A thrust bearing is described comprising first and second bearing assemblies (15, 17) rotatable relative to each and a plurality of axially arranged bearing stages (14a, 14b) formed between the first and second bearing assemblies (15, 17). Each bearing stage comprises a first load shoulder (16) provided on the first bearing assembly (15), a second load shoulder (18) provided on the second bearing assembly (17), a bearing structure (30) defined between the first and second load shoulders; and an extrudable component (32) forming part of the bearing structure. Wherein axial load applied between the first and second bearing assemblies (15, 17) in a first relative axial direction is transmitted between respective pairs of first and second load shoulders via the extrudable components (32) of respective bearing structures (30). The extrudable components (30) provide for load balancing between each bearing stage (14a, 14b).

A self-aligning bearing support assembly for supporting a radial load rotary or linear bearing. The bearing support assembly has a main axis (A) and includes an outer sleeve and an inner sleeve at least partially received in the outer sleeve. The inner sleeve has an axially extending bore for supporting a rotary or linear bearing or for forming a bearing surface of a bearing. Three or more circumferentially separated chambers are formed between the inner sleeve and the outer sleeve. Each chamber is confined in all directions by walls of the assembly. A lump of a substantially incompressible material fills each of the at least three chambers with the chamber concerned substantially completely enclosing the lump.

A self-aligning bearing support assembly for supporting a radial load rotary or linear bearing. The bearing support assembly has a main axis (A) and includes an outer sleeve and an inner sleeve at least partially received in the outer sleeve. The inner sleeve has an axially extending bore for supporting a rotary or linear bearing or for forming a bearing surface of a bearing. Three or more circumferentially separated chambers are formed between the inner sleeve and the outer sleeve. Each chamber is confined in all directions by walls of the assembly. A lump of a substantially incompressible material fills each of the at least three chambers with the chamber concerned substantially completely enclosing the lump.

To reduce the effect of a steering operation on feeling. A rack bush comprises: a bush body that is accommodated in a cylindrical housing, supports a load exerted on a rack bar while allowing the rack bar to move in the direction of an axial center O, and can be extended and retracted in a radial direction; and an elastic ring mounted on the bush body. The bush body has a mounting groove for mounting the elastic ring, the mounting groove being formed peripherally in an outer peripheral surface, and the mounting groove having a large-diameter part where the circumferential radius of a groove bottom is a first radius r1, and a small-diameter part where said radius is a second radius r2 that is less than the first radius r1. This configuration allows the formation of an elastic ring protruding part, in which the elastic ring protrudes greatly from the outer peripheral surface of the bush body, and an elastic ring embedded part, in which the elastic ring is embedded in the outer peripheral surface of the bush body.

To reduce the effect of a steering operation on feeling. A rack bush comprises: a bush body that is accommodated in a cylindrical housing, supports a load exerted on a rack bar while allowing the rack bar to move in the direction of an axial center O, and can be extended and retracted in a radial direction; and an elastic ring mounted on the bush body. The bush body has a mounting groove for mounting the elastic ring, the mounting groove being formed peripherally in an outer peripheral surface, and the mounting groove having a large-diameter part where the circumferential radius of a groove bottom is a first radius r1, and a small-diameter part where said radius is a second radius r2 that is less than the first radius r1. This configuration allows the formation of an elastic ring protruding part, in which the elastic ring protrudes greatly from the outer peripheral surface of the bush body, and an elastic ring embedded part, in which the elastic ring is embedded in the outer peripheral surface of the bush body.

A spherical plain bearing includes an outer ring having a concave interior spherical surface, and an inner member having a convex exterior spherical surface. The inner member is pivotally disposed in the outer ring such that the inner member and the outer ring are angularly misalignable relative to one another. The spherical plain bearing includes an angular misalignment restraint system which includes an inner member restraint feature on the inner member and an outer ring restraint feature on the outer member. The first and second portions are spaced apart when the inner member and the outer ring are angularly misaligned relative to one another by less than a predetermined maximum angle θ, and come into abutment when the inner member and the outer ring are angularly misaligned relative to one another by angle θ. The abutment prevents any further relative angular misalignment of the inner member and the outer ring.

A spherical plain bearing includes an outer ring having a concave interior spherical surface, and an inner member having a convex exterior spherical surface. The inner member is pivotally disposed in the outer ring such that the inner member and the outer ring are angularly misalignable relative to one another. The spherical plain bearing includes an angular misalignment restraint system which includes an inner member restraint feature on the inner member and an outer ring restraint feature on the outer member. The first and second portions are spaced apart when the inner member and the outer ring are angularly misaligned relative to one another by less than a predetermined maximum angle θ, and come into abutment when the inner member and the outer ring are angularly misaligned relative to one another by angle θ. The abutment prevents any further relative angular misalignment of the inner member and the outer ring.

The socket assembly has a housing with an inner bore which extends from a first end to a second end. A ball portion of a ball stud is received in the inner bore. A backing bearing is disposed in the inner bore and presents a curved bearing surface in surface-to-surface contact with the ball portion. A first spring biases the backing bearing against the ball portion. The socket assembly also includes an exit bearing with a cylindrical portion that is in contact with an equator of the ball portion and a semi-spherical portion that is in surface-to-surface contact with an opposite hemisphere from the first bearing surface. A second spring biases the exit bearing into a predetermined location established by the housing. The exit bearing is movable from the predetermined location in a direction towards the second end of the housing against a biasing force of the second spring.

A method for operating a rotating machinery comprising a rotor, a rotor shaft, and at least one journal bearing supporting the rotor shaft is disclosed. The bearing comprises a bearing housing, a bearing surface in the bearing housing, a sleeve torsionally and axially fitted on the shaft, and a lubrication oil film filling a clearance between the outer surface of the sleeve and the bearing surface. The method comprises the step of modifying the clearance by modifying a radial dimension of the outer surface of the sleeve as a function of a rotation speed of the shaft.

A method for operating a rotating machinery comprising a rotor, a rotor shaft, and at least one journal bearing supporting the rotor shaft is disclosed. The bearing comprises a bearing housing, a bearing surface in the bearing housing, a sleeve torsionally and axially fitted on the shaft, and a lubrication oil film filling a clearance between the outer surface of the sleeve and the bearing surface. The method comprises the step of modifying the clearance by modifying a radial dimension of the outer surface of the sleeve as a function of a rotation speed of the shaft.