低速大偏心滑动轴承润滑状态转变及特性分析

以动压滑动轴承为研究对象,建立了完全流体润滑模型和混合润滑模型。采用有限差分法进行数值求解,得到摩擦阻力、摩擦因数、承载力和端泄油温升等特性参数;通过膜厚比和摩擦因数判断轴承所处润滑状态,分析润滑状态转变后表面粗糙度对轴承特性的影响;并基于M2000型摩擦磨损实验机进行了混合润滑状态摩擦副跑合实验。结果表明,低转速下增大偏心率,轴承润滑状态从完全流体润滑转变为混合润滑,且综合表面粗糙度越大,润滑状态转变所需偏心率越小;混合润滑状态粗糙峰接触可以提高承载力,但导致轴承摩擦阻力和端泄油温升迅速升高;大偏心下实验结果与混合润滑理论计算结果基本一致。     

多因素影响的格莱圈材料摩擦磨损试验研究*

格莱圈由聚四氟乙烯(PTFE)矩形滑环和丁腈橡胶(NBR)O形圈组成。为了研究不同因素对于格莱圈密封材料摩擦磨损性能的影响,利用UMT-3多功能摩擦磨损试验机,通过改变往复频率、粗糙度、润滑状态研究格莱圈材料与45钢配副时的摩擦磨损性能,利用SEM对试块试验前后表面形貌进行观测,并对摩擦磨损机制进行分析。试验结果表明:在干摩擦和滴油润滑条件下PTFE材料相比NBR材料具有更为优异的摩擦磨损性能;NBR材料表面粗糙度过高或过低都会导致摩擦因数升高,表面粗糙度对具有自润滑性能的PTFE材料的摩擦因数影响不大;高往复频率会使NBR材料摩擦因数降低,过高或过低的往复频率都会使PTFE材料摩擦因数降低;NBR材料的磨损形式以磨粒磨损和黏着磨损为主,PTFE材料以黏着磨损和疲劳磨损为主。     

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。     

正弦波粗糙度对织构表面动压润滑的影响

为研究动压润滑状态下粗糙度对织构的影响,建立正弦波粗糙度对织构化表面影响的动压润滑理论模型,并采用有限差分法对模型进行求解,分析正弦波粗糙度幅值、波长和分布方式对织构滑移表面油膜压力分布、承载力和摩擦因数的影响。数值计算结果表明:垂直分布粗糙度对表面综合性能的提高优于平行分布粗糙度,有利于提高表面的承载能力及降低摩擦因数;粗糙度波长及幅值对动压性能的影响则与织构深度和粗糙度的分布方式有很大关系。     

考虑表面粗糙度和热效应的线接触非牛顿混合润滑分析

为了研究表面粗糙度及热效应对非牛顿混合润滑的影响,基于平均流量模型,考虑表面粗糙度以及热效应,建立线接触非牛顿混合润滑模型。研究表面粗糙度对膜厚、膜厚比、平均摩擦因数、载荷比以及温度分布的影响,并与等温解进行比较。结果表明:随着表面粗糙度的增大,油膜温度逐渐升高,尤其是出口区与入口区的温升最为显著,且油膜温升越大,载荷比及平均摩擦因数越大,膜厚比越小;与等温解相比,热解的膜厚比及平均摩擦因数小,载荷比大;等温与热条件相比,中心膜厚与最小膜厚随表面粗糙度的变化趋势差异显著,说明热效应对混合润滑的影响不可忽略。     

双疏铝合金表面的水/油润滑摩擦学性能

利用激光加工在5083船用铝合金表面构建间距为100μm的点阵和网格微结构,将Si O2纳米粒子涂覆在微结构上构建微纳结构,制备出双疏铝合金表面。采用接触角测量仪测量其表面接触角和滚动角,采用多功能摩擦磨损试验机探讨其在水润滑和油润滑条件下的摩擦学性能。结果表明,网格表面的超疏水/疏油性能比点阵表面更强,水接触角达到159.9o,对十六烷的接触角达到147.0o。随表面疏水和疏油性能的提高,摩擦因数减小,磨痕深度变浅,宽度变窄。油润滑条件下的摩擦因数显著小于水润滑条件下的,且波动性更小,磨痕也更浅更窄。水润滑条件下,点阵表面的摩擦因数大于网格表面;而油润滑条件下,点阵表面的摩擦因数小于网格表面。     

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。     

轴颈表面粗糙度对橡胶材料干摩擦特性的影响

当船舶艉轴承供水系统出现故障或轴承过载时,金属轴颈与橡胶轴承之间会发生局部接触而处于干摩擦状态下。为研究金属轴颈表面粗糙度对水润滑橡胶轴承干摩擦特性的影响,采用TIME3230表面粗糙度测量仪对金属轴颈表面微凸体进行测量,得到金属轴颈表面微凸体的位置参数分布曲线,并对其进行去噪处理;利用傅立叶变换重新构造去噪后的金属轴颈表面粗糙度分布,并依据理论计算金属轴颈-橡胶轴承摩擦副的摩擦因数。金属轴颈-橡胶轴承摩擦副的摩擦因数计算结果与实际情况吻合,说明建立的轴颈表面粗糙度分布模型合理。分析结果表明:在干摩擦状态下,金属轴颈-橡胶轴承摩擦副的摩擦因数随着表面粗糙度函数波幅的增大呈线性增大趋势,随着粗糙度分布函数的特征波长系数的增大呈非线性增大;润滑流动方向顺着加工纹理方向时,摩擦因数比垂直加工纹理方向和与加工纹理呈45°时的摩擦因数都小。因此,选择合理的轴承表面粗糙度的幅值和波长可以提高金属轴颈-橡胶轴承摩擦副的摩擦润滑性能;沿加工纹理加工、装配金属轴颈-橡胶轴承摩擦副,可降低摩擦因数。     

润滑点接触粗糙表面滑动摩擦因数的实验研究

利用多功能微摩擦试验机,在轻载荷条件下测量了具有横向纹理圆盘表面的摩擦因数,得到了包括流体润滑、混合润滑和边界润滑完整的Stribeck曲线。考虑了载荷和时间对实验结果的影响,对不同粗糙度表面的Stribeck曲线进行了比较。实验的初步结果表明:增加载荷与实验时间,会获得更加稳定的实验结果;表面越粗糙,从混合润滑向流体润滑转换的临界速度越大;表面越光滑,Stribeck曲线的“谷底”越明显。     

船用二冲程柴油机十字头轴承润滑分析

根据动载滑动轴承弹流润滑相关理论,将有限元法与非线性多体动力学相结合,计入摩擦表面的粗糙度、轴瓦与轴颈的弹性变形、供油特性等因素,分析船用二冲程柴油机十字头轴承润滑状况。结果表明,在整个工作循环内,十字头轴承始终受压,承受压应力;轴承载荷的峰值出现在缸内气压最大的时刻;十字头轴承轴心的运动轨迹始终坐落于下半区域的较小范围内,高油压区域相对集中;轴承下瓦开设油槽,降低了承压能力,峰值油膜厚度较小;在轴承摩擦面的光洁度很高的情况下,粗糙接触压力较小且持续时间短,对轴承的正常工作影响不大;整个工作循环内绝大部分为液动摩擦,粗糙接触摩擦功耗相对较小。     

表面横向波形点接触弹流动压性能的研究

物体的表面结构形态在有些场合下对润滑状况有重要的影响作用.本文研究了考虑表面粗糙度的点接触问题的特点,建立了点接触的分析模型和接触物体表面的横向波形数学模型,应用多网格重积分方法求解了在给定条件下其与时间相关的弹流动压性能的解.主要分析了表面横向波形的点接触的润滑性能,揭示了油膜压力、油膜厚度在油膜接触区上随参数变化的特征和规律.     

Investigation of the strain distribution with lubrication during the deep drawing process

A lubrication/friction model can be implemented in FEM codes to predict the contact area ratio, friction coefficient and strain distribution in lubricated deep drawing process. In the lubrication analysis, the surface roughness effect on lubrication flow is included by using Wilson and Marsault's average Reynolds equation that is appropriated for mixed lubrication with severe asperity contact. With regard to the asperity contact theory, the well-known flattening effect is considered. Friction is expressed in terms of variables such as lubricant film thickness, sheet roughness, lubricant viscosity, interface pressure, sliding speed, and strain rate. The proposed lubrication/friction model combined with a finite element code of deep drawing process to predict the contact area ratio, friction coefficient and strain distribution. Numerical results showed that the present analysis provides a good agreement with the measured strain distributions.     

表面粗糙度对配流副润滑特性的影响

为研究表面粗糙度对轴向液压柱塞泵马达配流副润滑特性的影响,引入Weierstrass-Mandelbort分形函数,对不同幅值的表面粗糙度的表面形貌进行二维和三维模拟,建立考虑表面粗糙度的流固热耦合下的配流副油膜润滑模型,采用中差分形式的有限差分法和松弛迭代法对其进行数值求解,并分析油膜厚度、油膜压力、油膜承载力、摩擦因数等性能参数随着表面粗糙度幅值变化的规律。通过盘-盘形式的配流盘-缸体摩擦磨损试验,得到不同幅值的表面粗糙度下配流副摩擦因数,对所建立的数学模型进行验证。数值计算结果表明,表面粗糙度幅值的增大会引起油膜承载力增大,但也会引起最大油膜压力和摩擦因数的增大,导致摩擦性能下降。摩擦磨损试验发现,表面粗糙度增大,配流盘表面摩擦磨损情况加剧,配流副润滑性能和耐磨性能整体降低。因此在配流盘表面加工处理中,应适当降低其表面粗糙度。     

A multi-scale model for friction in cold rolling of aluminium alloy

A simple and robust friction model is proposed for cold metal rolling in the mixed lubrication regime, based on physical phenomena across two length scales. At the primary roughness scale, the evolution of asperity contact area is associated with the asperity flattening process and hydrodynamic entrainment between the roll and strip surfaces. The friction coefficient on the asperity contacts is related to a theoretical oil film thickness and secondary-scale roll surface roughness. The boundary friction coefficient at the “true” asperity contacts is associated with tribo-chemical reactions between fresh metal, metal oxide, boundary additives, the tool and any transfer layer on the tool. The asperity friction model is verified by strip drawing simulations under thin film lubrication conditions with a polished tool, taking the fitting parameter of the boundary lubrication friction factor on the true contact areas equal to 0.1. Predicted values of average friction coefficient, using a boundary friction factor in the range 0.07–0.1, are in good agreement with measurements from laboratory and industrial rolling mill trials.     

Enhanced friction model for high-speed right-angle gear dynamics

The modeling of elastohydrodynamic lubrication friction and the analysis of its dynamic effect on right-angle gears, such as hypoid and spiral bevel types are performed in the present study. Unlike the classically applied empirical constant coefficient of friction at the contacting tooth surfaces, the enhanced physics-based gear mesh friction model is both spatial and time-varying. The underlying formulation assumes mixed elastohydrodynamic lubrication (EHL) condition in which the division and load distribution between the full film and asperity contact zones are determined by the film thickness ratio and load sharing coefficient. In the proposed time-varying friction model, the calculation of friction coefficient is performed at each contact grid inside the instantaneous contact area that is being subjected to mineral oil lubrication. The effective friction coefficient and directional parameters synthesized from the net frictional and normal contact forces are then incorporated into a nonlinear time-varying right-angle gear dynamic model. Using this model, the effect of friction on the gear dynamic response due to the transmission error and mesh excitations is analyzed. Also, parametric studies are performed by varying torque, surface roughness and lubrication properties to understand the salient role of tooth sliding friction in gear dynamics. The simulation results are included. But experimental verification is needed.     

Measurements of friction in strip drawing under thin film lubrication

Strip drawing is used to investigate the friction behaviour under thin film lubrication in metal forming with plastic deformation. Friction coefficients are measured under a wide range of tribological conditions. The surface roughness is measured on an interferometric profilometer. The results show that the friction coefficient decreases with increasing oil film thickness h_w, as estimated using a formula appropriate for smooth tool and workpiece. Measurements of the surface topography show that change in friction is associated with a change in contact ratio between the tool and strip. The effect of strip reduction, strip roughness and die roughness on the friction coefficient is also investigated.     

Water Lubrication of Silicon Nitride in Sliding

Several studies have shown that the coefficient of friction of self-mated silicon nitride in water decreases from an initially high value to about 0.002 after a certain run-in period. Since the worn surfaces become extremely smooth, the low friction is attributed to the initiation of hydrodynamic lubrication by a thin water film at the interface. The possibility of mixed lubrication, i.e., hydrodynamic lubrication by water and boundary lubrication due to the presence of colloidal silica on the wearing surfaces, has also been proposed. The purpose of our study is to investigate the influence of load, speed, and surface roughness on the duration of the run-in period. The results confirmed that a low coefficient of friction is obtained following a run-in period when a wear scar of sufficient size is developed to reduce the contact stress. The run-in period, during which the coefficient of friction is fairly high, was shorter for smoother surfaces and at higher loads and speeds. The low friction behavior was found to be unstable and occasional high friction spikes were observed. The surfaces of the wear tracks and wear scars contained a series of striations parallel to the sliding direction and exhibiting plastic deformation, delamination and fracture. The striations that appeared to be associated with the high friction spikes, could form as a result surface film breakdown. Although these results are consistent with the proposed mechanisms of hydrodynamic lubrication or mixed lubrication, it is proposed that the low friction behavior may be also related to fundamental interactions between two hard and elastically deforming surfaces covered with hydrogen-terminated oxide films.     

Thermoelastohydrodynamic Analysis of Spur Gears with Consideration of Surface Roughness

Thermoelastohydrodynamic lubrication (TEHL) analysis for spur gears with consideration of surface roughness is presented. The model is based on Johnson’s load sharing concept where a portion of load is carried by fluid film and the rest by asperities. The solution algorithm consists of two parts. In the first part, the scaling factors and film thickness with consideration of thermal effect are determined. Then, simplified energy equation is solved to predict the surfaces and film temperature. Once the film temperature is known, the viscosity of the lubricant and therefore friction coefficient are calculated. The predicted results for the friction coefficient based on this algorithm are in agreement with published experimental data as well as those of EHL simulations for rough line contact. First point of contact is the point where the asperities carry a large portion of load and the lubricant has the highest temperature and the lowest thickness. Also, according to experimental investigations, the largest amount of wear in spur gears happens in the first point of contact. Effect of speed on film temperature and friction coefficient has been studied. As speed increases, more heat is generated and therefore film temperature will rise. Film temperature rise will result in reduction of lubricant viscosity and consequently decrease in friction coefficient. Surface roughness effect on friction coefficient is also studied. An increase in surface roughness will increase the asperities interaction and therefore friction coefficient will rise.     

考虑边界膜强度的滑动摩擦副混合润滑模型研究

针对边界膜对摩擦副润滑状态的影响，提出一种能够综合反映压力及剪切速率对边界膜失效综合影响的边界膜强度模型，并基于润滑状态测试结果通过拟合获得模型参数；将该边界膜强度模型与流体动压润滑模型、粗糙表面接触模型耦合，建立考虑边界膜强度的混合润滑模型，并通过轴瓦摩擦实验机润滑测试结果对模拟结果进行验证。和现有典型混合润滑模型相比较，该混合润滑模型可以更准确地反映摩擦副的实际润滑状态以及摩擦因数变化规律。运用考虑边界膜强度的混合润滑模型分析轴瓦零件润滑状态转化特性和机制。结果表明：在存在边界润滑的混合润滑条件下，当加载力小于临界载荷，边界膜几乎未发生破裂，摩擦因数随载荷增加缓慢变大，其数值均较小；当加载力加至临界载荷，边界膜破裂，摩擦副微凸体接触区域出现干摩擦，摩擦因数出现突然增加，表明该摩擦副由边界润滑为主的混合润滑状态过渡到以干摩擦为主的润滑状态。