ROTATIONAL BEARING ARRANGEMENT FOR A STEERING COLUMN OF A MOTOR VEHICLE

Abstract

A pivot bearing arrangement for a steering column of a motor vehicle, having a steering shaft which is rotatably mounted in a casing unit in the direction of its axis of rotation but rigidly mounted in the radial direction, is improved in terms of a simple and cost-effective construction in that the casing unit is provided with at least one first sliding bearing shell, which comprises a first circumferential radial projection, which engages in a first circumferential groove.

Claims

1.-10. (canceled)

11. A pivot bearing arrangement for a steering column of a motor vehicle, comprising: a casing unit; a steering shaft including a first circumferential groove, the steering shaft rotatably mounted in the casing unit about an axis of rotation; and a first sliding bearing shell disposed on the casing unit, the first sliding bearing shell including a first circumferential radial projection that is configured to engage in the first circumferential groove of the steering shaft.

12. The pivot bearing arrangement of claim 11, including a second sliding bearing shell disposed on the casing unit, which is arranged axially spaced from the first sliding bearing shell and includes a second circumferential radial projection that engages in a second circumferential groove of the steering shaft.

13. The pivot bearing arrangement of claim 12, wherein the first sliding bearing shell is connected to an end section of the casing unit by press fit and the associated first circumferential groove is arranged in an end region of the steering shaft, which is configured to receive a steering wheel.

14. The pivot bearing arrangement of claim 12, wherein on the casing unit, adjacent to the second sliding bearing shell, a bearing ring with a bearing section projecting inwardly is fastened, and a radial outside of the second sliding bearing shell lies against the casing unit with sliding fit and between the bearing section of the bearing ring and an axial lateral face of the second sliding bearing shell a compression spring is arranged, which is configured to axially preload the second sliding bearing shell relative to the first sliding bearing shell held on the casing unit.

15. The pivot bearing arrangement of claim 14, wherein the bearing ring is arranged on an axial side of the second sliding bearing shell facing the first sliding bearing shell, such that the compression spring biases the two sliding bearing shells apart.

16. The pivot bearing arrangement of claim 14, wherein the bearing ring is arranged on an axial side of the second sliding bearing shell facing away from the first sliding bearing shell, such that the compression spring biases the two sliding bearing shells towards one another.

17. The pivot bearing arrangement of claim 14, wherein the compression spring is a disk spring or a wave spring.

18. The pivot bearing arrangement of claim 12, wherein one or both of the first sliding bearing shell and the second sliding bearing shell is plastic.

19. The pivot bearing arrangement of claim 18, wherein the plastic is a polyoxymethylene or a polyamide.

20. The pivot bearing arrangement of claim 11, wherein one or both of the first circumferential groove and the second circumferential groove is molded into the steering shaft by rolling.

Description

[0017] In the following, exemplary embodiments of the invention are explained in more detail by way of the drawings. In detail:

[0018] FIG. 1 shows a perspective view of a steering column with rigid casing unit and rotatable steering shaft;

[0019] FIG. 2 shows a pivot bearing arrangement as claimed in the invention of a rotatable steering shaft in a casing unit as an exploded representation;

[0020] FIG. 3 shows a section through casing unit and steering shaft with pivot bearing arrangement as claimed in the invention in a first embodiment;

[0021] FIG. 4 shows an enlarged detail from FIG. 3 of the region of the first pivot bearing;

[0022] FIG. 5 shows an enlarged detail from FIG. 3 of the second pivot bearing;

[0023] FIG. 6 shows a representation as claimed in FIG. 3, however of a second embodiment of the invention.

[0024] A section of a steering column 1 of a motor vehicle is evident in FIG. 1. A steering shaft 2 is rotatably mounted in the interior of a casing unit 3. The casing unit 3 is firmly connectable to the chassis of a motor vehicle, which is not shown, by means of a support 4. A clamping tube 5 is pivotably connected about a pivot axis 44 with the support 4 designed as console, the clamping tube 5 having a longitudinal slit 55 on the top side. Furthermore, a clamping device 6 is arranged on the support 4, which can be clamped or opened by means of an actuaton lever 7. When the actuation lever 7 is moved in the clamping direction the clamping device 6 causes an elastic deformation of the clamping tube 5, the mentioned longitudinal slit becoming smaller (narrower) and the casing unit 3 arranged in the clamping tube 5 being clamped tight, so that it is rigidly connected to the support 4. An end region 8 of the steering shaft 2 projecting from the casing unit 3 is provided with a positive connection profile designed as external splines and is intended for receiving a steering wheel that is not shown. The steering shaft 2 is connected to a universal joint 200. As is best evident in the FIGS. 3 to 6, the steering shaft 2 is rotatably mounted in the casing unit 3 by means of a first sliding bearing 9 and a second sliding bearing 10.

[0025] The first sliding bearing 9 consists of a first sliding bearing shell 11 made of plastic, which is connected to an end section 13 of the casing unit 3 by press fit. Furthermore, the first sliding bearing shell 11 comprises a circumferential first radial projection 14, which engages in a first circumferential groove 15 of the steering shaft 2. The first circumferential groove 15 is arranged in the end region 8 of the steering shaft 2, which is intended for fastening a steering wheel.

[0026] Accordingly, the second sliding bearing 10 has a second sliding bearing shell 12 which, axially spaced from the first sliding bearing shell 11, is arranged with sliding fit on the casing unit 3. The second sliding bearing shell 12 has a second circumferential radial projection 16 which engages in a second circumferential groove 17 of the steering shaft 2.

[0027] Furthermore, a circumferential bearing ring 18 is fastened on the casing unit 3, adjacent to the second sliding bearing shell 12, which bearing ring 18 has a circumferential bearing section 19 projecting towards the inside. Between an inner axial face 20 of the bearing section 19 and an axial lateral face 21 of the second sliding bearing shell 12 located opposite, a compression spring 22 is arranged which supports itself on the inner axial face 20 of the bearing section 19 and attempts to shift the second sliding bearing shell 12 to the right in the axial direction relative to the casing unit 3. The second sliding bearing shell 12 however is supported by its second radial projection 16 in the second circumferential groove 17 of the steering shaft 2 namely both in the radial direction and in the axial direction. For this reason, the preload of the compression spring 22 in the axial direction causes the second sliding bearing shell 12 to attempt to shift the steering shaft 2 to the right in the axial direction (see FIGS. 5 and 3). This is possible because the radial outside 23 of the second sliding bearing shell 12 forms a sliding fit with the inner wall face 24 of the casing unit 3 and can be shifted relative to the casing unit 3 in the axial direction by strong forces. As a reaction to this, a preload materializes on the first sliding bearing 9 since the first sliding bearing shell 11 is connected to the casing unit 3 by a firm press fit and is not shiftable relative to the casing unit 3. However, the compression spring 22 causes the steering shaft 2 to shift to the left in the axial direction while the casing unit 3 pulls to the right. This causes the first sliding bearing shell 11 to be preloaded relative to the first circumferential groove 15 of the steering shaft 2. Because of the sloping flanks of the circumferential grooves 15, 17, the preload in the axial direction also causes a preload in the radial direction so that the resulting preload force is also oriented obliquely, i.e. at an angle to the longitudinal axis 33. The dashed lines 25 to 28 in FIG. 3 are oriented in the direction of the resulting preload forces. The lines 25 and 27 and 26 and 28 respectively intersect outside the first and second sliding bearing shells 11, 12, i.e. the points of intersection of the lines 25 and 27 and 26 and 28 respectively are not located between the sliding bearing shells 11, 12 but on the respective side of the sliding bearing shell facing away from the other sliding bearing shell. Such a bearing arrangement as is shown in the FIGS. 3 to 5 is also referred to as O-arrangement. Such a bearing arrangement offers the advantage that axial loads are absorbed in both axial directions, but in each case only by one bearing or bearing set, which produces a rigid mounting. Thanks to the large distance between the effective bearing centers (intersection point of the lines 25 and 27 and 26 and 28 respectively), this arrangement is particularly well suited for absorbing moment loads acting on the steering shaft, for example in the case of a vehicle head-on collision. During a vehicle head-on collision, a bending moment is introduced into the steering shaft by the vehicle driver striking the steering wheel.

[0028] In the embodiment described above, the bearing ring 18 is arranged between the first sliding bearing shell 11 and the second sliding bearing shell, i.e. in the inner region. Here, the two sliding bearing shells 11, 12 are axially pressed to the outside, namely the first sliding bearing shell 11 to the left and the second sliding bearing shell 12 to the right.

[0029] However, in a second embodiment of the invention shown in FIG. 6, the bearing ring 18 is arranged on the axial side of the second sliding bearing shell 12 facing away from the first sliding bearing shell 11, and is thus located outside the interior space delimited by the two sliding bearing shells 11, 12. This has the consequence that the second sliding bearing shell 12 is pushed to the left and in the process drives the steering shaft 2, so that the first sliding bearing shell 11 lies against the right flank of the first circumferential groove 15. Thus, the two sliding bearing shells 11, 12 are pushed towards one another. This has repercussions on the resulting forces between the sliding bearing shells 11, 12 and the circumferential grooves 15, 17. As is evident in FIG. 6, the dashed lines 29 to 32 oriented in the force direction run differently from the dashed lines 25 to 28 from FIG. 3, for the dashed lines 29 and 31 and the line 30 and 32 intersect between the sliding bearing shells 11, 12. This bearing arrangement is referred to as X-arrangement.

[0030] In the present exemplary embodiment, the compression spring 22 is designed as a disk spring stack. However, a wave spring can also be used. The sliding bearing shells 11, 12 consist of plastic. The bearing ring 18 is produced from metal. The circumferential grooves 15, 17 were molded into the steering shaft 2 by rolling. The two sliding bearings 9, 10 thus consist of the sliding bearing shells 11, 12 and the circumferential grooves 15, 17 molded into the steering shaft 2 by rolling. The production is therefore particularly simple and cost-effective. The device for the axial preload is also constructed particularly simply. It merely consists of the bearing ring 18 and the compression spring 22. The bearing ring 18 and the inner diameter of the casing unit 3 have an interference fit, i.e. the bearing ring 18 is received in the casing unit 3 after the assembly by means of a press fit and constitutes a counter bearing for the compression spring 22.

[0031] Obviously, the invention includes embodiments in which the grooves are molded into the casing unit 3 and the sliding bearing shells are fastened to the steering shaft 2. The bearing ring can likewise also be fastened to the steering shaft 2 instead of the casing unit 3.

[0032] For assembling the pivot bearing arrangement as claimed in the invention, the first sliding bearing shell 11 is slid over the steering wheel-side end region 8 of the steering shaft 2, wherein the sliding bearing shell 11 consisting of plastic expands elastically and thereafter snaps into the first circumferential groove 15. Following this, the assembly consisting of steering shaft 2 and first sliding bearing shell 11 is pressed into the tube of the casing unit 3, wherein the first sliding bearing shell 11 is firmly connected to the end section 13 of the casing unit 3 by press fit. Following this, the assembly consisting of bearing ring 18, compression spring 22 and second sliding bearing shell 12 is slid into the annular intermediate space between the steering shaft 2 and the casing unit 3 until the second radial projection 16 of the second sliding bearing shell 12 snaps into the second circumferential groove 17 of the steering shaft 2.

LIST OF REFERENCE NUMBERS

[0033] 1 Steering column [0034] 2 Steering shaft [0035] 3 Casing unit [0036] 4 Support [0037] 5 Clamping tube [0038] 6 Clamping device [0039] 7 Actuation lever [0040] 8 End region [0041] 9 First sliding bearing [0042] 10 Second sliding bearing [0043] 11 First sliding bearing shell [0044] 12 Second sliding bearing shell [0045] 13 End section [0046] 14 First radial projection [0047] 15 First circumferential groove [0048] 16 Second radial projection [0049] 17 Second circumferential groove [0050] 18 Bearing ring [0051] 19 Bearing section [0052] 20 Inner axial face [0053] 21 Axial lateral face [0054] 22 Compression spring [0055] 23. Radial outside [0056] 24 Inner wall face [0057] 25 to 32 Dashed line [0058] 33 Axis of rotation