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摘要:
为探究含油轴承基体渗流及压力扩散对接触面间油膜润滑性能的影响，建立双级孔含油轴承系统的渗流润滑模型，研究轴承摩擦面上油膜分布规律与双级孔隙中压力扩散行为，分析摩擦副倾角与轴承表层渗透率变化对油膜润滑性能的影响. 结果表明，流体动压力产生于摩擦界面的收敛区，并逐渐由摩擦界面向轴承基体扩散，在油压扩散过程中流体压力的作用面积增大，压力数值降低. 油膜的润滑性能随倾角增大或表层渗透率减小而得到改善，相比单层含油轴承，具有致密表层的双级孔含油轴承具有较好的润滑性能. 不同表层渗透率下，倾角对油膜摩擦系数的影响差异显著：在本文中计算参数下，当表层渗透率小于7×10−15 m2时，油膜的摩擦系数随倾角增大而减小；当表层渗透率高于7×10−15 m2时，油膜的摩擦系数随倾角增大而增大. 倾角和表层渗透率影响含油轴承基体中的油液渗流和压力扩散行为，最终使油膜的润滑性能发生改变. 研究工作为明晰含油轴承润滑机理提供一定理论依据.
Abstract:Oil bearing is usually prepared by powder metallurgy process, which has the characteristics of self-lubrication, lightweight and near net shape forming. It has significant technical advantages in the current situation of mechanical products pursuing high performance, low energy consumption and environmental friendliness. For exploring the influence of seepage and pressure diffusion on the oil film lubrication performance of oil bearing, the seepage lubrication model of two-stage hole oil bearing system was established. The oil film distribution on the friction surface and the pressure diffusion behavior in the two-stage hole were studied. The effects of the variable obliquity and surface permeability on the oil film lubrication performance were analyzed. The main purpose of the study was to reveal the interaction between fluid seepage and pressure diffusion in two-stage porous structure. Results showed that the hydrodynamic pressure was generated in the convergence zone of the friction face. From the friction face to the bottom of the bearing, the fluid pressure gradually diffused to the matrix, the pressure action area increased and the pressure value decreased during the oil pressure diffusion process. The lubrication performance of oil film became better with the increase of obliquity or the decrease of surface permeability. Reducing the surface permeability could decrease the seepage and diffusion effect of oil into the porous matrix in the oil film area, which was conducive to increasing the hydrodynamic pressure of oil film on the friction interface. The lubrication performance of two-stage oil bearing with dense surface was better than that of single-layer oil bearing. Under different surface permeability, the effect of obliquity on friction coefficient was significantly different. Under the calculation parameters in this paper, when the surface permeability was less than 7 ×10−15 m2, the friction coefficient decreased with the increase of obliquity. While when the surface permeability was higher than 7 ×10−15 m2, the friction coefficient increased with the increase of the obliquity. At lower surface permeability, the hydrodynamic pressure of oil film between friction interfaces increased with the increase of the obliquity. And the lubrication performance became better. At the same time, the seepage and pressure diffusion effects of oil film into the pores of bearing matrix were enhanced, which would hinder the improvement trend of the lubrication performance to a certain extent. When the surface permeability reached a certain value, the bearing capacity of the oil film hardly changed with the increase of the obliquity, and the friction coefficient of the oil film increased with the increase of the obliquity. Under different obliquity and surface permeability, the seepage behavior of oil in porous bearing interacted with pressure diffusion, and finally changed the lubrication performance of oil film. The research provided a theoretical basis for clarifying the lubrication mechanism of oil bearing.
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Keywords:
- two-stage hole /
- oil bearing /
- permeability /
- pressure diffusion /
- lubrication performance
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图 2 含油轴承渗流润滑模型的计算程序框图
Figure 2. Calculation program diagram of seepage lubrication model of oil bearing
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图 3 环面摩擦副系统中的油膜厚度与压力分布：(a)油膜厚度；(b)摩擦面上压力分布；(c)层间界面上压力分布；(d)轴承底面上压力分布
Figure 3. Oil film thickness and pressure distribution in toroidal friction pair system: (a) oil film thickness; (b) pressure distribution on friction face; (c) pressure distribution on interlayer face; (d) pressure distribution on bottom face
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图 4 倾角作用下三个层面上的无量纲压力分布：(a)摩擦界面上无量纲压力沿周向的分布；(a')摩擦界面上无量纲压力沿径向的分布；(b)层间界面上无量纲压力沿周向的分布；(b')层间界面上无量纲压力沿径向的分布；(c)轴承底面上无量纲压力沿周向的分布；(c')轴承底面上无量纲压力沿径向的分布
Figure 4. Dimensionless pressure distribution on three layers under obliquity: (a) distribution of dimensionless pressure along the circumferential direction on the friction interface; (a') radial distribution of dimensionless pressure on friction interface; (b) distribution of dimensionless pressure along the circumferential direction at the interlayer interface; (b') radial distribution of dimensionless pressure at interlayer interface; (c) distribution of dimensionless pressure along the circumferential direction on the bottom surface of bearing; (c') radial distribution of dimensionless pressure on the bottom surface of bearing
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图 5 两种渗透率下环面摩擦副系统的油膜承载能力和摩擦系数随倾角变化：(a) k1=1×10−14 m2, k2=1×10−13 m2；(b) k1=1×10−16 m2, k2=1×10−13 m2
Figure 5. Oil film carrying capacity and friction coefficient of ring friction pair system vary with inclination at two permeabilities: (a) k1=1×10−14 m2, k2=1×10−13 m2; (b) k1=1×10−16 m2, k2=1×10−13 m2
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图 6 表层渗透率作用下三个层面上的无量纲压力分布：(a)摩擦界面上无量纲压力沿周向的分布；(a')摩擦界面上无量纲压力沿径向的分布；(b)层间界面上无量纲压力沿周向的分布；(b')层间界面上无量纲压力沿径向的分布；(c)轴承底面上无量纲压力沿周向的分布；(c')轴承底面上无量纲压力沿径向的分布
Figure 6. Dimensionless pressure distribution at three levels under surface permeability: (a) distribution of dimensionless pressure along the circumferential direction on the friction interface; (a') radial distribution of dimensionless pressure on friction interface; (b) distribution of dimensionless pressure along the circumferential direction at the interlayer interface; (b') radial distribution of dimensionless pressure at interlayer interface; (c) distribution of dimensionless pressure along the circumferential direction on the bottom surface of bearing; (c') radial distribution of dimensionless pressure on the bottom surface of bearing
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图 7 层间界面及轴承底面上圆心部压力随渗透率的变化
Figure 7. Variation of pressure at the center of the circle on the interlayer interface and bearing bottom face with permeability
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图 8 不同表层渗透率作用油膜的承载能力和摩擦系数：(a)承载能力；(b)摩擦系数
Figure 8. Loading capacity and friction coefficient of oil film under different surface permeability: (a) load capacity; (b) friction coefficient
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图 9 不同倾角作用下环-面摩擦副间的法向渗析速度
Figure 9. Normal dialysis velocity between ring-face friction pairs at different inclination angles
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图 10 不同倾角作用下摩擦界面上的无量纲法向速度：(a)法向速度沿周向的分布；(b)法向速度沿径向的分布
Figure 10. Dimensionless normal velocity at friction face under different inclination angles: (a) circumferential distribution of normal velocity; (b) radial distribution of normal velocity
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图 11 不同表层渗透率作用下环-面摩擦副间的法向渗析速度
Figure 11. Normal dialysis rate between ring-surface friction pairs under different surface permeability
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图 12 表层渗透率作用下摩擦界面上的无量纲法向速度：(a)法向速度沿周向的分布；(b)法向速度沿径向的分布
Figure 12. Dimensionless normal velocity at friction interface under surface permeability: (a) circumferential distribution of normal velocity; (b) radial distribution of normal velocity
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