A hydrodynamic bearing includes an annular washer having an annular face configured to form a hydrodynamic thrust bearing. The annular face defines a plurality of circumferentially spaced oil grooves having opposing first and second lips extending between inner and outer diameters of the face. The annular face further defines a plurality of circumferentially spaced thrust segments alternating with the grooves such that each of the thrust segments is disposed between an associated pair of first and second ones of the grooves. Each of the thrust segments includes a land that is raised on the face relative to the first and second lips of the associated pair, a first ramp extending from the second lip of the first groove to a first side of the land, and a second ramp extending from the first lip of the second groove to a second side of the land.

The present invention relates to techniques for lowering friction between moving surfaces of, for example, an internal combustion engine. Friction reduction is achieved by adding texture modifications to surfaces that come in contact with each other. Texture modifications that reduce friction in accordance with the present invention include dimples of varying geometries and depths ion the surfaces of components. The present invention also relates to the fabrication technique for applying the texture to the surfaces. In another embodiment, the patterned soft mask is applied onto a large surface (flat or curved including cylindrical rollers surfaces) to be followed by electrochemical etching to imprint the textures onto the component And, in another embodiment, a diamond-like-carbon (DLC) film may be applied to the turbine component to also reduce friction.

A bearing comprising an axial channel formed along a longitudinal axis of the bearing having an inner radius comprising an inner surface and an outer radius comprising an outer surface and at least one dam region formed on the inner surface of the inner radius of the channel wherein the dam region comprises a modified crescent shape between 90 and 180 degrees about the longitudinal axis of the channel.

The disclosure relates to a turbocharger for an internal combustion engine, comprising a housing (2) with a compressor blade (3) on the air side, a shaft (1) driving the blade (3), and at least one radially acting rotary bearing (5) for mounting the shaft (1). The bearing (5) is designed as a hydrodynamic sliding bearing, and a stationary bearing element (6) is penetrated by the shaft (1) and a first mounting is formed on one first side of the bearing element (6) and acts axially against a bearing collar (7) rotating with the shaft (1). The bearing element (6) forms a second mounting on an opposite second side which acts axially against a sealing bushing (8) rotating with the shaft (1). An oil supply (9) is designed in the bearing element (6), a plurality of flow surfaces (10) is formed on one surface of the bearing element (6) facing the collar (7) in the axial direction, and an individually dimensioned throttle element (11, 12) is designed in the oil supply (9) for each of the two mountings.

The invention relates to a support of a bearing pad of a sliding bearing. Provided is a bearing pad support connection including a bearing pad and a bearing pad support, whereby the bearing pad is connected to the bearing pad support by a pivot joint. The pivot joint includes a pivot pocket, and a pivot. The pivot pocket includes a sealing that abuts on the pivot of the pivot joint.

A support part supports a bearing pad from an outer circumferential side so as to be swingable at a pivot position. A radius of curvature of a rotary shaft is Rj, a radius of curvature of a pad surface is Rp, and a radius of curvature of a reference circle centered at an axial line and having a radius equal to a distance between a center and the pivot position on the pad surface is Rb, and a relationship of Rj<Rp<Rb is established.

A lubricant supported electric motor includes a stator presenting an outer raceway and a rotor extending along an axis and rotatably disposed within the stator to present an inner raceway disposed in spaced relationship with said the raceway to define a gap therebetween. A lubricant is disposed in the gap for supporting the rotor within the stator. At least one of the outer raceway or the inner raceway are profiled with a non-circular, cross-sectional shape for maintaining consistent support of the rotor over a wide range of operating speeds and dynamic situations encountered by the lubricant supported electric motor during operation.

A shaft member for a fluid bearing device includes, on an outer peripheral surface thereof, two bearing surfaces (31 and 32) separated from each other in an axial direction, and a middle relief portion (33) formed between the bearing surfaces (31 and 32) and having a diameter smaller than a diameter of the bearing surfaces. The middle relief portion (33) includes a cylindrical surface portion (331) having a ground surface, and stepped portions (332) arranged on both axial sides of the cylindrical surface portion and having a diameter difference from the cylindrical surface portion.

A bearing bushing for a charging device may include an inner jacket surface including at least two radial depressions. A respective lowest point of the at least two radial depressions may be disposed on a circle having a radius R1. A plurality of plateau surfaces may be disposed circumferentially between the at least two radial depressions and may be offset radially towards an inside of the bearing bushing. The plateau surfaces may be curved and may have a constant radius R2. A ratio between the radius R1 and the radius R2 may correspond to the relationship: R1/R2=1.001 to 1.015.

In an exemplary embodiment, a sliding member includes sliding faces S configured to slide in relation to one another, at least one sliding face 5 of the sliding faces being provided with a plurality of dimples 11 having multi-sided shapes whose edges are formed without interruption. A pair of the edges A1-B1, A1-C1 of each of the multi-sided dimples 11, extending radially on opposite sides of a radial axis R of the sliding member, are sloped to become farther apart as they extend toward a high-pressure fluid side, and an edge B1-C1, which connects end points B1, C1 on the high-pressure fluid side of the pair of the edges, is formed such that its length is not greater than the lengths of the pair of the edges A1-B1, A1-C1. The sliding member can reduce friction between the sliding faces and improve sealing performance regardless of the direction of rotation.