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摘要: 理论研究表明不同润湿性界面对流体动压润滑油膜厚度有着显著地影响，一般采用接触角(CA)来表征固液界面润湿性. 而由热力学原理推导出的界面势能垒理论模型不仅与接触角相关，也是接触角滞后(CAH)的函数. 本文作者通过对不同基体材料的滑块进行表面张力修饰，获得了不同亲和性的界面. 利用干涉法及荧光法分别测量了不同润湿性界面的流体动压润滑膜厚及油膜受剪切的流动特性，研究了接触角及接触角滞后两个界面参数对流体动压润滑油膜厚度的影响，并对势能垒与接触角滞后的关系进行了讨论. 结果表明：接触角与流体动压润滑油膜厚度的相关性较差，接触角滞后可以更好地表征界面效应对流体动压润滑油膜厚度的影响.Abstract: Theoretical studies have proved that different solid-liquid affinity surfaces have significant effects on hydrodynamic lubrication film. In general, contact angle (CA) is used to characterize the wettability of solid-liquid interface. However a theoretical model derived based on thermodynamic principles shows that the potential energy barrier of a surface is not only a function of contact angle, but also of another interfacial parameter, contact angle hysteresis (CAH). By modifying the surface of the slider, different affinity interfaces were obtained. The lubricating film thickness and the continuity of flow velocity were measured by a fixed-inclined slider bearing system using optical interference method and fluorescence method respectively. This study thus evaluated the two, CA and CAH, by conducting thin film hydrodynamic lubrication experiments with surfaces of hydrophilic and hydrophobic. Fundamental relation between the potential energy barrier and CAH was discussed. The results show that the correlation between CA and hydrodynamic lubrication oil film thickness was unsatisfactory. But CAH can better characterize the influence of interface effect on the hydrodynamic lubrication film thickness.
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图 1 面接触润滑油膜干涉测量系统
Figure 1. Test system for interferometry measurement of film thickness in conformal contacts
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图 3 不同润湿性界面干涉图
Figure 3. Interferogram of different wettability interfaces (PEG400，Steel/FAS，w=4 N)
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图 6 油膜厚度与(a)接触角；(b)接触角滞后；(c)后退角；(d)cosθR-cosθA的关系
Figure 6. Correlation of film thickness and(a)contact angle;(b)contact angle hysteresis;(c)θR;(d)cosθR-cosθA
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图 8 PAO10相对于Steel块与FAS块、Steel块与AF块界面的荧光漂白过程及其流速示意图
Figure 8. Fluorescence photobleaching process and flow of a liquid under shear(h=1.5 μm，u=0.5 mm/s)
表 1 试验所用润滑油特性(@22℃)
Table 1 Properties of lubricants used in the test (@22℃)
Lubricant Dynamic viscosity，η/(mPa·s) Refractive index，N PEG200 59.7 1.46 PEG400 112.7 1.46 PEG600 160.5 1.47 PAO10 122.2 1.46 
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表 2 试验所用PEG润滑油在滑块表面的接触角及接触角滞后
Table 2 CA and CAH of the PEG lubricants on the slider surfaces
Slider Lubricant Contact
angle，CA/(°)Contact angle
hysteresis，CAH/(°)Steel PEG400 $50.3_{ - 2.3}^{ + 3.2}$ $28.9_{ - 6.3}^{ + 3.1}$ FAS PEG400 $95.3_{ - 2.1}^{ + 3.2}$ $13.5_{ - 4.4}^{ + 1.9}$ AF PEG400 $86.7_{ - 1.7}^{ + 0.8}$ $28.8_{ - 3.1}^{ + 2.8}$ SiO2 PEG400 $26.7_{ - 1.7}^{ + 3.8}$ $33.2_{ - 2.5}^{ + 1.7}$ SiO2+AF PEG400 $87.5_{ - 1.1}^{ + 1.4}$ $30.38_{ - 4.3}^{ + 4.1}$ Steel PEG200 $54.6_{ - 1.6}^{ + 1.4}$ $29.4_{ - 2.7}^{ + 2.3}$ FAS PEG200 $102.2_{ - 1.2}^{ + 0.8}$ $10.8_{ - 2.3}^{ + 3.2}$ Steel PEG600 $47.5_{ - 5.0}^{ + 5.0}$ $30.5_{ - 3.2}^{ + 2.1}$ FAS PEG600 $94.1_{ - 1.6}^{ + 1.9}$ $11.2_{ - 2.6}^{ + 2.1}$ FAS PAO10 $70.2_{ - 2.2}^{ + 3.3}$ $22.5_{ - 2.6}^{ + 2.7}$ AF PAO10 $57.6_{ - 5.0}^{ + 1.9}$ $27.5_{ - 2.2}^{ + 2.1}$
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