基于混合润滑模型的往复密封动特性研究

为研究往复运动密封性能,采用MatLab数值方法建立一种混合润滑模型,该模型包含弹性力学、流体力学和接触力学分析。基于混合润滑模型,研究粗糙度和往复速度对动态往复密封摩擦力、泄漏量和油膜厚度等密封性能的影响规律,揭示液压往复密封机制。结果表明:往复运动密封圈处于混合润滑状态,接触区不仅有流体压力,还包含粗糙度接触压力;存在临界粗糙度σ_c和临界速度u_c,当粗糙度σ<σ_c时,随粗糙度的增大内行程的泄漏表现为越来越小的内泄漏,当σ≥σ_c时,随粗糙度的增大内行程的泄漏表现为越来越大的外泄漏;当速度uc时,净泄漏量随速度的增大表现为越来越小的外泄漏,当u≥u_c时,净泄漏量随速度的增大表现为越来越大的内泄漏;随着粗糙度的增加,膜厚与内行程的摩擦力增大,而外行程的摩擦力无明显变化;随着速度的增加,油膜厚度增加,内行程摩擦力减小,而外行程摩擦力变化很小。     

表面粗糙度对矩形动密封特性的影响

基于耦合了密封圈的弹性变形、流体动力分析和过盈接触的密封性能数值计算流程,利用Matlab 软件编程实现矩形动密封特性的数值计算,得到矩形密封圈的油膜厚度、泄漏量及摩擦力等密封性能参数,分析表面粗糙度对矩形密封圈的润滑状态和泄漏量的影响。结果表明：往复运动速度一定时,随着密封圈粗糙度的增加,密封偶合面的润滑状态由流体润滑转变为润滑润滑状态,密封的泄漏量也呈几何式增加,说明粗糙度对密封圈的工作寿命和密封性能有较大的影响;往复运动速度也是影响矩形密封圈密封性能的关键工作参数之一,密封压力一定时,随着粗糙度的增加,不发生泄漏的临界速度降低。     

润滑接触摩擦力的往复式实验研究

在往复式试验机上研究实际加工表面球-盘式接触混合润滑摩擦特性,比较采用不同黏度润滑油光滑接触摩擦力的大小。针对表面粗糙度幅值和纹理对摩擦行为的影响进行研究,结果表明,混合润滑时较高黏度润滑油的摩擦力较小;表面粗糙度幅值在混合润滑时对摩擦力影响较大,且随速度增加而增强,边界润滑时影响很小。与纵向纹理相比,横向纹理表面的摩擦力较小且稳定,低速时这种差别更加明显。     

往复式密封流变特性的分析与验证

为了提高往复式密封的密封性能,对密封区内杆-密封界面的流变特性进行分析.基于变形理论,通过引入混合润滑状态下弹性流体动压润滑数值模型,进一步揭示了往复式密封的密封机理.基于此理论模型同时考虑多耦合场的相互作用,通过引入流体方程(考虑空化现象)、微观接触模型以及变形模型,进一步分析了不同密封表面粗糙度、润滑油黏度以及密封...     

斜齿轮时变摩擦激励与啮合效率研究

基于斜齿轮时变接触线长度变化规律,推导了斜齿轮摩擦力和摩擦力矩的解析算法;基于时变摩擦因数模型,研究了滑动摩擦对齿面啮合力和啮合效率的影响。结果表明,考虑滑动摩擦时,齿面啮合力小于法向力,齿面啮合力随转速增大而增大,随齿面粗糙度和润滑油黏度增大而减小,且在多齿啮合区影响更显著;在时变摩擦因数作用下,平均啮合效率随转速、转矩增大而增大,随齿面粗糙度增大而降低,尤其在低温润滑油黏度较大时,影响较大。     

旋转轴唇形密封圈的建模与仿真研究

为了进一步研究唇形密封圈的密封机制,建立唇形密封的理论模型。基于流量因子分析轴向泵汲效应,建立泵汲流量方程;运用圆周平均雷诺方程描述密封界面流场,采用G-W模型近似描述唇轴粗糙峰互相接触下的接触力与径向变形;定量分析密封界面的周向摩擦力,并给出流体摩擦表达式;对以上各因素进行强耦合分析。结合船舶桨轴密封圈的实际应用工况及结构参数进行仿真计算,得出其方向角、膜厚、压力分布,并得到净流量随转速和粗糙度的变化关系。研究结果表明:净流量随转速增加而增加,但增速逐渐变缓;净流量随粗糙度近似呈线性增加,但高粗糙度会使泄漏量增大和导致表面更容易被磨损,因此实际唇口粗糙度的选取应综合考量多种因素。     

表面粗糙度对橡塑O形圈往复密封性能的影响

建立三维确定性混合润滑数值仿真模型,该模型采用统一Reynolds方程系统法,耦合了固体力学分析、流体力学分析和接触力学分析;生成非高斯粗糙表面,基于混合润滑模型研究表面粗糙度、自相关长度比值和纹理方向对橡塑O形圈往复密封摩擦力、泄漏率、平均膜厚和接触面积比等密封性能的影响规律。研究表明：低速时随着表面粗糙度的增大,润滑区接触面积比增大,引起摩擦因数增大,平均膜厚先增大后减小,临界接触面积比约为40%;在混合润滑状态时,对于横向纹理粗糙表面,存在合适的自相关长度比值使得密封的摩擦因数和接触面积比最低;当纹理方向θ=π/10时,摩擦因数最小。     

介质温升对流体静压型机械密封性能影响的研究

以抛物线型流体静压型机械端面密封(PHS-MS)为研究对象,建立了PHS-MS流体润滑理论模型,考虑流体液膜粘温压效应,采用有限差分法对广义Reynolds方程、能量方程、热传导方程组成的耦合数学模型进行了数值计算,获得了介质温升对PHS-MS密封性能影响规律。结果表明,介质温升使PHS-MS的端面开启力先增大后减小,泄漏率增大,而摩擦力减小,并随着时间推移各项密封性能参数趋向稳定;当介质温升较快时,开启力、泄漏率增大及摩擦力减小的趋势快,但密封性能参数达到的稳定值不变。     

三叉杆滑移式万向联轴器油膜刚度的分析

基于等温线接触弹流润滑理论,在考虑表面粗糙度的同时,建立三叉杆滑移式万向联轴器的油膜刚度计算模型,分析载荷、润滑油卷吸速度及黏度、表面粗糙度波长及幅值对润滑油膜刚度的影响。结果表明：润滑油膜刚度随着载荷及黏度的增大而增大,随着卷吸速度的增大而减小;相比较于载荷和卷吸速度,黏度对油膜刚度的影响相对较小。在远离接触区中心位置,油膜刚度变换幅度较小,在中心位置附近变换幅度最大。随着表面粗糙度波长与幅值的增大,油膜刚度呈非线性变化,且油膜刚度的振荡频率及幅度变小,油膜刚度的最大峰值靠近接触区中心。     

方向性微孔对润滑状态转化的影响

基于平均流量模型和微凸体接触模型,研究混合润滑状态下织构表面的摩擦特性,通过数值求解得到Stribeck曲线,分析法向载荷、润滑油黏度、表面粗糙度、方向因子和倾斜角对摩擦因数及名义摩擦副间隙等摩擦性能参数的影响规律。结果表明：混合润滑条件下,随着载荷的减小或润滑油黏度的增大,摩擦因数减小,名义摩擦副间隙增大,混合润滑转变为流体润滑时的临界转速降低;随着表面粗糙度的增大,摩擦因数和名义摩擦副间隙均增大,临界转速升高;随着倾斜角的减小或方向因子的增大,摩擦因数减小,名义摩擦副间隙增大,并且倾斜角越小,临界转速越低。     

Some Observations on Frictional Force During Fretting Fatigue

Frictional force behavior during fretting fatigue and its interdependence on other fretting variables are investigated. Both coefficient of static friction and the normalized frictional force (i.e., the ratio of frictional force and normal contact load) increase during the earlier part of a fretting fatigue test and then both reach to a stabilized value. The variation of temperature in the contact region and normalized frictional force with increasing cycle numbers and bulk stress show similar trend implying that normalized frictional force represents the average friction in the contact region during a fretting fatigue. An increase in bulk stress, relative slip, and hardness of pad material results in an increase of the normalized frictional force, while an increase in contact load, frequency and temperature decreases the normalized frictional force. The normalized frictional force is also affected by the contact geometry. On the other hand, coefficient of static friction increases with an increase in the hardness of mating material, temperature and roughness from shot-peening treatment, but is not affected by contact geometry and displacement rate. Further, the normalized frictional force is not affected by the contact geometry, roughness and applied bulk stress level when fretting fatigue test is conducted under slip controlled mode, however it increases with increasing applied relative slip and decreasing contact load in this case.     

Calculation of mixed lubrication at piston ring and cylinder liner interface

This paper reports on the theoretical analysis of mixed lubrication for the piston ring. The analytical model is presented by using the average flow and asperity contact model. The cyclic variations of the nominal minimum oil film thickness are obtained by numerical iterative method. The total friction is calculated by using the hydrodynamic and asperity contact theory. The effects of the roughness height, pattern, and engine speed on the nominal minimum film thickness, friction force, and frictional power losses are investigated. As the roughness height increases, the nominal oil film thickness and total friction force increase. Also, the effect of the surface roughness on the boundary friction is dominant at low engine speed and high asperity height. The longitudinal roughness pattern shows lower mean oil film pressure and thinner oil film thickness compared to the case of the isotropic and transverse roughness patterns.     

Solution and analysis of VL combined seal lubrication model under the effect of wear

Through the finite element calculation of VL combined seal models under different wear conditions, contact pressure distributions of models are obtained. Considering the coupling effect between seal deformation and lubricating oil film, a mathematical model of elastohydrodynamic lubrication for VL combined seal is established. Based on the theory of small deformation, the elastic deformation of VL composite seal under high pressure is obtained by the deformation influence coefficient matrix method. Considering the influence of sealing surface wear and surface roughness, the oil film thickness distribution and oil film pressure distribution of VL combined seal are solved by the finite difference method. The analysis results show the wear of VL combined seal, the decrease of viscosity, the increase of roughness and rotational speed can raise the thickness and pressure of lubricating oil film. The correctness of numerical simulation is verified by experimentally measuring the friction torque and leakage rate of seal.

     

表面粗糙度和润滑油黏度对活塞裙-缸套摩擦副润滑性能的影响

以一多缸内燃机为对象,研究表面粗糙度和润滑油黏度对活塞裙-缸套摩擦副润滑性能的影响。建立活塞二阶运动方程与平均Reynolds方程相结合的活塞裙-缸套摩擦副润滑分析模型。活塞二阶运动方程采用Broyden方法求解,应用有限差分法进行活塞裙-缸套摩擦副的润滑分析。结果表明,表面粗糙度对活塞裙-缸套摩擦副润滑性能影响不明显,而随润滑油黏度增加,活塞裙-缸套摩擦副的最小油膜厚度、摩擦力和摩擦功率增加,最大油膜压力在进气和排气行程随润滑油黏度变化比较明显,在其他行程变化较小。     

Tribological study on the surface modification of metal-on-polymer bioimplants

The tribological performance of artificial joints is regarded as the main factor of the lifespan of implanted prostheses. The relationship between surface roughness and coefficient of friction (COF) under dry and lubricated conditions is studied. Results show that under dry test, friction coefficient is not reduced all the time with a decrease in surface roughness. On the contrary, a threshold of roughness value is observed, and frictional force increases again below this value. This critical value lies between 40 and 100 nm in S_a (roughness). This phenomenon is due to the transfer of friction mechanisms from abrasion to adhesion. Under wet test, COF always decreases with reduction in surface roughness. This result is mainly attributed to the existence of a thin layer of lubricant film that prevents the intimate contact of two articulating surfaces, thus greatly alleviating adhesion friction. Furthermore, surface texturing technology is successful in improving the corresponding tribological performance by decreasing friction force and mitigating surface deterioration. The even-distribution mode of texturing patterns is most suitable for artificial joints. By obtaining the optimal surface roughness and applying texturing technology, the tribological performance of polymer-based bioimplants can be greatly enhanced.     

Role of nanometer roughness on the adhesion and friction of a rough polymer surface and a molecularly smooth mica surface

Friction and adhesion measurements between surfaces of cross-linked, stiff polymers of varying roughness against smooth, bare mica surfaces were carried out in dry air as well as in the presence of lubricating oil. The nominal (macroscopic) contact area varies with the applied load according to the Johnson, Kendall and Roberts (JKR) theory, yet shows significant hysteresis due to the irreversibility arising from the loading/unloading curves of multiple asperities. Upon introducing the oil between the surfaces, the critical shear stress is reduced to zero due to the elimination of the adhesion force. However, the effect is less noticeable on the friction coefficient. Lastly, the effect of increasing the (RMS) roughness was greatest over the first few nanometers due to the diminution of the adhesion-controlled contribution to the friction, after which a further increase in roughness had less dramatic effects. A model is presented to account for the observed adhesion hysteresis during repeated loading/unloading cycles of purely elastically deforming rough surfaces. Bruno Zappone and Kenneth J. Rosenberg made equal contributions.     

Possibility of slip in hydrodynamic oil films under sliding contact conditions

In hydrodynamic lubrication theory, the oil film thickness build‐up increases with increasing sliding speed or oil viscosity, and the viscous resistance or shear stress also increases, both without limit. The entraining force forming the oil film is given by the moving surfaces, or by the adhesive force of the oil molecules on the rubbing surfaces and the interaction force between them. Therefore, the maximum friction force and maximum oil film thickness will be limited by the operating conditions, such as oil properties, rubbing materials, sliding speed, and load. In this study, friction tests were conducted using a plate‐on‐cylinder sliding contact apparatus. It was found that a critical shear stress existed, above which the friction force and oil thickness decreased from theoretical values. Slip in an oil film seems to occur when the theoretical shear stress exceeds the critical value of the oil, according to test conditions. The occurrence of slip in an oil film is responsible for the reduction in the oil film and friction force from theoretical values, leading to the lower‐viscosity components of the oil selectively passing through the conjunction zone.     

Prediction of the frictional coefficient between a hard protuberance and a soft metal surface

Sliding contact is investigated between a soft metal surface (duralumin) and a hard protuberance ball (steel). The frictional coefficient in this case does not obey Amonton's law of friction, and it increases with an increase of normal load. The experimental value of the frictional coefficient agrees well with the calculated one. In the calculation, the variation of work-hardened depth corresponding to normal force is taken into consideration. It is confirmed that the normal force dependence of the frictional coefficient is generated from the contact pressure determined by the work-hardened depth corresponding to normal force, and from the ploughing effect.     

Combined effects of surface roughness and viscosity variation due to additives on long journal bearing

Abstract

The combined effects of surface roughness and viscosity variation due to additives on long journal bearing are analytically studied. The variation in viscosity along the film thickness is considered. The presence of solid particles in the lubricant is an increased effective viscosity, which increases the load carrying capacity and decreases the frictional coefficient, whereas the viscosity variation tends to decrease both the load carrying capacity and coefficient of friction for non-micropolar fluid case. The modified Reynolds type equation for surface roughness has been derived on the basis of Eringen’s micropolar fluid theory. The generalised stochastic random variable with non-zero mean, variance and skewness is assumed to mathematically model the surface roughness on the bearing surface. Numerical results were obtained for the fluid film pressure, load carrying capacity and the coefficient of friction. It is observed that the combined effect is to increase the load carrying capacity and to decrease the coefficient of friction, which improves the performance of the bearing.     

基于微凸体侧接触模型的机械密封端面混合摩擦热理论预测

基于微凸体侧接触模型,推导了机械密封端面混合摩擦热计算式,研究了转速、摩擦间隙和粗糙度对常用机械密封端面混合摩擦热的影响。结果表明：常用混合摩擦状态下的机械密封端面微凸体接触多为第Ⅱ类弹塑性接触;当转速ω ≤ 2 800 r/min时,微凸体接触摩擦热所占比重较大,但随着转速上升,黏性摩擦热比重逐渐增大至百分之百;随着摩擦间隙d的增大,黏性摩擦热和微凸体接触摩擦热曲线均呈下降趋势,当d ≥ 2.8σ时,微凸体接触摩擦热减小至零,而黏性摩擦热随d变化不大;随着粗糙度的增加,端面摩擦热先下降后上升,在近1.6 μm处最小,因而在机械密封设计时,存在某一粗糙度使混合摩擦热最少。