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• W789267613 abstract "This research work describes a method for the determination of the static friction factor in slide bearings. To determine tangential stresses distribution in a real area of a contact the author uses a molecular-mechanical theory of friction. In this theory, the total frictional force is equal to the sum of system of forces: molecular and material resistance to the deformation of bodies' surface coating. To design a model the following assumptions are accepted: a journal surface is rough, and a bushing surface is perfectly smooth. The results are represented in the form of graph which * Rzeszow University of Technology, Faculty of Mechanical Engineering and Aeronautics, al. Powstancow Warszawy 8, 35-959 Rzeszow, phone: (017) 8651640, fax: (017) 8651150, e-mail: almaz@prz.edu.pl. T R I B O L O G I A 6-2013 48 shows an influence of the contact angle of a journal surface and a bushing on a load, a frictional moment, tangential stresses, and a friction coefficient. REGISTER OF SYMBOLS Relating to properties of a bearing bushing material: E – Young's modulus [N/m], μ – Poisson's modulus, τ0 – shear resistance of adhesive bonds [N/m], β – molecular component of friction resistance, Relating to values of a bearing geometry: B – bearing bushing width [m], CR = RB1 – RJ – radial clearance [m], gB = RB2 – RB1 – bearing bushing thickness [m], RJ – journal radius [m], RB1 – inner radius of bush [m], RB2 – outer radius of bushing and [m], 2φ0 – contact angle on journal and bushing surfaces [rad], Relating to values describing the geometric structure of a journal surface: Ac – contour area (total) for a journal – bearing bushing contact, Ar – real friction surface, Ari – friction surface relating to single micro roughness [m], b – parameter of capacity profile curve, h – penetration depth of roughness peaks [m], k1 – constant dependent on capacity curve parameters, R – curvature radius of surface roughness peak [m], Rmax – maximum roughness profile height [μm], Rz – surface roughness height parameter [μm], tp – capacity profile function, α – coefficient which describes stress states in a static balance position in friction area: α = 0.5 – concerning elastic deformation, α = 1.0 – concerning elasticplastic deformation, ν – parameter of capacity profile curve, ∆ – roughness dimensionless coefficient, max R h h = e − relative depth, Other values: f – friction factor on bearing bushing surface, F – load [N], MT – frictional moment [Nm], αef – dissipation factor resulting from hysteresis deformation of micro roughness on bushing surface, σ – stresses on bushing surface [N/m], τT – resultant tangential stresses on bushing surface [N/m], τTm – tangential stresses arising from molecular interaction on solids boundary [N/m], τTd – tangential stresses in deformation area of micro roughness [N/m]. ASSUMPTIONS FOR A FRICTION MODEL CONSTRUCTION When a slide bearing starts operating (Fig. 1) the essential structural parameter that has an influence on this operation is a static friction coefficient [L. 1], [L. 5, 6], and [L. 9]. This research suggests a method that determines a static friction coefficient with the use of a molecular-mechanical theory of friction. The theory was developed by Kragelsky and discussed in these works [L. 3, 4]. The molecular–mechanical theory of friction accepts that friction 6-2013 T R I B O L O G I A 49 dissipation results from tangential stresses. Tangential stresses are examined on a real area of a contact where its geometrical structure is taken into consideration. The total frictional force is equal to the sum of system of forces: molecular and material resistance to deformation of bodies' surface coating. To characterize frictional forces in slide bearings at rest, the author accepts the following assumptions: – A deformation of a shaft surface coating is essentially small in comparison with a deformation of a bushing. – A frictional force and pressure are examined on the contact area between a journal and a bushing. (This area is called contour one.) – A real contact between a journal and a bushing is studied by means of micro roughness, assuming that the journal surface is rough and the bushing surface is perfectly smooth. – A deformation of a bearing bushing is examined as an elastic deformation. – Micro roughness of a surface is described by a profile capacity function. – A bearing journal is made of a very hard material while a bushing is made of an elastic-plastic material. – A bearing journal temperature does not have an influence on the materialphysical properties of a journal and a bearing bushing. EQUATIONS OF A MATHEMATICAL MODEL TO DETERMINE A FRICTIONAL MOMENT AND A STATIC FRICTION COEFFICIENT The above assumptions suggest that a friction force can be described as the sum of forces of a molecular interaction between the journal and bushing materials and forces dependent on the deformation of a body’s surface coating whose material hardness is low for example, a bushing. A resultant friction force can be written as an equation as follows: Td Tm T F + F = F (1) The friction force molecular component (FTm) is equal to a product of the real friction surface and tangential stresses that appear on this surface: Tm r Tm A F τ ⋅ = (2) The friction force component (FTd) depends on a material surface coating deformation in the bushing. This relationship is expressed by the following equation [L. 2, 5]: T R I B O L O G I A 6-2013 50" @default.
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• W789267613 date "2013-01-01" @default.
• W789267613 modified "2023-09-24" @default.
• W789267613 title "Method for determination of the static friction factor in slide bearings" @default.
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