise, the flow velocity and pattern distribution rule, wall shear stress, temperature distribution and thermal deformation under different L-shaped groove internal and external diameter ratio and length-to-diameter ratio. The results show that the L-groove viscous bottom layer thickens with the increase of shear speed, and the oil film thickness becomes thinner with the increase of motion period.When the ratio of the internal diameter to the external diameter of the L-groove is less than 1.07, the shear stress increases as the ratio decreases, and the maximum change rate is 7%.The average shear stress of the piston ring reaches the maximum when the length-to-diameter ratio is 0.19. If the ratio continues to increase, the oil film temperature rise and thermal deformation decrease as the velocity gradient decreases. The research results can provide theoretical guidance and basis for the optimization of motor to reduce energy loss and improve the lubrication condition of piston ring.
- high pressure and high shear rate /
- shear vortex /
- piston ring /
- thermo-hydrodynamic lubrication /
- fluid-solid-thermal multi-physics coupling

HTML全文

图 1 密封环缝隙结构简图与受力分析

Figure 1. Structure diagram and stress analysis of piston ring gap

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图 2 密封环复合运动形式

Figure 2. Compound movement form of piston ring

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图 3 密封环缝隙流体动力润滑

Figure 3. Hydrodynamic lubrication of piston ring gap

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图 4 密封环计算区域和局部网格分布

Figure 4. Calculation area and local grid distribution of piston ring

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图 5 多物理场耦合实现原理

Figure 5. Principle of multiple physical fields coupling

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图 6 仿真结果与理论计算结果对比

Figure 6. Comparison between simulation results and theoretical calculation results

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图 7 网格无关性验证

Figure 7. Grid independence verification

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图 8 不同主轴转角下油液流动形态

Figure 8. Oil flow pattern under different angles of principal axis

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图 9 初始时刻油膜厚度分布三维图

Figure 9. Three-dimensional distribution of oil film thickness at initial moment

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图 10 运动5个周期后油膜厚度的变化

Figure 10. Change of oil film thickness after 5 movement cycles

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图 11 不同内外径比和不同长径比下缝隙流体流速流线和温度分布云图

Figure 11. Velocity streamline and temperature distribution contour of flow in gap under different internal and external diameter ratios and different length-to-diameter ratios

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图 12 不同内外径比下密封环壁面剪切应力变化

Figure 12. Change of piston ring's wall shear stress under different intenal and external diameter ratios

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图 13 不同长径比下密封环壁面剪切应力变化

Figure 13. Change of piston ring's wall shear stress under different length-to-diameter ratios

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图 14 密封环在多物理场下的变形

Figure 14. Deformation of piston ring in multiple physical fields

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表 1 密封环参数设定

Table 1. Parameter setting of piston ring

参数	取值范围
L型槽长L/密封环宽度D	0.13~0.27
L型槽外径d₂/密封环内径d₁	1.03~1.08
密封环密度ρ_m/(kg·m^-3)	7 801
弹性模量E/MPa	2.07×10⁵
泊松比ε	0.29

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表 2 密封环工况条件

Table 2. Working condition of piston ring

环境参数	数值
初始缝隙高度δ₀/μm	10
工作压差Δ P/MPa	35
剪切速度v_x/(m·s^-1)	6
负载/(N·m)	889
进油温度T_i/℃	45
Fe热膨胀系数/℃	1.0×10^-5
初始润滑油黏度μ₀/(mm²·s^-1)	68

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表 3 不同长径比下密封环的变形量与润滑特性

Table 3. Deformation and lubrication characteristics of piston ring under different length-to-diameter ratio

L/D	三维模型	最大变形/μm	最大应力/MPa	最小油膜厚度/μm
0.13		2.62	159	0.8
0.16		2.69	164	0.75
0.19		2.76	169	0.70
0.22		2.71	165	0.73
0.25		2.65	159	0.76
0.27		2.59	154	0.79

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