计入油膜惯性作用椭圆接触弹流润滑性能研究

基于计入惯性项的Navier-Stokes方程和连续性方程,建立了计入油膜惯性作用的椭圆接触弹性流体润滑模型,研究了油膜惯性对椭圆接触弹流润滑性能的影响. 弹性变形通过快速傅里叶变换(FFT)计算,而油膜压力通过复合直接迭代法求解. 数值结果表明:在计入油膜惯性作用后,润滑膜的二次压力峰增大,入口区的油膜速度减小,且逆流区范围扩大;考虑油膜惯性作用后油膜厚度有所增大,当载荷从300 N增加到700 N时,中心膜厚最大增加了5.14%. 试验结果也表明,考虑油膜惯性作用后的中心膜厚数值解与试验结果更加接近.      

椭圆接触弹性流体动力润滑的供油条件分析

通过数值求解研究了椭圆接触弹流润滑的供油条件,分析了供油油膜厚度对乏油润滑中心膜厚和最小膜厚的影响,以及中心膜厚和最小膜厚与润滑油膜压力区形成位置的关系.结果表明:当供油油膜厚度较小时,中心膜厚和最小膜厚很小,压力区形成位置距Hertz接触区很近,处于严重乏油状态;当供油油膜的厚度达到一定数值时,中心膜厚和最小膜厚基本不变,多余的润滑油几乎不能进入接触间隙,即达到准充分供油状态;当供油油膜厚度继续增加时,乏油区最终消失,达到充分供油或过量供油状态.     

预紧方式对弹流润滑下角接触球轴承内部力学特性的影响

油膜厚度预测在评估弹流润滑(EHL)下角接触球轴承的性能和耐久性方面发挥着重要的作用. 耦合拟静力学理论和自旋下椭圆接触弹流模型,以干接触角接触球轴承拟静力学分析方法为基础,建立了定压和定位预紧方式下考虑弹流润滑和钢球自旋运动的角接触球轴承的拟静力学分析模型. 采用快速傅里叶变换(FFT)计算椭圆接触的弹性变形,运用Gauss-Seidel迭代方法求解Reynolds方程,得到自旋弹流模型的完全数值解,将其代入轴承拟静力学模型中迭代,得到轴承内部接触载荷、三维接触压力及三维膜厚分布. 对采用不同预紧方式的SKF7210型角接触球轴承进行分析,结果表明:富油润滑下,当轴承转速从0增大到15 000 r/min时,定压预紧时内圈轴向位移减小17.83%,而定位预紧时内圈承受的轴向载荷增大23.17%;定压预紧方式下球与内外滚道间膜厚均略大于定位预紧. 此外,不同预紧方式下,外圈上的中心膜厚大于内圈10%. 与干接触相比,定压下考虑弹流润滑内圈上接触载荷略大0.64%.      

牵引模式下球环点接触高速弹流润滑行为机理分析

基于球环点接触高速膜厚测量系统采用PAO6基础润滑油进行了高速弹流润滑试验研究,采用玻璃环转动带动钢球旋转的牵引方式,模拟轴承外圈与钢球的润滑接触状态.试验结果显示高速下试验测得的中心膜厚值严重偏离经典弹流理论的预测.基于高速热弹流润滑模型分析了高速下膜厚降低并偏离经典弹流理论预测的原因,计算结果表明钢球与玻璃环之间的运动不是纯滚动,存在滑滚比,并通过测量钢球转速加以验证;进而结合数值计算结果中接触区温度的变化,探讨了高速弹流润滑膜厚行为机理,高速时较大滑滚比的存在使得卷吸速度远低于纯滚动理论值是膜厚下降的主要原因,由此而产生的热效应使得润滑油黏度下降,膜厚进一步减小.     

两表面速度均为任意方向的非牛顿椭圆接触等温弹流润滑分析

提出了一种简单易行的方法用于进行两表面速度均为任意方向的等温点接触弹流润滑分析;建立了等温非牛顿椭圆接触弹流润滑的数学模型,综合考虑了两表面速度同向、反向及不共线且与椭圆短轴成一定角度的工况,并得到了两表面速度均为任意方向的等温数值解.结果表明:随着两表面速度方向的改变,合卷吸速度的方向不断变化,接触椭圆在计算域内的倾斜角度也随之改变;由于接触椭圆与坐标轴成一定角度,油膜的压力和膜厚不再与Y=0平面对称,Y=0平面内第二压力峰和油膜颈缩出现在出口区,而在X=0平面内第二压力峰和油膜颈缩出现在入口区.     

表面微织构对球盘点接触润滑摩擦性能的影响

基于统一Reynolds方程系统模型开展了富油点接触工况下微织构表面润滑摩擦性能的数值模拟研究.在通过实验标定数值模拟中润滑剂流变参数的基础上,系统分析了微织构表面摩擦系数周期变化的全过程,初步揭示了微织构的减摩机理.结果表明：数值模拟结果与实验结果有较好的吻合;瞬时摩擦系数达到最小值时,微坑单元一般处于名义Hertz接触区域的前边界;当微坑运动到Hertz接触区域内时,微坑前沿局部膜厚减小,而微坑后边沿膜厚局部增大,形成局部膜厚增大区;局部膜厚增大区的大小对微织构的润滑摩擦性能有较大影响,其面积越大,减摩效果越好.     

步态条件下人工膝关节线接触弹流润滑分析

参照关节模拟试验机的运动和力学参数,利用多重网格技术对人工膝关节摩擦副进行了1个步态周期仿人体环境线接触弹流润滑仿真,关节支承表面的弹性变形按半无限体计算.同时,观察了几种参数对流体压力分布和膜厚形状的影响.结果表明:在1个步态周期内,中心压力与载荷变化基本相同,且等效曲率半径的变化会引起中心压力的跳跃.站立相时在卷吸和挤压膜效应的共同作用下,中心膜厚呈逐步减小并伴随着波动;摆动相时,载荷固定,膜厚的变化主要与卷吸速度有关.减小胫骨平台曲率半径有助于提高滑液膜厚度;延长步态周期的时间,会使滑液膜厚减小.     

粗糙度纹理对有限长线接触混合润滑影响

采用统一Reynolds方程建立有限长线接触混合润滑模型,研究横向、纵向和二维规则表面粗糙度的波长、幅值及工况变化对润滑影响.结果表明:波长、幅值与工况对三种表面粗糙度接触副的润滑影响类似;随着载荷增大,平均膜厚降低,摩擦系数、接触载荷比与接触面积比均增大;随着转速升高,平均膜厚增大,摩擦系数、接触载荷比与面积比均降低,其中摩擦系数随转速进一步增大而小幅升高.在润滑状态转换区域润滑特征参数变化显著,而其他润滑区域变化平缓.沿卷吸速度方向的压力与膜厚波动分布存在相位差,垂直方向则同相位;相同的工况和粗糙度参数时,纵向粗糙度分布更有利于接触润滑.     

考虑热弹性变形的角接触球轴承微观热弹流分析

运用点接触热弹性流体动压润滑理论,考虑了润滑油膜温升变化引起的角接触球轴承中滚珠和内圈接触表面的热弹性变形和表面随机粗糙度的影响,提出了一种计入热弹性变形和随机粗糙度影响的角接触球轴承热弹性流体动压润滑分析方法.该方法通过将热弹性变形进行热力转换,得到了滚珠和内圈接触表面的材料线热膨胀系数,计算修正了滚珠和内圈表面因油膜温度场变化引起的热弹性变形,求得了计入热弹性变形和表面粗糙度后的油膜压力、油膜厚度、油膜温升以及热弹性变形等主要润滑特性,研究了内圈转速、滑滚比和滚珠数量的变化对油膜厚度和油膜压力的影响规律,结果表明:最大热弹性变形量与最小油膜厚度处在同一量级,并且内圈转速、滑滚比和滚珠数量的变化对油膜厚度和压力会产生明显的影响.进一步对比分析了几种算法下的最小膜厚,验证了计入热弹性变形的数值算法的可行性.     

边界膜剪切弹性模量对于微接触性能的影响

建立接触模型,理论分析了微接触中边界膜剪切弹性模量对于接触性能的影响. 接触区由两平行平面形成,属一维接触. 上接触表面为粗糙表面,具有矩形微凸体. 下接触表面为光滑平面. 两接触表面均处理成刚性表面. 微接触区中充满流体. 它分成两个子区,在微接触的出口区由于极小的接触间隙充满边界膜,在微接触的入口区由于接触间隙较大充满流体膜. 边界膜和流体膜行为决定整个微接触性能. 当膜厚较大时,这里边界膜可看成纳米级薄膜. 由于上接触表面处有限的剪应力承受能力,边界膜可于上接触表面滑移. 设下接触表面处剪应力承受能力很大而边界膜在下接触表面不滑移. 由于边界膜-接触表面间相互作用,边界膜黏度、密度和剪切弹性模量均沿膜厚变化,在理论分析中使用它们的等效值,这些值与边界膜厚度有关. 流体膜在两个接触表面均不发生滑移,分析中不考虑流体膜剪切弹性模量. 流体膜采用传统分析法. 给出了理论分析和若干变工况参数下的计算结果.      

高压微间隙下4010航空油的润滑特性研究

在自制的新型膜厚测量仪上,测量4010航空油在不同接触压力、温度和卷吸速度下的干涉图像,分析接触区的润滑特性。结果表明：在低温高速区主要表现为弹流润滑,中心膜厚与接触压力呈负相关;而在低温低速、高温区主要表现为薄膜润滑,中心膜厚受接触压力的影响较小。在弹流润滑区内高接触压力下油膜形状呈平坦状分布,而薄膜润滑区内油膜形状总体上比较平滑。随着载荷的增加,弹流润滑区内由Hamrock-Dowson理论算得的膜厚值和实测值逐渐偏离,理论公式中卷吸速度和载荷的指数需要调整;而薄膜润滑区的膜厚值基本上保持平稳。     

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.     

Indentation responses of piezoelectric films ideally bonded to an elastic substrate

The influences of elastic substrate on the indentation force, contact radius, electric potential and electric charge responses of piezoelectric film/substrate systems are investigated by the integral transform method. The film is assumed to be ideally bonded to the substrate and the contact interaction between the indenter and the film is assumed to be frictionless, with three kinds of axisymmetric insulating and conducting indenters (i.e., punch, cone and sphere) considered. Obtained results show that when the ratio of the contact radius to the film thickness is close to zero, the influences of the elastic substrate disappear and the indentation behaviors converge to the piezoelectric half space solutions while the indentation responses approach the corresponding ones of elastic half space as the ratio gets to infinity. The transition between the piezoelectric and the elastic half space indentation solutions for the film/substrate system is quantified in terms of the film thickness and the elasticity of the substrate. Finite element analysis on an insulating sphere indentation is conducted to verify the numerical calculations and good agreement is observed. The obtained results are believed to be useful for developing experimental techniques to extract the material properties of piezoelectric film/substrate systems.     

Cylindrical nano-indentation on metal film/elastic substrate system with discrete dislocation plasticity analysis: A simple model for nano-indentation size effect

The cylindrical nano-indentation on metal film/elastic substrate is computationally studied using two-dimensional discrete dislocation plasticity combined with the commercial software ANSYS®, with a focus on the storage volume for geometrically necessary dislocations (GNDs) inside the films and the nano-indentation size effect (NISE). Our calculations show that almost all GNDs are stored in a rectangular area determined by the film thickness and the actual contact width. The variations of indentation contact width with indentation depth for various film thicknesses and indenter radii are fitted by an exponential relation, and then the GND density underneath the indenter is estimated. Based on the Taylor dislocation model and Tabor formula, a simple model for the dependence of the nano-indentation hardness of the film/substrate system on the indentation depth, the indenter radius and the film thickness is established, showing a good agreement with the present numerical results.     

润滑状态下球-盘点接触摩擦副的低速轻载滑滚特性研究

选用镀Cr膜的玻璃盘和GCr15球作为摩擦副,在NGY-6纳米润滑膜测量仪上开展球-盘点接触摩擦副在润滑状态下的低速轻载滑滚特性试验,研究不同接触应力、钢球转速、滑滚比等参数对摩擦副的摩擦系数及对应油膜厚度的影响规律.结果表明:当接触应力和钢球转速一定时,摩擦系数随滑滚比的增大逐渐增加后达到稳定状态,当滑滚比较大时,滑滚比的变化对油膜厚度几乎没有影响;当滑滚比一定时,摩擦系数随接触应力的增大逐渐增大,随钢球转速的增大逐渐减小,油膜厚度随接触应力的增大逐渐减小,随钢球转速的增大逐渐增大.摩擦副在弹流润滑状态下,摩擦系数的增加幅度随接触应力的变化较小,而在薄膜润滑状态下,其增加幅度变大.摩擦副在薄膜润滑状态下,当滑滚比在0.10~0.50变化时,摩擦系数和油膜厚度基本处于稳定状态.     

齿向修形对滤波减速器润滑性能的影响分析

综合考虑了滤波减速器齿向修形参数、真实齿面粗糙度和瞬态效应等因素,建立了轮齿混合润滑数学模型,数值计算了不同修形参数值对应不同啮合点的最大压力和中心膜厚,分析了齿面粗糙度和转速对润滑性能的影响.结果表明:修形参数r和Ry均存在一个优化范围,使得轮齿表面最大油膜压力显著降低,边缘效应弱化,而中心膜厚则随着r和Ry的增大而逐渐增大;未修形轮齿边缘油膜压力受粗糙度的影响而急剧增大,边缘效应更加显著,修形后轮齿的边缘效应得到了明显改善,因此,轮齿修形也因粗糙表面的存在而显得更加重要;随着转速逐渐降低,轮齿表面的平均油膜厚度逐渐变小,接触比逐渐增大,轮齿表面由弹流润滑逐渐转为混合润滑,最后演变为边界润滑.     

On the numerical solution of some two-dimensional boundary-contact delocalization problems

The elastic equilibrium of a multi-layer confocal elliptic ring is studied. The ring consists of steel, rubber and celluloid layers which differ in thickness and in the order in which they are placed relative to one another. Using the solutions of the considered problems, the following delocalization problem is solved: for a three-layer elliptic body, the external elliptic boundary of which is loaded by normal point force and the internal boundary is stress-free and the layers of which are in rigid or sliding contact with one another, by an appropriate choice of layer thickness and arrangement of the layers relative to one another we can obtain a sufficiently uniform distribution of normal displacements on the internal elliptic boundary. Numerical solutions are obtained by the boundary element method and the related graphs are constructed. For the two-layer ellipse, exact and approximate solutions of the same problem are obtained respectively by the method of separation of variables and by the boundary element method. The results obtained by both methods are compared and the conclusion as to the reliability of the numerical boundary element method is made.     

Thickness of the film in an elastic hydrodynamic contact

A method is proposed for determining the thickness of the film in a heavily loaded elliptical elastic hydrodynamic contact. The method consists of integration of the Reynolds equation over the region occupied by the film, using the boundary differential equation for the integral of the reduced pressure. To determine the thickness of the film it is sufficient to know only the integral of the reduced pressure along the line of a constant gap. A new formula is obtained for the thickness of the film in an elliptical elastohydrodynamic contact, i.e., for the general case of a heavily loaded Hertzian contact in the presence of a lubricant.