Drivetrain systems and methods are provided. In one example, the drivetrain system includes an interaxle differential (IAD) configured to receive power from a prime mover, a motor configured to drive a planetary gearset, and a ball ramp actuator configured to selectively engage a plurality of plates in a clutch pack of a friction clutch in response to receiving rotational input from the planetary gearset. In an engaged configuration, the friction clutch prevents speed differentiation between a first IAD output and a second IAD output.

A wheel unit for an electric vehicle with a disengageable drive includes a wheel support, a wheel hub rotatably supported by the wheel support, and a wheel pin carried by a member driven by the electric motor and rotatably mounted within the wheel hub, by means of two rolling bearings. A coupling device connects in a releasable way the driven member to the wheel hub. The two rolling bearings that support in rotation the wheel pin have respective outer rings mounted by interference fit within a cylindrical wall of a central opening of the wheel hub, and respective inner rings rigidly connected together by means of a spacer sleeve having a predetermined length. The wheel-hub unit with the two rolling bearings and the spacer sleeve can be assembled before being mounted on the wheel pin.

A packaging system having an outboard guard and an outboard retainer cap. The outboard guard includes an outboard guard opening having a hole through the planform of the outboard guard, an engagement portion having an annular surface radially surrounding the outboard guard opening, an outboard bearing protector portion having an annular surface radially surrounding the engagement portion of the outboard guard, and an outer rim having an annular surface radially surrounding the outboard bearing protector portion. The outboard retainer cap is configured to be removably affixed to the outboard guard and includes an outboard alignment protrusion having a circular surface, an engagement portion having an annular surface radially surrounding the outboard alignment protrusion, and a retaining flange having an annular surface radially surrounding the engagement portion of the outboard retainer cap.

A packaging system having an outboard guard and an outboard retainer cap. The outboard guard includes an outboard guard opening having a hole through the planform of the outboard guard, an engagement portion having an annular surface radially surrounding the outboard guard opening, an outboard bearing protector portion having an annular surface radially surrounding the engagement portion of the outboard guard, and an outer rim having an annular surface radially surrounding the outboard bearing protector portion. The outboard retainer cap is configured to be removably affixed to the outboard guard and includes an outboard alignment protrusion having a circular surface, an engagement portion having an annular surface radially surrounding the outboard alignment protrusion, and a retaining flange having an annular surface radially surrounding the engagement portion of the outboard retainer cap.

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 gas turbine engine with a lubrication system includes a ball bearing assembly and a rotor circumscribing a rotational axis and journaled within the ball bearing assembly. The gas turbine engine also includes a lubrication system located radially outward from a rotational axis and radially outward and adjacent to the ball bearing assembly, which includes a lubrication channel having an inlet and an outlet and a dispersion cone adjacent to the outlet of the lubrication channel.

In accordance with one aspect of the present disclosure, a turbocharger having a rolling element bearing (REB) assembly contained within a bearing housing includes an axial damper configured to dampen and limit axial displacement of the REB assembly. The axial damper can include different embodiments, including an elastomeric axial damper, wire mesh, or oil film, for interrupting contact between the bearing assembly and a displacement limit when an axial displacement force exceeds a preload force. Further, the axial damper can include an apparatus having at least two axially compressible rings, where one of the axially compressible rings includes a displacement limit feature.

An axle assembly that includes an axle housing, a differential carrier, and an electric motor module. The differential carrier that is mounted to the axle housing and rotatably supports a differential. The electric motor module is received inside the differential carrier and is operatively connected to and provides torque to the differential.

The invention relates to a bearing cage for a bearing of the type comprising a first ring having a first bearing race, a second ring having a second bearing race, rolling bodies positioned in an annular rolling volume between the first and the second bearing races in such a way as to enable a relative rotation between the first and second rings around a reference axis of the bearing, the cage comprising cells for housing rolling bodies, the cage being characterised in that it comprises an interface for coupling with a maneuvering member, such that when the maneuvering member is engaged with the coupling interface, the bearing cage is capable of being rotationally driven by the maneuvering member in a predetermined direction with respect to the reference axis.

A bearing device includes a rotational shaft; a first outer ring; a second outer ring; first balls; second balls disposed; and a C-spacer and a second spacer. α>δd is satisfied, where δd represents a difference between an inside diameter of the second spacer at an end portion on a second side and an outside diameter of a shaft outer circumferential face, and a represents a half of a difference between a diameter of a cylindrical face of the C-spacer on an outer circumferential side and a diameter of the cylindrical face of the C-spacer on an inner circumferential side.