Rotary shafts – gudgeons – housings – and flexible couplings for ro – Coupling accommodates drive between members having... – Coupling transmits torque via radially spaced ball
Reexamination Certificate
2000-02-10
2001-07-17
Browne, Lynne H. (Department: 3629)
Rotary shafts, gudgeons, housings, and flexible couplings for ro
Coupling accommodates drive between members having...
Coupling transmits torque via radially spaced ball
C464S145000, C464S906000
Reexamination Certificate
active
06261184
ABSTRACT:
BACKGROUND OF THE INVENTION
The invention relates to a constant velocity joint, especially for steering a motor vehicle.
In particular, constant velocity joints are used in the driveline of a motor vehicle such as, for example, in the side shafts between the differential and the wheels to be driven; or in the propeller shaft between the gearbox output positioned in front, and the axle drive arranged at the rear axle.
DE 40 31 819 C1 describes a joint for large articulation angles and high torque values, for example, wherein the outer part is provided with alternating first and second outer running grooves, and the inner part is provided with alternating first and second inner running grooves. The first outer running grooves and first inner running grooves start from a first open end, and extend in an undercut-free way towards the second open end, whereas the second outer running grooves and the second inner running grooves extend from the opposed open end in an undercut-free way. The joint thus comprises tracks which alternately extend in opposite directions on the circumference. Between the outer part and inner part, there is arranged a cage. By means of a hollow spherical face, the cage is arranged centrically relative to the spherical outer face of the inner part. Furthermore, the cage, by means of its spherical outer face, is arranged concentrically relative to the spherical inner face of the outer part. The spherical inner face of the outer part is formed by first and second partial inner faces. The first partial inner faces start and extend, in an undercut-free way, from the open end from which the first outer running grooves extend in an undercut-free way. The second partial inner faces start from and extend, in an undercut-free way, from the second open end of the outer part, from which the outer running grooves extend in an undercut-free way. With the first and second outer running grooves and first and second inner running grooves alternately following one another, the first and second partial inner faces are arranged in the region of the webs between two circumferentially adjoining first and second outer running grooves in such a way that the first partial inner faces directly adjoin the first outer running grooves, and the second partial inner faces directly adjoin the second outer running grooves, and abut one another in the central region between first and second outer running grooves. The outer part is a solid part and can be produced by precision forming. The same applies to the inner part.
With regard to the foregoing joint, after the outer part has been produced to its final dimensions, it is typically broken into two individual annular segments by applying radial pressure. In this way, during assembly, after the cage has been slid on to the inner part by means of its hollow spherical face, the balls can be inserted into the windows from the outside. Subsequently, the two annular segments are mounted radially, and the unit, by means of the outer face of the outer part, is inserted into a bore of a bell. The bell supports the outer part in the radial direction. To achieve a rotationally fast connection, there are provided recesses in one of the end faces which form the open ends. After the unit has been inserted, the wall of the bell is deformed in such a way that it extends over an end face forming the open end, with material entering the region of the recesses. In this way, there is produced a rotationally fast connection. While it is true that producing such components by precision forming is less expensive than embodiments which start from a forged blank and have to be machined in a chip-forming way, the costs are still very high. This is especially true for constant velocity joints which are used for the transmission of low torque values only and at low speeds.
SUMMARY OF THE INVENTION
It is therefore an object of the present invention to provide a constant velocity joint of the above-described type which is characterized by low production costs.
In accordance with one embodiment of the present invention, the foregoing object is achieved by providing a constant velocity joint comprising a first axial end and a second axial end, and having an annular outer part. The annular outer part comprises a longitudinal outer part axis, and first outer running grooves and second outer running grooves which are alternately arranged around the longitudinal outer part axis. The first outer running grooves start from the first end and extend towards the second end, with the track bases of same approaching the longitudinal outer part axis towards the second end. Furthermore, the second outer running grooves start from the second end and extend towards the first end, with the track bases of same approaching the longitudinal outer part axis towards the first end. Preferably, the outer part is produced from at least one planar plate metal part which, after the first outer running grooves and second outer running grooves have been formed in a non-chip producing way, is bent into an open ring which may include one or more annular segments. In addition, the outer part, towards the first end and towards the second end, is provided with centering faces on its outer face between the first outer running grooves and the second outer running grooves.
The constant velocity joint of the present invention further includes a receiving part which is provided in the form of a closed ring. The receiving part comprises a cylindrical bore interrupted by grooves. The number of grooves correspond to the number of first and second outer running grooves. The grooves circumferentially receive, in a form-fitting way, at least axial partial portions of the outwardly projecting formations of the outer part in the region of the first outer running grooves and second outer running grooves. Furthermore, the outer part is held in the axial direction between stops relative to the receiving part.
The constant velocity joint of the present invention further includes an inner part which comprises a longitudinal inner part axis, and an outer face in which first inner running grooves and second inner running grooves are alternately distributed around the longitudinal inner part axis. The first inner running grooves are positioned opposite first outer running grooves forming pairs therewith. The first inner running grooves start from the first end and extend towards the second end, with their track bases moving away from the longitudinal inner part axis. Whereas the second inner running grooves start from the second end and extend towards the first end, with the track bases of same moving away from the longitudinal inner part axis.
The constant velocity joint of the present invention also includes a cage which is arranged between the outer part and the inner part, and is provided with radial windows. The joint also includes balls which are guided in the windows of the cage and which are each engaged by pair-forming first outer running grooves, and first inner running grooves and pair-forming second outer running grooves and second inner running grooves.
The advantage of the foregoing embodiment is that the design allows advantageous production conditions. For example, it is possible to start from a high-quality plate metal strip which, by punching, stamping and bending, can cost-effectively be given a pre-shape. The final shape can be achieved by placing the bent plate metal strip onto a mandrel comprising the inner contour of the outer part and by pulling same through a tool containing the final outer contour. In the process, it is possible to produce the final dimensions of the centering seat which is located only on outer portions of the formations in which the outer running grooves are provided. The annular segments are not provided with a direct counter-support along the whole length of the outer running grooves, but the specific shape ensures a relatively high degree of stiffness. On the other hand, a limited amount of elasticity for cage guiding purposes is advantageous, so that it is possible to achiev
Jacob Achim
Jacob Werner
Browne Lynne H.
GKN Lobro GmbH
Thompson Kenn
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