压力相关的壁面滑移在滑动间隙流体动压力产生中的作用

近年来,壁面滑移在纳米流变学、微流体力学、薄模润滑和微机电系统(MEMS)等领域越来越引起关注。以前大部分研究集中于表面初始极限剪应力对薄模润滑的壁面滑移和流体动力学的影响。本文通过一个极限剪切应力比例系数主要研究了与压力相关的壁面滑移滑动间隙流体动压力产生中的作用,发现极限剪切应力比例系数以相反的两种方式影响着流体膜的流体动力学:在高初始剪应力区使流体动力增加,但在低初始剪应力区使流体动力减小,这意味着就极限剪切应力比例系数影响流体动压力而言,存在一个初始极限剪切应力的转换点。但是在界面滑移存在时,较小的极限剪切应力比例系数总是产生较小的摩擦阻力。     

滑滚表面间的流体膜壁面滑移和流体动力学

经典雷诺润滑理论建立在无壁面滑移的假设基础之上。近年来许多试验报告了发生在流体膜流动的壁面滑移证据。本文研究了两固体表面间的流体膜流动特性和流体动力学,发现壁面滑移显著影响膜的流体动力学问题,流体动压力不仅受黏度和几何间隙的影响,而且还由壁面滑移和表面运动强力控制,通过控制表面的吸附性质,甚至可以得到零摩擦表面。另一方面,如果两个表面具有相同的滑移特性,存在一个临界滑动速度使得流体动压效应完全消失;但是在纯滚动条件下,即使界面极限剪应力很小,仍然有相当可观的流体动压效应。     

粘塑性流体的界面滑移对润滑性能的影响研究

首先指出经典润滑理论中的边界无滑移条件已不再适用于具有极限剪应力的粘塑性流体润滑．而后,通过确定最大剪应力位置和加入剪应力边界条件,建立了界面滑移后的润滑方程．在联立求解不同区域的润滑方程基础上,对界面滑移的开始位置及扩展方式进行了分析．最后,讨论了不同膜厚比下滑移对润滑性能的影响．     

黏度对流固界面滑移影响的试验研究

为了研究微纳米间隙下固液界面间流体的流动及输运特性,本文改进了商用的原子力显微镜,并利用其对微纳米间隙下固液界面的边界滑移现象进行了试验研究,重点考察了流体黏度对边界滑移的影响.固体壁面样品采用Si(100)表面,试验液体采用不同黏度的去离子水和蔗糖溶液.结果表明,Si(100)表面与去离子水和蔗糖溶液作用会发生边界滑移,而且随着溶液黏度的升高,滑移长度也随之升高,表现了边界滑移与流体黏度的相关性.所得结果对于微流体输运与控制有重要的理论意义与实际价值.     

微纳米结构壁面对流场及动压润滑的影响研究

固体边界具有的微纳米结构将影响流体在近壁面处的流动行为,进而由于尺度效应改变流体在整个微间隙的流动或润滑规律.将壁面可渗透微纳米结构等效为多孔介质薄膜,采用Brinkman方程来描述流体在近壁面边界渗透层内的流动,并将其与自由流动区域的不可压缩流体Navier-Stokes控制方程耦合,在界面处的连续边界条件下求解和分析了速度分布规律和压力变化规律.针对恒定法向承载力的油膜润滑条件,进一步讨论了静止表面或运动表面的微纳米结构对近壁面流动行为的影响;并揭示了考虑壁面微纳米结构的流体动压润滑的油膜厚度和摩擦系数的变化规律.论文结果为具有可渗透微结构表面的微间隙流动与润滑提供了理论参考.     

冲击载荷下蛋白质水溶液吸附成膜的润滑试验研究

利用球盘接触形式的光干涉膜厚测量试验机,研究了周期冲击载荷作用下蛋白质水溶液在材料表面的吸附膜生长特性.对比了溶液蛋白质组分、亲疏水对偶表面和冲击条件对球盘接触区蛋白质吸附膜厚的影响.结果显示动态冲击下蛋白质的吸附膜厚要远高于静态吸附,吸附膜不断在接触区生长,之后趋于稳定.金属钢球比陶瓷球、疏水盘表面比亲水盘面,均更有利于蛋白质吸附膜的生长.同时发现吸附膜厚与单一蛋白质的浓度关系不大,却和蛋白质种类关系很大,球蛋白比白蛋白具有更好的吸附成膜性能.     

点接触润滑粗糙表面滑动摩擦力的预测研究

在整个润滑区域内基于统一Reynolds方程的混合润滑模型,根据流变模型计算流体摩擦力,根据边界膜极限剪应力模型计算微突体接触摩擦力,二者相加得到混合润滑摩擦力.分析了粗糙度幅值和纹理对摩擦系数的影响以及非牛顿流变模型对流体摩擦系数的影响.模拟跨越整个润滑区,即弹流润滑、混合润滑和边界润滑,得到完整的Stribeck曲线.结果表明,表面越粗糙,混合润滑的摩擦系数越大,弹流润滑和边界润滑时粗糙度幅值影响很小.交叉斜纹的润滑效果优于横向纹理.不同极限剪应力流变模型计算的摩擦系数相差不大.     

基于荧光漂白成像的润滑油膜剪切流速测量

沿润滑油膜厚度方向的剪切流速分布是影响机械部件润滑性能的重要因素.为此,搭建了基于荧光漂白成像的微间隙油膜剪切流速分布测量平台.通过对漂白区域形状演化过程进行图像分析,获得了微米量级间隙中的PB450和PAO6润滑油膜的剪切速度分布.结果表明:在设定测试条件下,厚度为8.5μm的PB450油膜沿膜厚方向的剪切流速近似为典型的线性分布,而相同厚度下的PAO6油膜流速分布表现为非线性塞流,界面附近油膜黏度较中层显著下降.研究还发现,同一滑动速度下,PAO6剪切流速偏离线性分布的程度随膜厚的降低而增加.经过比对分析,试验结果与流体动压润滑条件下的相关数据吻合.     

风沙粒子冲击钢结构涂层力学行为的理论与有限元分析

利用接触力学理论和三维有限元分析了钢结构受到风沙粒子冲击后其涂层表面接触区应力、涂层内部应力、涂层与基体界面上应力的分布规律。分析结果表明:涂层表面径向应力在接触中心出现最大压应力,在接触区边缘出现最大拉应力,且在接触区边缘易发生环状撕裂破坏;在涂层内部,涂层对Z向应力的承受力较好;涂层内部剪应力的最大值出现在碰撞接触点的左下方和右下方,这两个位置易受到剪切破坏,在接触点和剪应力最大值之间的剪应力变化速度较大;涂层与基体界面上r/h为0~0.4时,Z向应力变化较小;在r/h为0.4~1时,Z向应力剧烈减小;r/h1时,Z向应力基本保持不变;涂层与基体界面上剪应力最大值出现在冲击点附近,且冲击点附近剪应力变化较大,易引起剪切撕裂破坏。     

单个微油滴弹流润滑行为的试验研究

利用光干涉技术研究了微油滴通过弹流润滑接触区的润滑行为,考察了油滴大小、卷吸速度和载荷等因素的影响.结果表明微油滴在入口区域因挤压或毛细力效应发生表面积扩展,从而影响润滑膜的形成.油滴越大,挤压扩展直径越大,形成的膜厚越大.卷吸速度越高,入口处微油滴表面积扩展越不充分,仅接触区局部形成油膜,微油滴在接触表面挤压出凹坑穿过接触区.     

Boundary film shear elastic modulus effect in hydrodynamic contact. Part II: influence of operational parameters

The present paper is the subsequent research of the first part (Theor Comput Fluid Dyn, 2009). It investigates the boundary film shear elastic modulus effect in a hydrodynamic contact in different operating conditions. The hydrodynamic contact is one-dimensional, composed of two parallel plane surfaces, which are respectively rough rigid with rectangular micro projections in profile periodically distributed on the surface and ideally smooth rigid. The whole contact consists of cavitated area and hydrodynamic area. The hydrodynamic area consists of many micro Raleigh bearings which are discontinuously and periodically distributed in the contact. The hydrodynamic contact in a micro Raleigh bearing consists of boundary film area and fluid film area which, respectively, occur in the outlet and inlet zones. In boundary film area, the film slips at the upper contact surface due to the limited shear stress capacity of the film–contact interface, while the film does not slip at the lower contact surface due to the shear stress capacity of the film–contact interface large enough. In boundary film area, the viscosity, density, and shear elastic modulus of the film are varied across the film thickness due to the film–contact interactions, and their effective values are used in modeling which depends on the film thickness. In fluid film area, the film does not slip at either of the contact surfaces, and the shear elastic modulus of the film is neglected. It is found from the simulation results that the boundary film shear elastic modulus influences are normally negligible on the mass flow through the contact, the carried load of the contact and the overall film thickness of the contact, and the boundary film shear elastic modulus would normally influence the local film thickness in an elastic contact when the local film thickness is on the film molecule diameter scale. It is also found that the boundary film shear elastic modulus effect has the tendency of being increased with the reduction of the width of a micro contact. It is increased with the reduction of the boundary film–contact interfacial shear strength or with the increase of the critical boundary film thickness, while it is strongest at certain values of the contact surface roughness, the width ratio of fluid film area to boundary film area, and the lubricant film shear elastic modulus.

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Boundary film shear elastic modulus effect in hydrodynamic contact. Part I: theoretical analysis and typical solution

Boundary film shear elastic modulus effect is analyzed in a hydrodynamic contact. The contact is one-dimensional composed of two parallel plane surfaces, which are, respectively, rough rigid with rectangular micro projections in profile periodically distributed on the surface and ideally smooth rigid. The whole contact is consisted of cavitated area and hydrodynamic area. The hydrodynamic area consists of many micro Raleigh bearings which are discontinuously and periodically distributed in the contact. Analysis is thus carried out for a micro Raleigh bearing in this contact. The hydrodynamic contact in this micro Raleigh bearing consists of boundary film area and fluid film area which, respectively, occur in the outlet and inlet zones. In boundary film area, the film slips at the upper contact surface due to the limited shear stress capacity of the film–contact interface, while the film does not slip at the lower contact surface due to the shear stress capacity large enough at the film–contact interface. In boundary film area, the viscosity, density and shear elastic modulus of the film are varied across the film thickness due to the film–contact interactions, and their effective values are used in modeling, which depend on the film thickness. The analytical approach proposed by Zhang (J Mol Liq 128:60–64, 2006) and Zhang et al. (Int J Fluid Mech Res 30:542–557, 2003) is used for boundary film area. In fluid film area, the film does not slip at either of the contact surfaces, and the shear elastic modulus of the film is neglected. Conventional hydrodynamic analysis is used for fluid film area. The present paper presents the theoretical analysis and a typical solution. It is found that for the simulated case the boundary film shear elastic modulus effects on the mass flow through the contact, the overall film thickness of the contact and the carried load of the contact are negligible but the boundary film shear elastic modulus effect on the local film thickness of the contact may be significant when the boundary film thickness is on the 1 nm scale and the contact surfaces are elastic. In Part II will be presented detailed results showing boundary film shear elastic modulus effects in different operating conditions.

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Fretting contact of two elastic solids with graded coatings under torsion

In this paper, the fretting contact problem for two elastic solids with graded coatings is investigated. We assume a conventional axisymmetric Hertzian contact takes place between two elastic solids under the action of the normal pressure. The application of the torque produces an annulus of slip. It is assumed that the surface shear traction within the contact area is limited by Coulomb’s friction law and the torsion angel was produced within the central adhesion zone as a rigid body. The linear multi-layer model is used to model the functionally graded coating with arbitrarily varying shear modulus. This model divides the coating into a series of sub-layers with the elastic modulus varying linearly in each sub-layer and continuous on the sub-interfaces. By using the transfer matrix method and Hankel integral transform technique, this problem is formulated as the solution of the Cauchy singular integral equations. The contact tractions are calculated by solving the equations numerically. The results show that the appropriate gradual variation of the shear modulus can significantly alter the contact tractions. Therefore, graded coatings may have potential applications in improving the resistance to fretting contact damage at the contact surfaces.     

SQUEEZE FILM FLOW WITH NONLINEAR BOUNDARY SLIP

A nonlinear boundary slip model consisting of an initial slip length and a critical shear rate was used to study the nonlinear boundary slip of squeeze fluid film confined between two approaching spheres. It is found that the initial slip length controls the slip behavior at small shear rate, but the critical shear rate controls the boundary slip at high shear rate. The boundary slip at the squeeze fluid film of spherical surfaces is a strongly nonlinear function of the radius coordinate. At the center or far from the center of the squeeze film, the slip length equals the initial slip length due to the small shear rate. However, in the high shear rate regime the slip length increases very much. The hydrodynamic force of the spherical squeeze film decreases with increasing the initial slip length and decreasing the critical shear rate. The effect of initial slip length on the hydrodynamic force seems less than that of the critical shear rate. When the critical shear rate is very small the hydrodynamic force increases very slowly with a decrease in minimum film thickness. The theoretical predictions agree well with the experiment measurements.     

Boundary slippage for generating hydrodynamic load-carrying capacity

Boundary slippage is used to generate the load-carrying capacity of the hydrodynamic contact between two parallel plane surfaces. In the fluid inlet zone, the fluidcontact interfacial shear strength on a stationary surface is set at low to generate boundary slippage there, while in the fluid outlet zone the fluid-contact interfacial shear strength on the stationary surface is set at high enough to prevent the occurrence of boundary slippage. The fluid-contact interfacial shear strength on the entire moving surface is set at high enough to prevent boundary slippage on the moving surface. These hydrodynamic contact configurations are analyzed to generate the pronounced load-carrying capacity. The optimum ratio of the outlet zone width to the inlet zone width for the maximum load-carrying capacity of the whole contact is found to be 0.5.     

A Simplified Model for Calculating Hydrodynamic Lubrication Film Thickness in Elastoplastic Line Contacts

The present paper proposes a simplified model for calculating hydrodynamic lubrication film thickness in elastoplastic line contacts. According to the Saint-Venant’s principle, the pressure in the contact is taken as uniformly distributed, this gives the contact surface elastic deformations in the inlet zone far away from the contact center close to real ones while gives those close to the contact center greater than real ones. This treatment is validated for hydrodynamic lubricated elastic contacts for relatively light loads and high rolling speeds. It gives the film thickness at the contact center a little higher than that calculated based on the real elastic model. The treatment is extended to a hydrodynamic lubricated elastoplastic line contact. The contact surfaces in the inlet zone are assumed as elastic and their deformations are calculated based on the uniform pressure distribution in the elastoplastic contact area. An inlet zone analysis is taken for obtaining the calculating equation of the hydrodynamic film thickness at the contact center. The equation overestimates the central film thickness but gives a satisfactory film thickness prediction for the heavy load which gives significant plastic deformations in the elastoplastic contact. It is found that when the load is lighter than 0.6 w _pc , the contact can be taken as elastic when calculating the central film thickness, while when the load is heavier than 0.6 w _pc , the contact can be taken as fully plastic; Here w _pc is the critical load for the contact fully plastic deformation. The plastic deformation in an elastoplastic line contact is found to reduce the hydrodynamic lubrication film thickness in the contact. This reduction is greater for higher rolling speeds and heavier loads. However, it is significantly dropped with increasing surface hardness.     

表面特性对纯滑弹流油膜形状和摩擦力的影响的试验研究

针对界面滑移效应可能产生较低的摩擦力,采用具有不同表面浸润性的玻璃盘,进行了纯滑弹流润滑试验.在采用SiO2镀膜玻璃盘的球-盘接触高聚物纯滑润滑试验中,从弹流到动压润滑的摩擦系数曲线呈现不同于传统Stribeck曲线的两个拐点.两个拐点分别与凹陷出现及弹性变形消失相关联.在较低载荷下,不同盘表面产生相近的干涉图像和摩擦系数曲线,高聚物的非牛顿效应产生的表观滑移可能是入口凹陷及非典型摩擦系数曲线的主因;在较高载荷下,盘滑试验中铬盘产生的摩擦系数和油膜厚度均较SiO2盘低,具有较低表面能的铬盘产生的界面滑移被认为是产生较低摩擦系数的主因.     

Hydrodynamic lubrication in fully plastic asperity contacts

A line contact inlet zone analysis is carried out for the hydrodynamic lubrication in a fully plastic asperity contact. A governing equation of the central film thickness i.e. the film thickness in the fully plastic contact area is derived. An equation predicting this film thickness is also derived. It is found that for the fully plastic contact, under relatively light loads the prediction accuracy for the central film thickness is good, while at the load heavy enough the prediction equation greatly overestimates the central film thickness and the central film thickness solved from the analytical governing equation is significantly low showing the asperity in boundary layer lubrication. For the fully plastic contact, the central film thickness is nearly half of that obtained based on the elastic contact assumption for relatively light loads or even lower for heavier loads. The hydrodynamic lubrication is found difficult to form in the fully plastic asperity contact for the carried load heavy enough or the significantly low sliding speed between the asperities. To achieve a high hydrodynamic lubrication film thickness in the fully plastic asperity contact it is recommended to employ a high sliding speed or a high fluid viscosity. However, in the fully plastic asperity contact, the potential hydrodynamic load-carrying capacity is limited and much smaller than that based on the elastic contact assumption or predicted by conventional line contact elasto-hydrodynamic lubrication theory.     

Torsion of rough elastic half-space by rigid punch

Torsion of an elastic half-space by a rigid punch is investigated. The boundary of the half-space is assumed to be rough. Two geometries of the punch-parabolic and flat end are considered. It is shown that the contact area consists of stick and slip zones. This fact, which is well-known in the classical torsional contact of the elastic half-space with the smooth surface and the parabolic punch, also holds true for the flat-ended punch if the boundary roughness is involved. The partial slip problems are reduced to the integral equations, which are solved numerically. The presented results show the effects of boundary roughness on the shear stresses, size of the stick area and the relation between the twisting moment and the angle of twist.     

一般各向异性单侧接触界面上波的反射和折射

研究简谐弹性波在一般各向异性介质单侧接触界面上的反射和折射问题．利用Fouier分析方法将非线性Coulomb摩擦接触边界波动问题化为一组代数方程．给出了确定局部分离、滑移和粘着区的思路和方法及各区域的解；讨论了出现界面局部分离和滑移的条件．对特定材料组合情况进行了详细数值计算，给出了界面力、相对滑移速度、张开位移、高频谐波的反射折射系数等特征参量；考察了平面和反平面波动的耦合及整体滑移等．其中关于高频谐波的结果可对已有实验结果给出很好的定性解释．在大多数情况下，即使对摩擦系数无穷大的粘滞接触界面，分离区端部也总是存在一个很小的滑移区。