A bearing arrangement for a turbomachine includes first and second roller element bearings. The first bearing and the second bearing are disposed on opposite axial ends of an intermediate sleeve of the rotating group. The first bearing has a first inner race with a first inner radial surface and a first outer radial surface. The first inner radial surface has a first interference fit with a shaft of the rotating group. The first outer radial surface has a second interference fit with the intermediate sleeve. The second bearing has a second inner race with a second inner radial surface and a second outer radial surface. The second inner race receives the shaft with a clearance fit. The second outer radial surface has a third interference fit with the intermediate sleeve. The second inner race is coaxially aligned with the first inner race and the shaft via coaxial alignment of the intermediate sleeve and the first inner race.

Electric motors are disclosed. The motors are preferably for use in an automated vehicle, although any one or more of a variety of motor uses are suitable. The motors include lift, turntable, and locomotion motors.

A dental hand piece or angle piece including a rotating tool, which is driven via a rotating drive element disposed in a housing, wherein the rotating drive element is mounted in the housing by a radial rolling bearing, wherein the rolling bearing comprises an axial abutment surface and the housing comprises an axial countersurface, and wherein the rolling bearing is axially preloaded with respect to the housing by a spring element 11 and has a coefficient of friction for the static friction of the abutment surface to the countersurface or the abutment surface and the countersurface to the spring element that is at least 0.16 in the lubricated state and at least 0.25 in the unlubricated state.

A bearing structure includes: a shaft provided with a turbine impeller; a pair of rolling bearings accommodated in a bearing hole and each including: an inner ring provided to the shaft; and an outer ring having a damper portion formed on an outer periphery of the outer ring; an opposing surface opposed to, from a turbine impeller side, a lateral surface of the outer ring of the rolling bearing provided on the turbine impeller side; and a first oil supply groove formed in the opposing surface and opposed to at least the damper portion and the lateral surface of the outer ring.

A load cell for determining a radial force acting on a crankshaft having a receiving sleeve for receiving a bearing ring and a fastening ring for attaching the load cell in a transmission housing. Axial support areas are provided on the fastening ring for axially supporting the outer ring of the first bearing. Moreover, measuring regions for receiving radial forces of the receiving sleeve are provided which connect the receiving sleeve with the fastening ring. Strain sensors are attached to at least two of the measuring regions.

An aircraft is described comprising: a support element; a shaft rotating about an axis; a pair of oblique rolling bearings mounted so as to couple the shaft to the support element (rotatingly about the axis; the rolling bearings comprising: respective first races cooperating radially in contact with a first component (defined by one from the support element and the shaft; respective second races cooperating radially in contact with a second component (defined by the other from the support element and the shaft; and respective pluralities of rolling elements adapted to roll on the first and second races; the aircraft further comprises a pair of preloaded elastic members, which couple the first races to the first component respectively, axially and in an elastically yielding manner.

A method and system for an axle assembly are provided. The axle assembly, in one example, includes a cover at least partially circumferentially surrounding a shaft, a bearing coupled to the shaft and the cover, the bearing including an outer race, and a bearing adjuster including a first axial side adjacent to the outer race and configured to set a bearing preload and/or end play. The assembly further includes a lubricant seal spaced axially away from the bearing adjuster and sealing a lubricant bore and the lubricant bore traverses the cover and extends axially toward the bearing adjuster.

In an angular ball bearing (10), an outer race (12) has at least one diameter-directional hole (15) that supplies lubricating oil and passes through from the outer circumferential surface to the inner circumferential surface along the diameter direction. In a cross-section taken along the axial direction passing through a center (O) of the ball (13), the axial-directional position of a line extending through a central axis (X) of the diameter-directional hole (15) in the outer circumferential surface of a retainer (14) is located between an intersection position (A), at which an outer circumferential surface (14a) of the retainer (14) and a surface of a ball (13) intersect, and an axial-directional end (B) of a pocket (P).

A transmission assembly includes a sun gear including an outer set of gear teeth, a planet carrier disposed around the sun gear, and a ring gear surrounding the planet carrier and the sun gear and including an inner set of gear teeth. At least one double planet is attached to the planet carrier. The double planet includes a first set of gear teeth and a second set of gear teeth, the outer set of gear teeth of the sun gear meshes with the first set of gear teeth, and the second set of gear teeth meshes with the inner set of gear teeth of the ring gear.

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.