A sealing device for a bearing unit, the device having a stationary part provided with: a first metal shield, an elastomer coating, co-molded on the first shield, at least one contacting lip, radially internal, belonging to the elastomer coating. The sealing device having a rotatable part provided with a second metal shield on which the contacting lip makes a sliding contact. The second metal shield is provided with a plurality of flow baffles positioned at least on an axially exposed surface of the shield, shaped as recesses realized through the axially exposed surface and distributed along a radially outer peripheral edge of the shield.

A bearing including a sidewall including a substrate and a low friction material extending along at least one of a radially inner surface or a radially outer surface of the sidewall, the sidewall further including: a body defining a bore about a central axis; and a flange contiguous with and extending from an axial end of the body, where the flange includes a folded over outermost peripheral edge, where the substrate has a reduced thickness at the outermost peripheral edge, the flange being configured such that the substrate is not exposed along the outermost peripheral edge.

The invention relates to an imide polymer-based solid film lubricant, a method for producing same, a sliding element comprising same and the use thereof. According to the method, difunctional or cyclized difunctional compounds and optionally functional fillers are added to a non-imidized or partly imidized polyamide acid prepolymer or an imidized short-chain blocked prepolymer in a solvent or solvent mixture and then, depending on the prepolymer, a polymerization reaction or an imidization reaction and in both cases a crosslinking reaction is carried out. The solid film lubricant comprises an imide polymer as the resin matrix and optionally functional fillers, the molecules of the imide polymer comprising groups (R.sub.1) of the difunctional compounds that additionally contribute to the crosslinking.

A tapered roller bearing includes an inner ring having a tapered raceway surface and a large-collar surface on a large-diameter side of the raceway surface, and tapered rollers. Each of the rollers has a large end surface guided by the large-collar surface. When R represents a set curvature radius of the large end surface and R.sub.BASE represents a base curvature radius from a vertex of a cone angle of each of the tapered rollers to the large-collar surface, the base curvature radius R.sub.BASE is 100 mm or less, and a ratio R/R.sub.BASE of the set curvature radius R to the base curvature radius R.sub.BASE is set to 0.90 or less. When R.sub.ACTUAL represents an actual curvature radius of the large end surface of each of the tapered rollers, a ratio R.sub.ACTUAL/R of the actual curvature radius R.sub.ACTUAL to the set curvature radius R exceeds 0.5.

A rolling bearing is a tapered roller bearing, a cylindrical roller bearing, or a deep groove ball bearing including an inner ring, an outer ring, and a rolling element, each of the inner ring, the outer ring, and the rolling element being composed of a steel, the rolling bearing having a quench-hardened layer in at least one of an inner ring raceway surface of the inner ring, an outer ring raceway surface of the outer ring, and a rolling contact surface of the rolling element. A ratio of a total area of a plurality of martensite crystal grains in the quench-hardened layer is more than or equal to 70%. The plurality of martensite crystal grains are classified into a first group and a second group. An average grain size of the martensite crystal grains belonging to the first group is less than or equal to 0.97 μm.

An example bushing of a hydraulic hammer tool includes a bulk region and an inner region. The inner region has a relatively greater hardness than the bulk region. The inner region may also be compressively stressed, while the bulk region may have tensile stress. The stress and/or hardness profile of the bushing may enhance its resistance to wear and galling defects when a hammer of the hydraulic hammer tool is held in alignment by the bushing. The bulk region of the bushing may be relatively soft, resulting in the bushing having a relatively high level of toughness. The bushing may be formed using medium to high carbon steel by rough forming the bushing, hardening the bushing, tempering the bushing, induction hardening the inner region of the bushing, and then quenching the inner region.

The present invention provides a sliding member which enables further reduction of friction and improvement of seizure resistance without deteriorating wear resistance of a sliding surface. The sliding member includes a porous metal base material, and a resin material with which the porous metal base material is impregnated. The sliding member includes an exposed sliding surface. The sliding surface includes a top surface made of the resin material, and a bottom surface made of the porous metal base material. A height from the bottom surface to the top surface is 10 to 30 μm, and the resin material includes fluorine resin.

A wheel bearing assembly includes a wheel hub, at least one inner ring, an outer ring, and one or more rolling elements. An accommodation space may be formed inward of a vehicle-body-side end portion of the wheel hub to accommodate a constant velocity joint, and a plurality of recesses for accommodating rotating elements of the constant velocity joint are formed on an inner peripheral surface of the accommodation space to be spaced apart from each other along a circumferential direction. A first heat-treated hardened portion may be formed on the inner peripheral surface of the accommodation space, and may be formed to have portions with which the rotating elements of the constant velocity joint is brought into contact. A second heat-treated hardened portion may formed on an outer peripheral surface of the wheel hub. The first and second heat-treated hardened portions may not overlap each other.

A dynamic pressure bearing structure with double beveled edges is provided. The dynamic pressure bearing structure includes a bearing body, a shaft hole, and at least one oil guiding groove group. The shaft hole is disposed inside the bearing body and passes through two ends of the bearing body. The oil guiding groove group is arranged on an inner wall of the shaft hole. Two beveled edge portions are disposed on outer walls of the bearing body and forms an air escape structure. An outer diameter of the bearing body, an inner diameter of the shaft hole, and a height of the bearing body form an optimized size, with a thinnest position having a thickness being greater than or equal to 0.01 mm. The dynamic pressure bearing structure is manufactured using a metal cutting process or a powder metallurgy process.

Provided are sliding components capable of obtaining a stable low-friction effect under a wide range of conditions of use. A sliding component has a relatively sliding surface. A base material of one of the sliding components is coated with a graphite film, and the sliding surface of the other of the sliding components is made of the graphite film.