A bearing includes an inner raceway and an outer raceway extending about a rotational axis. The outer raceway is spaced radially from the inner raceway such that an annular cavity is defined between the inner raceway and the outer raceway. The bearing also includes a plurality of first rollers disposed in the annular cavity. Each first roller of the plurality of first rollers includes a first end, a second end spaced axially from the first end, and a first surface extending between the first end and the second end. A first profile drop extends between the first end and the first surface. A second profile drop extends between the second end and the first surface. The second profile drop differs from the first profile drop. The bearing further includes a plurality of second rollers disposed in the annular cavity and spaced axially from the plurality of first rollers.

A roller bearing includes an inner ring having an inner-ring raceway surface on an outer periphery of the inner ring, an outer ring arranged concentric with and peripherally outside the inner ring, and having, on an inner periphery of the outer ring, an outer-ring raceway surface that faces the inner-ring raceway surface, a plurality of rollers interposed between the inner-ring raceway surface and the outer-ring raceway surface in a rollable manner, and a cage that holds the rollers at predetermined intervals along a circumferential direction. Opposite end portions of the outer-ring raceway surface in an axial direction serve as guide surfaces or which rotation of the cage is guided. Or an outer periphery of the cage, slidable contact surfaces are formed which slidably contact the guide surfaces and which are arranged to thee the respective guide surfaces across a labyrinth clearance.

Bearing 13 has lining layer 17 that is formed of an alloy having a predetermined shape and that has chamfered portion 25, and overlay layer 19 that is formed of a resin on an inner circumferential surface of lining layer 17, the inner circumferential surface sliding relative to a mating shaft, and that covers at least a portion of chamfered portion 25.

Embodiments of the invention relate to methods of fabricating leached polycrystalline diamond compacts (PDCs) in which a polycrystalline diamond table thereof is leached and resized to provide a leached region having a selected geometry. Creating a leached region having such a selected geometry may improve the performance of the PDC in various conditions, such as impact strength and/or thermal stability.

Vehicle input shafts are disclosed. The vehicle input shafts include a bearing boss, a spline portion, a cylindrical shaft body portion and a drive end. The spline portion includes spline teeth and spline grooves that do not exit directly onto the shaft body. Instead, the spline grooves include blend out fillets that interrupt the spline grooves by providing additional material near the shaft body. The bearing boss includes an increased diameter at a central point along its axial length and decreased diameters at its first and second boss ends.

An assembly that includes a rotating shaft supported with respect to a stationary housing by at least one active magnetic bearing presenting a mean radial air gap and at least one auxiliary bearing having a bushing fixed to the housing and a sleeve fixed on the rotating shaft. The bushing and the sleeve have opposite surfaces that define a clearance (E2) which is less than the mean radial air gap (E1). The bushing and the sleeve each exhibit symmetry around a longitudinal axis of the shaft and have different profiles in a longitudinal cross-section including the longitudinal axis to optimize the contact pressure distribution when the rotating shaft lands on the auxiliary bearing.

Gearbox (1) having a tooth carrier (40) for receiving teeth (7) of a gear ring that are disposed about a rotation axis (5) of the gearbox, wherein the teeth (7) are disposed in the tooth carrier (11) so as to be displaceable and guided in the radial direction, a cam disk (20) which is rotatable about the rotation axis (5) and for driving the teeth (7) in the radial direction has a cam curvature that is variable over the circumference, wherein bearing segments (24) which are mounted so as to slide on the cam disk (20) are disposed between the teeth (7) and the cam disk (20), and wherein the bearing segments (24) have a contact region which has a concave curvature and is disposed so as to be centric on a running surface that faces the cam disk (20), wherein the concave curvature is larger than the smallest cam curvature of the cam disk, and smaller than the largest cam curvature of the cam disk.

A bushing may include a support surface and a sliding surface having a perimeter midpoint. The sliding surface of the bushing may have a convex profile in relation to a cross section of the bushing. The convex profile may be offset from the perimeter midpoint of the sliding surface of the bushing.

A Planetary roller bearing having an outer ring with a tooth profile formed on the inner circumference by grooves, an inner ring with a tooth profile formed on the outer circumference by grooves, and a plurality of planetary rolling elements which are accommodated on the end side in cage disks and have a tooth profile formed by grooves. The tooth profiles of the planetary rolling elements engage in the tooth profiles of the rings, wherein a height, viewed axially, of at least one first tooth of the planetary rolling elements or of the outer or inner ring is less than that of the following second tooth, or that an axial distance (d1), viewed axially, of at least one first tooth to the following second tooth less than a distance of the second tooth to the third tooth.

A tapered roller bearing includes: an inner ring; an outer ring; a plurality of tapered rollers having a roller large end face that is a convex curved surface; and an annular cage that holds the tapered rollers at intervals along a circumferential direction. The inner ring includes a large rib portion having a rib surface that is a concave curved surface and that contacts the roller large end face. Inequalities represented by R>Ri>Rr are satisfied, where Rr is a curvature radius of the roller large end face, Ri is a curvature radius of the rib surface in a longitudinal cross section of the inner ring, and R is a distance from a cone center to a center of a contact ellipse obtained by contact between the roller large end face and the rib surface.