固体润滑滑动材料

固体润滑滑动材料常州牵引电机厂石淼森固体润滑滑动材料，按其工作原理和制造方法可以分成两大类：背村型材料和镶嵌型材料。这些材料通常作为轴承、导套、导板及垫片，机床导轨面，冲压模具和挤出机模具机构等各种摩擦表面材料。一、背衬型材料将固体润滑剂覆盖在摩擦物...     

镀银膜轴承在油和脂润滑下的摩擦性能

试验研究镀银膜轴承在干摩擦、润滑油和润滑脂复合润滑下的摩擦性能。试验结果显示:在中低转速下,镀银膜轴承在银膜和液体润滑剂(油和脂)复合润滑下的摩擦因数仅相当于银膜干摩擦下摩擦因数的10%左右,且变化平稳;在高转速下,试验轴承在银膜和液体润滑剂复合润滑下的摩擦因数随转速增加而增加,且银膜与润滑脂复合润滑条件下的摩擦因数随转速增加得更快,但仍小于银膜干摩擦下的摩擦因数;镀银膜轴承在银膜和液体润滑剂(油和脂)的复合润滑下的磨损小于银膜干摩擦时的磨损;中低转速下,镀银膜轴承在液体润滑剂(油和脂)复合润滑下的摩擦磨损性能远优于银膜干摩擦时的摩擦磨损性能。     

球盘机构中边界吸附膜形成的研究

研究了润滑剂在45#碳素结构钢和聚四氟乙烯（PTFE）2种不同固体表面的润湿性能；在球一盘摩擦机构中，分别使用45#碳素结构钢和PTFE作为摩擦副进行试验，研究了4种不同类型系统中润滑和吸附特性。结果表明，2种润湿性能好的材料接触时，边界润滑性能最佳，而润湿性较好的球和润湿性较差的盘接触的润滑性能最差，盘的润湿性能对润滑系统更为重要，在一定范围内提高速度和载荷，可以提高润湿性较差材料的边界润滑性能。     

固体润滑的应用

润滑的目的在于降低摩擦和减少磨损.固体润滑的引入,突破了油膜润滑极限,在许多场合下,自润滑轴承以其自润滑功能,显示出巨大的优越性.镶嵌固体润滑轴承,就是其中的例子,它具有防污、防蚀、耐高温及低温性能好、长寿命等优点.     

WS_2复合润滑膜制备及轴承性能试验分析

为提高某高速电动机用转子轴承的自润滑性能,采用WS_2作为固体润滑材料,经工艺研究,制备了满足轴承使用要求的WS_2复合薄膜。通过对镀膜前后轴承的性能测试、试验以及与国外产品对比分析可知:采用WS_2复合薄膜后,轴承的摩擦力矩更小且更稳定,可直接在高速下运转,试验后轴承工作表面的固体润滑膜更加致密细腻;采用自润滑保持架与WS_2复合固体润滑膜相结合的润滑方案后,轴承的摩擦力矩与国外产品相比明显降低。     

耐高温复合固体润滑涂层的研究

常见的金属基固体润滑剂MoS 2、WS 2、Sb 2 O3性能优良,但作为单一涂层的局限性较大.将3种固体润滑剂复配成一种耐高温复合固体润滑涂层,通过正交试验得到优化的涂层配比,通过高温摩擦磨损试验考察该复合涂层的润滑性能.结果表明,在高温高压下该复合涂层具有较低的摩擦因数和良好的耐磨性能.电镜分析表明,高温高压摩擦磨损试验后,涂层试件表面仍然存在较均匀的固体润滑膜,可以起到很好的润滑作用.     

聚四氟乙烯基固体润滑剂摩擦表面的X-光光电子能谱研究

利用扫描电镜(SEM)对聚四氟乙烯基固体润滑剂摩擦表面及在45^#钢表面所形成的润滑转移膜形貌进行表征；采用X-光光电子能谱(XPS)仪测定了聚四氟乙烯基固体润滑剂烧结前后、在45^#钢表面摩擦试验前后，试样表面的元素组成及价态的变化。结果表明：摩擦过程中固体润滑剂在45^#钢表面形成了润滑转移膜，在烧结及摩擦过程中发生了化学反应，并产生磨粒磨损、腐蚀金属等现象。     

镶嵌固体润滑剂的硬质合金摩擦学性能研究

在硬质合金YT5表面利用微细电火花加工小孔,并装填MoS2固体润滑剂以改善基体表面的摩擦磨损性能.在UMT摩擦试验机上进行摩擦磨损试验,结果表明:装填固体润滑剂MoS2的微孔表面比光滑表面的摩擦系数显著降低,改善了摩擦表面磨损工况,表现出良好的减摩和润滑效果.结合SEM和EDX分析微孔固体润滑的机理:在摩擦过程中,存储于微孔中的固体润滑剂受到相对摩擦和挤压作用而粘着、拖覆在基体表面,形成一层固体润滑膜,从而起到减摩润滑作用.表面微孔润滑技术是提高基体表面摩擦磨损特性的有效方法,但需通过合理设计微孔结构尺寸,兼顾微孔表面的减摩润滑作用和基体的物理机械性能之间的平衡.     

激光微造型表面固体润滑性能研究

采用声光调Q二极管泵浦固体光源(DPSS)Nd:YAG激光器,在45#钢试样表面进行表面微造型加工。以聚酰亚胺(PI)和二硫化钼(MoS2)复合固体润滑材料作为固体润滑剂,通过两步加温固化黏结工艺成功制备微造型固体润滑试样。在MMW-1A型摩擦磨损试验机上进行光滑无润滑试样、光滑表面固体润滑试样和微造型固体润滑试样的摩擦性能对比试验,以及微造型固体润滑试样在不同转速和压力下的摩擦性能试验。结果表明,在经过激光加工的微凹坑中填充复合固体润滑材料的试样,在摩擦过程中微凹坑中填充的固体润滑材料能有效转移到在摩擦表面,补充消耗掉的润滑材料,因而表现出更好的摩擦学性能。     

第一讲 固体润滑技术概论

第一讲固体润滑技术概论常州牵引电机厂石淼森关键词团体润滑；润滑剂；摩擦磨损编者的话：为了让广大读者能较系统地了解“固体润滑技术”，我刊特开辟本讲座。该讲座共分六讲：一、概论；二、固体润滑膜的性能；三、固体润滑膜的制备；四、层状润滑材料；五、高分子和金...     

高速透平箔片动压气体轴承固体润滑涂层研究进展

箔片动压气体轴承广泛应用于高速透平膨胀机、微小型燃气轮机、涡轮增压机等高速透平机械中。固体润滑涂层可为箔片动压气体轴承提供启停阶段的润滑保护,对保证箔片动压气体轴承稳定性与使用寿命至关重要。本文回顾了国内外箔片动压气体轴承固体润滑涂层的研究历史与现状;结合文献资料着重分析了PS系列、Korolon系列和DLC系列的固体润滑涂层特性,并对其应用场合和优缺点进行了探讨。     

Influence of Particles on the Loading Capacity and the Temperature Rise of Water Film in Ultra-high Speed Hybrid Bearing

Ultra-high speed machining technology enables high efficiency, high precision and high integrity of machined surface. Previous researches of hybrid bearing rarely consider influences of solid particles...     

Zinc oxythiomolybdate (ZnMoO2S2) powder as a solid lubricant for high-temperature rolling contact applications

Conventional liquid lubricants being used in today's gas turbine engines will not be able to operate effectively in the hostile bearing environments expected in future turbine engines. The expected high operating temperatures (500–800°C) mandate new and innovative lubrication schemes to achieve success. Recent studies have demonstrated that a new class of solid lubricants, the complex chalcogenides or metal ocythiomolybdates, have good potential for high temperature lubrication. This paper describes the friction, wear and rolling contact endurance of three high-temperature bearing materials using a zinc oxythiomolybdate (ZnMoO₂S₂) powder lubricant. Rolling contact tests were conducted using VIM-VAR M50, micromelt T15 tool steels and silicon nitride (Si₃N₄) at temperatures ranging from 23°C to 649°C, using a modified ball-on-rod type rolling-contact fatigue tester. Significant improvements in friction, endurance and wear were observed at all test temperatures, and with all three materials evaluated, when ZnMoO₂S₂ was used as a lubricant. Overall, silicon nitride exhibited the best frictional and antiwear performance. The lubricant powder exhibited the best tribological performance with T15 and M50 specimens between 177°C and 316°C. Energy Dispersive X-Ray Analysis (EDAX) of wear tracks showed the presence of iron (Fe) on the Si₃N₄ specimens as well as the presence of zinc (Zn) on both the T15 and the M50 specimens.     

Test of a Fluid-Film Wave Bearing at 350°C with Liquid Lubricants

A novel fluid-film wave bearing has been run at a higher temperature (350°C) than ever before with a perfluoropolyether (PFPE)-K liquid lubricant. Additionally, the wave journal bearing (45 mm diameter and 24 mm long) completed an 8-h endurance test at the NASA Glenn Research Center. The lubricant was PFPE-K XHT 500. After being maintained at 350° C for 8 h, the bearing temperature was raised to 356°C for the last 30 min of the run. The speed was 29,000 rpm and the load ranged from 2670 to 3560 N. The bearing was perfectly stable both dynamically and thermally. The observed temperature was more than 150°C above that run with current turbine engine lubricants. The use of high-temperature bearings as tested here would allow efficiency increases of more than 5% in aero or terrestrial turbine engines.     

Calculation of six-lobe and eight-lobe deformable thrust sliding bearings

The paper deals with the development of a model and the calculation of characteristics of a hydrodynamic thrust sliding bearing which provides the compensation of the axial force in high-speed and low-speed rotors of stationary gas turbine units. In the framework of creating a method for determining the stiffness and damping characteristics of the bearing and calculating the parameters of lubricant flow in the gap, we develop a model of the thrust bearing based on the coupled solution of the problem of the flow of incompressible lubricant between the sliding surfaces and the problem of the deformation of the bearing parts and the shaft under the lubricant pressure. The model makes it possible to find the basic characteristics of the thrust sliding bearing at various relative displacements of the bearing and shaft. The bearing model is verified by comparing our results with the results of calculating lubricant flow in the STAR-CD software package and the results of calculations and experiments reported in the literature. The stiffness and damping characteristics are calculated for two thrust sliding bearings with six and eight lobes, depending on the sliding surfaces closure and variations in the shaft rotation angle with account of the deformation of the sliding surfaces. A significant influence of the shaft rotation angles in the bearing section and the deformations of the sliding surfaces on the integral characteristics of the bearing is demonstrated.     

Rolling Contact Testing of Vapor Phase Lubricants—Part II: System Performance Evaluation

The relative effects of several vapor lubrication parameters on bearing performance were examined using a ball-on-rod tester. Lubricants included in the evaluation were a tertiary-butylphenyl phosphate (TBPP), a 2 cSt polyalphaolefin blended with 15 percent TBPP (PAO+), the TBPP blended with 33 percent tributyl phosphate (TBPP+), a cyclophosphazine (X-1P), a polyphenylether (5P4E), and a perfluoroalkylether (Z). Parameters included in the study were bearing temperature, vapor concentration, and vapor temperature. Additionally, a solid lubricant coating was included to improve the bearing performance under cold-start conditions. The lubricants containing phosphorus demonstrated the best high temperature performance. The TBPP lubricant failed shortly after test at 650°C., while the X-1P lubricant performed satisfactorily over an eight-hour period at 650°C. The TBPP+ lubricant demonstrated the widest temperature range capability, with 600°C operation and a projected pump-ability point of–-45°C. Lubricant concentration was the most significant system parameter affecting bearing friction and wear.     

Geometric effects in high‐temperature vapour‐phase lubrication using hydrocarbon feed gases

The effectiveness of ‘far‐field’ vapour‐phase lubrication, in which areas of a bearing surface that are cycled through the contact are exposed to vapour while outside the contact, has been demonstrated in both sliding and combined roll slide tests using acetylene vapours to deposit pyrolytic graphite. Friction coefficients as low as μ = 0.008 have been measured for steel at 540°C with far‐field acetylene concentrations as low as 5%. Effective vapour‐phase lubrication depends on solid lubricant deposition that exceeds the contact's capacity to remove solid lubricant through wear. While the rate of removal is increased by increasing the sliding velocity, in far‐field vapour‐phase lubrication the rate of lubricant deposition, and therefore the lubrication effectiveness, is augmented by increased areas available for far‐field deposition, such as those provided by performing wear tests with increased wear‐track diameters. These geometric concepts may be considered in rolling‐element bearing and gear set applications where vapour‐phase lubrication is to be employed.     

Rolling Contact Fatigue Evaluation of Advanced Bearing Steels with and Without the Oil Anti-Wear Additive Tricresyl Phosphate

The effect of the oil anti-wear additive tricresyl phosphate (TCP) on rolling contact fatigue (RCF) life of advanced bearing steels—AISI VIMVAR M50, CSS 42L, Pyrowear 675, and Cronidur 30 was investigated with silicon nitride balls at 177 °C and at a maximum Hertzian stress of 5.5 GPa. TCP at 1% additive concentration was blended into a synthetic polyol ester turbine engine lubricant basestock having a nominal viscosity of 3 cSt at 100 °C. Additionally, the basestock was fortified with the anti-oxidants dioctyl-diphenyl amine (DODPA) and phenyl-α-napthyl amine (PANA) at 1% concentration each. The presence of TCP has a measurable positive effect on RCF life and wear. Also, all the advanced bearing materials exhibited superior fatigue life compared to conventional bearing steel M50, both with and without TCP. The study indicates that current gas turbine lubricant formulations with TCP have positive effects on fatigue life and wear performance of M50, Pyrowear 675, CSS 42L, and Cronidur 30.     

A Method to Calculate Frictional Effects in Oil-Lubricated Ball Bearings

Friction and heat generation in oil-lubricated ball bearings is mainly the result of sliding in the ball-raceway contacts and agitation of the lubricant in the free space between the balls, cage. and bearing rings. Endurance of a ball bearing is highly dependent on the thicknesses of the oil films which serve to separate the balls from the raceways in a well-lubricated bearing. The film thicknesses, in turn, are dependent upon the lubricant's viscous properties. These are functions of bearing temperatures and are determined by the balance between the rates of frictional heat generation and heat dissipation. Therefore, in the design of a ball bearing application such as the high speed rotor and low speed rotor support bearings in an aircraft gas turbine, it is important to be able to predict the bearing frictional heat generation rates with reasonable accuracy. This paper presents a method to perform the required calculations considering hearing loading and speeds, realistic lubricant rheological properties, and a relatively simple heat transfer system between the hearing rings, halls. And lubricant. The results of the analysis are shown to compare favorably with experimental data.     

Theoretical effects of solid particles on the lubrication of journal bearings considering cavitation

The theory of micropolar fluids, characterized by the presence of solid particles, is applied to the lubrication of an infinitely long journal bearing considering cavitation. The prominent feature of the presence of solid particles in the lubricant is an increased effective viscosity, especially in thin films. The effects of microstructure or solid particles are presented graphically. Tables are given to facilitate the comparison of the results obtained by using Reynolds' boundary conditions with those obtained by using half-Sommerfeld boundary conditions.