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为获得内燃机缸套-活塞环磨合磨损过程中微凸体的承载情况,利用粗糙峰的接触模型推导出磨合过程中微凸体承载方程,其中对弹性变形部分微凸体承载和塑性变形部分微凸体承载分别进行了研究,重点比较了内燃机缸套-活塞环磨合过程中假定接触微凸体全部为弹性变形与考虑接触微凸体产生弹、塑性变形时承载能力的不同.研究结果表明,在磨合磨损的中后期,即当h/σ大于0.5,ψ小于0.9时,两者差别不大,可以假定微凸体变形全部为弹性变形进行微凸体载荷的计算;而在磨合磨损初期,即当h/σ小于0.5,ψ大于0.9时,假定微凸体变形全部为弹性变形时的承载为考虑弹、塑性变形时的50%～85%左右.考虑到内燃机缸套-活塞环磨合过程中初期磨合的重要性,在计算缸套-活塞环磨合过程中微凸体承载时,应将塑性变形部分微凸体和弹性变形部分微凸体承载分别进行研究.也说明了本文所建立的微凸体承载方程更有益于缸套-活塞环磨合过程的摩擦学状态分析.
In order to obtain the bearing status of asperities during wear and tear of cylinder liner-piston ring in internal combustion engine, the bearing capacity of asperities in asperities was deduced by using the contact model of roughness peak. The bearing and plastic deformation of asperities Convex body bearing were studied respectively, focusing on the comparison of the bearing capacity of the contact asperities on the premise that all contact projections were elastically deformed and the contact asperities were generated and plastic deformed during the running-in process of the cylinder liner-piston ring of the internal combustion engine.The results show that, In the mid-and-late period of running-in wear, that is, when h / σ is greater than 0.5 and ψ is less than 0.9, the difference between the two is insignificant. It can be assumed that the asperities are all deformed elastically for the calculation of asperity load. That is, when h / σ is less than 0.5 and ψ is greater than 0.9, assuming that the deformation of the asperities is all elastic deformation, the bearing capacity is about 50% -85% when the elastic deformation and the plastic deformation are taken into account. Considering the running-in process of cylinder liner- The importance of early run-in in calculating the asperities bearing in the cylinder-piston ring run-in should be studied separately for the asperities of the plastic deformation and the asperities of the elastically deformable part. Tribological piston ring running state analysis - asperity carrier equation established more useful herein liner.