The invention concerns a turbomachine rotor (1), characterised in that it comprises a threaded or tapped part (3, 6) and a damping nut (8) screwed onto the threaded or tapped part (3, 6) so as to allow the threads of the nut (8) and of the threaded or tapped part (3, 6) to rub against each other in the event of vibration of the rotor (1).

A clutch arrangement is provided with a clutch housing that connects a drive unit to an output, such as a transmission, which is rotatable around a central axis and with which an axial central projection is associated at the side of the clutch housing facing the drive unit in the radial extension area of its rotational center. The axial central projection receives a rotor carrier receiving a rotor of an electric machine. The central projection is connected at least so as to be fixed with respect to relative rotation to the drive unit via a first connection device and to the rotor carrier via a second connection device.

A clutch arrangement is provided with a clutch housing that connects a drive unit to an output, such as a transmission, which is rotatable around a central axis and with which an axial central projection is associated at the side of the clutch housing facing the drive unit in the radial extension area of its rotational center. The axial central projection receives a rotor carrier receiving a rotor of an electric machine. The central projection is connected at least so as to be fixed with respect to relative rotation to the drive unit via a first connection device and to the rotor carrier via a second connection device.

The invention relates to a wheel bearing unit (1) for supporting a vehicle wheel which can be driven. This wheel bearing unit (1) includes a wheel hub (2) which forms a hollow space (11) and is rotatably supported by a wheel bearing (3) formed as a rolling bearing, wherein the wheel bearing is inserted (3) in a wheel carrier. Furthermore the wheel hub (2) is connected by a hub flange (21) to the vehicle wheel and reciprocally to the hub flange (21) by an end toothing (9) in positive engagement with a drive joint (8). A measurement of a torque or a torsion takes place by a sensor (18) at an inner wall (17) of the hollow space (11) of the wheel hub (2).

A coupling is provided that includes a shaft, a hub, a retainer and a fastener. The shaft includes a plurality of shaft splines. The shaft splines are arranged circumferentially about an exterior of the shaft. The hub includes a plurality of hub splines, a hub bore and a hub fastener aperture. The hub splines are arranged circumferentially about the hub bore. The hub splines are mated with the shaft splines. The shaft is within the hub bore. The retainer includes a plurality of retainer splines, a retainer bore and a retainer fastener aperture. The retainer splines are arranged circumferentially about the retainer bore. A first of the retainer splines circumferentially overlaps and is axially next to a first of the shaft splines. The shaft is within the retainer bore. The fastener is within the hub fastener aperture and the retainer fastener aperture. The fastener connects the retainer to the hub.

A drive gear adapted to be disposed in a gear box includes a body having a perimeter and a skirt that extends outwardly from the perimeter of the body. A plurality of teeth extends outwardly from the body along a portion of the perimeter of the body. An opening extends through the body and is defined by an inner surface of the body. The inner surface includes a plurality of planar portions and a plurality of rounded portions that extend between the plurality of planar portions. The plurality of planar portions is arranged such that a force (e.g., a torque) applied to the body is directed toward the plurality of teeth.

An exhaust-gas turbocharger (1), having a shaft (2) which has an outer diameter (A.sub.2); a turbine wheel (5) which is fastened to the shaft (2); and a connecting device (8) via which the shaft (2) is fastened to the turbine wheel (5). The shaft (2) has, in the region of an end side (3), a shaft shoulder (4) with an outer diameter (A.sub.4) larger than the outer diameter (A.sub.2) of the shaft (2). The turbine wheel (5) has an external thread portion (7) integrally formed on its wheel rear side (6) The connecting device (8) has a sleeve nut (8A) which is screwed onto the external thread portion (7) and, in a process, engages behind the shaft shoulder (4) in order to brace the shaft (2) against the turbine wheel (5).

An exhaust-gas turbocharger (1), having a shaft (2) which has an outer diameter (A.sub.2); a turbine wheel (5) which is fastened to the shaft (2); and a connecting device (8) via which the shaft (2) is fastened to the turbine wheel (5). The shaft (2) has, in the region of an end side (3), a shaft shoulder (4) with an outer diameter (A.sub.4) larger than the outer diameter (A.sub.2) of the shaft (2). The turbine wheel (5) has an external thread portion (7) integrally formed on its wheel rear side (6) The connecting device (8) has a sleeve nut (8A) which is screwed onto the external thread portion (7) and, in a process, engages behind the shaft shoulder (4) in order to brace the shaft (2) against the turbine wheel (5).

A freewheel assembly includes a central axis of rotation, a single-piece flange formed by deep drawing, and a freewheel unit. The single-piece flange includes a sleeve portion, a disk portion protruding radially outward from the sleeve portion, and a centering collar. The disk portion includes a first end face and the centering collar is formed on the first end face. The freewheel unit includes an outer ring fastened to the sleeve portion by press fitting, and a plurality of rolling elements accommodated within the outer ring. The outer ring includes a plurality of clamping ramps, and each one of the plurality of rolling elements cooperates with a one of the plurality of clamping ramps.

The fastening elements 71 are first set through the rotary disk 1 to be then fixed to the retention plates 2 so that the stretching force induced by the fixing operation is acting upon the retention plates 2. This helps prevent the rotary disk 1 from being affected by the stretching force and thus deformed. Further, the fastening holes 22 are located adjacent to the retention grooves 21 so that they can directly and effectively apply forces to the support members 3 and due to the torque (distance) thereof with respect to the support members 3 being reduced, it is possible to effectively reduce the occurrence of deformation of the retention plates 2. To summarize, since the stretching force induced by fixing is born by the retention plates 2, the rotary disk 1 may have a lifespan that is greater than that of the retention plates 2 and with the arrangement that releasable engagement is formed between the retention plates 2 and the rotary disk 1, it only needs to replace an individual one of the retention plates 2 that has been deformed in the maintenance thereof. Further, due to the size of the retention plates 2 being reduced, the cost of maintenance can be greatly lowered down.