DE102007002992A1 - Wheel bearing unit for motor vehicle, has transverse control arm connected with bearing carrier in flexible manner according to type of hinge joint, and joint connection designed in O-arrangement by sliding or antifriction bearing - Google Patents

Abstract

The bearing unit (1) has a wheel bearing carrier (2) and a transverse control arm (5) connected with the bearing carrier in a flexible manner according to a type of a hinge joint. A joint connection (4) is designed in O-arrangement by a sliding or antifriction bearing. The antifriction bearing exhibits an inner ring, which is connected with the bearing carrier or control arm over a clamping screw forming a bearing axis. The antifriction bearing is an inclined roller bearing, inclined spherical roller bearing and an inclined ball bearing.

Description

Field of the invention

The The invention relates to a wheel bearing unit of a motor vehicle, comprising a wheel bearing carrier and one articulated with this in the manner of a hinge joint Wishbone.

Background of the invention

One Swivel bearing serves to over a wheel bearing a wheel, for example, with a drive shaft connected to store.

there is usually the pivot bearing on the one hand with the outer ring of the wheel bearing, on the other connected with a strut, in turn, with the bodywork connected is. A strut dome picks up vertical forces and allows the Pivoting the unit. It forms the upper attachment and Movement point of the unit.

in the lower area is the pivot bearing in a known manner via a joint connected to a wishbone, which when accelerating, braking and picks up horizontal forces when cornering. The hinge So, in addition to the upper suspension tower the second lower one Storage of the vertical wheel swivel axle available.

The Connection of the control arm to the pivot bearing is usually by means of a Ball joint realized. The wishbone itself is about the axis of rotation, through the two bearings on the body in the direction of travel runs, more or less movable to the vertical movement of the strut to allow during compression.

in the The prior art is thus the connection between the wishbone and Swivel bearing a ball joint, which is the translational connection between swivel bearing and wishbone in all three directions sets; the rotatory ones are not blocked.

The essentially lying in the direction of travel axis allows as described the deflection while the substantially vertical axis required for steering Swivel movement allows.

There the puncture point the wheel axle through the force application plane of the pivotable wheel bearing unit but outside the connection guide joint - upper damper storage is located on the strut tower, arise during acceleration (front-wheel drive) just this axis a moment on the pivot bearing, which are supported on the vehicle must, here at the tie rod. The result is a disturbing steering torque at different coefficients of friction between the drive wheels and the road in case of acceleration.

The Avoidance of this effect is due to the displacement of the above-mentioned pivot axis into the wheel plane possible.

in the The prior art does not fully match the pivot axis and wheel plane, but a reduction of the spread angle from about 14 ° (MacPherson) to about 5 ° (Revo-Knuckle, Ford).

To For this purpose, the system is designed such that a pivot bearing with pressed wheel bearing swiveling in a non-swiveling Wheel carrier connected is. The wheel bearing carrier in turn, is so connected to the vehicle, that on the one hand the vertical forces, to others induced from longitudinal forces Moments supported become.

The Bearing connection between wheel bearing carrier and wishbone is here executed by means of a hinge joint as a guide joint. The joint is by means of a quasi in the length drawn ball joint realized on plain bearing base. The longitudinal axis this bearing arrangement is directed parallel to the vehicle longitudinal axis, so that a pivoting movement about the vehicle longitudinal axis is possible, as they are for compression of the wheel is required.

however Movements around the orthogonal standing horizontal axis and vertical axis locked and supported, therefore, accordingly Moments about these axles taken from this particular bearing design.

The joint offers in this embodiment no more steering function is So no longer part of the steering. Rather, the steering is alone laid in the area of the connection of the pivot bearing to the wheel bearing carrier, the vertical pivot axis extends So, as mentioned above with significantly less spread than the MacPherson axis.

Though offers the above-described special design of the guide joint compared with the previously described pivot bearing connection a torque support between wheel bearing carrier and Wishbone by the big one axial distance between the supports due to the elongated "ball joint geometry" in this embodiment, however, despite the considerable axial extent an X-arrangement of the storage.

considered one is now the effective acting support base due to the X-arrangement, so this ultimately relatively small, the joint so axially seen unnecessarily long, thus only partially effective. Because of the very short support base can not too big Moments over the bearing be absorbed or supported.

Summary of the invention

Of the The invention is thus based on the problem of a wheel bearing unit consisting of a wheel bearing carrier and an articulated with this in the manner of a hinge joint Wishbone with an improved supporting effect in the area of the hinge-joint type Wheel carrier-wishbone connection specify.

to solution This problem is in a wheel bearing unit of the aforementioned Art provided according to the invention, that the hinge connection by means of a sliding or rolling bearing formed in O arrangement.

According to the invention was recognized that when using a sliding or rolling bearing in O arrangement a very wide, axially long support base in the region of the joint connection from the wheel bearing carrier can be achieved to the control arm.

At the Wheel carrier Occurring moments about the vehicle transverse and vertical axis can therefore on this seen axially very long support base excellent supported and be recorded while at the same time movability around the Longitudinal axis of the Vehicle to enable a deflection of the wheel, which in turn arranged by a sprung Wheel carrier can be effected.

Farther can thus also the vertical pivot axis of the wheel to the wheel plane be shifted back after the articulation between a - in this Case not mitschwenkendem and / or sprung arranged - Radlagerträger and the wishbone in the wheel bearing unit according to the invention no steering function, but exclusively the function of suspension capability and the moment support due.

The used according to the invention Sliding or rolling bearings offers a high load rating and at the same time does not build axially too long, so no constructive difficulties with the adjacently extending steering arrangement result. In front everything when turning leads too big axial Expansion of the guide joint to collision between the joint and surrounding structures such. B. the brake disc.

Especially is preferred in view of the high forces to be absorbed or Moments the use of a rolling bearing in the form of a tapered roller bearing, in particular with conical or cylindrical rolling elements, one Inclined spherical bearing or an angular contact ball bearing, which are designed in corresponding O-arrangement realized.

Such Bearings are extremely high Load capacities at the same time relatively low friction moments on what has a positive effect on the response of a suspension. Demanded here is a very robust Bearing that is free of play to the high moments when braking or Accelerate optimally over support the O-arrangement to be able to.

The Sliding or rolling bearings itself may have an inner ring which forms over a bearing axis Clamping screw with the wheel bearing carrier or is connected to the wishbone. There is always the possibility the respective bearing with its inner ring either on the wheel bearing carrier or on To attach the wishbone and the other part with the outer ring connect to. In any case, this is expediently via a bearing axis forming Clamping, z. B. a clamping screw, so that basically a simple construction results.

there it is particularly preferred if the inner ring on the clamping means relative in terms of of the outer ring can be clamped to produce a bearing preload.

About the Clamping, z. B. the clamping screw, so it can generate a high bearing stress so that the camp itself does not have any play and no freedom of movement to have other than the axis of rotation.

As described the bearing must be very robust and record high moments can, so that a high tension is beneficial. This can according to the invention to simple Way over a clamping screw can be generated and adjusted.

In In this context, it is expedient if the inner ring a is one-piece forming part, or two inner ring parts, respectively Forming parts are. For one, this is the production Relatively simple, since it only needs one forming step, However, the inner ring is not made of the full material to manufacture. The use of a suitable cold strip, hot strip or similar qualities is possible without further ado. The same of course applies also for the outer ring.

The sliding or rolling bearing, in particular the tapered roller or ball bearing, either a be symmetrical or asymmetric bearing, with an asymmetric bearing is particularly easy to form when the inner ring is made in two parts.

The Stock itself can additionally be sealed, including appropriate sealing means may be provided can.

If the bearing with the inner ring is supported on one side, for example a sealing cover in the outer ring caulked and omitted the seal on this page.

Farther may preferably be provided that the wheel bearing carrier such connected to a wheel bearing is that the wheel bearing carrier at a pivoting of the wheel bearing and / or a Radverschwenkung not mitverschwenkt.

Also can preferably be provided that the Radlagerträger bearing receptacles and on the wheel bearing, in particular on an outer ring of the wheel bearing, journals are formed. It can the bearing mounts and trunnions connected in such a way be that the wheel bearing about a vertical axis z pivotally mounted relative to the wheel bearing carrier is.

Farther can be provided that the bearing receivers and the journals are arranged such that a vertical axis formed thereby z passes through a wheel supported by the wheel bearing.

Brief description of the invention

Further Advantages, features and details of the invention will become apparent below based on embodiments described with reference to the figures. The figures are schematic Representations and show:

1 a perspective view, partially in section, of a wheel bearing unit according to the invention,

2 a detailed view of the connecting portion between the wheel bearing support and wishbone using a rolling bearing of a first embodiment, and

3 a representation accordingly 2 using a rolling bearing of a second embodiment.

Detailed description the drawings

1 shows a wheel bearing unit according to the invention 1 comprising a wheel bearing carrier which does not pivot when the wheel is swiveled 2 , which is partially shown here in section.

This wheel bearing carrier 2 has an upper receptacle 3 for connection to a strut in a conventional manner. In the lower area is the wheel bearing carrier 2 via a joint connection 4 with a wishbone 5 , which is also shown partially cut here, connected to this a leading hinge joint performing joint connection 4 will be discussed in more detail below.

At the wheel bearing carrier 2 is in an upper and lower bearing receptacle 6 a wheel bearing 7 over its outer ring 8th , on the corresponding journal 9 are formed, pivotally mounted about a vertical axis z. To this vertical axis z, the wheel which is rotatably mounted thereon, are pivoted via a steering connection not shown in detail. This steering link engages the track lever on the outer ring 8th of the wheel bearing 7 in a manner not shown in detail.

The upper bearing support 6 preferably takes on vertical or axial forces resulting from a wheel contact force. The upper and lower bearing mount 6 continue to take radial forces that consist of a longitudinal component - resulting from longitudinal forces during braking and / or acceleration - and from a transverse component - resulting from forces due to cornering, excessive road and / or crosswind - on. Continue to take the upper and lower bearing 6 Radial or transverse forces as a pair of forces to compensate for moments that result from longitudinal and / or lateral forces, on.

The wheel bearing 7 also has an inner ring 10 on, with respect to the position-fixed outer ring 8th over the rolling elements 11 of the executed here as a ball bearing wheel bearing 7 is rotatable. With this inner ring 10 is in a conventional manner, the brake disc 12 connected to the turn the not shown here in detail wheel or its rim is attached.

In the embodiment shown here, furthermore, the inner ring 10 with the drive shaft 13 , which is driven by the gearbox, connected, which is realized via a hinge connection not shown here.

As described, the vertical axis z lies in the wheel bearing in this embodiment 7 even; she walks through the journals 9 and thus directly through the wheel itself.

This is made possible here, after, unlike previously mostly usual, the hinge connection 4 , so the hinge-like guide joint between the wheel bearing carrier 2 and the wishbone 5 No more steering function, so it is no longer part of the steering.

Rather, the local joint stock is there 4 designed so that it allows only a pivotal movement about the vehicle longitudinal direction x-axis, while pivotal movements about the vertical z-axis and the orthogonal thereto horizontal axis y, which runs in the vehicle transverse axis, are locked and any on the Radlagerträger 2 torques arising from the z or y axis resulting from acceleration or braking are supported.

Consequently, the hinge bearing described in more detail below 4 in that it has high rigidity against tilt about the z-axis and about the y-axis (during braking and / or acceleration). The spherical bearing acts radially (vehicle lateral forces, y-forces) and axially (vehicle longitudinal forces, x-forces), whereas it is effective for forces in the z-direction.

2 shows in the form of a schematic representation of a first embodiment of the hinge connection 4 in the form of a rolling bearing 14 , here a tapered roller bearing.

Shown is in 2 a sectional view through the wheel bearing carrier 2 and the wishbone 5 that are only partially illustrated. At the wheel bearing carrier 2 is a camp recording 15 provided, which also in 1 is shown. In this is the outer ring 16 of the rolling bearing 14 inserted positive and non-positive, preferably pressed.

The optionally also in two parts formable outer ring 16 has a cross-sectionally substantially V-shaped profiling. Corresponding is also the inside 17 the recording 15 executed. The outer ring 16 is preferably made as a formed part of a suitable metal strip.

The rolling bearing 14 also has a split inner ring 18 on, whose two inner ring parts 18a . 18b each made as a one-piece component of a metal strip.

The outer ring 16 as well as the inner ring 18 have corresponding running surfaces for the rolling elements 19 on, which are designed here as cylindrical rollers.

The inner ring 18 in turn, via a clamping screw, which is not shown here, fixed to the wishbone 5 connected, for this purpose, provided with an internally threaded screw receptacle 20 having. The screw lies with its screw head on the bearing surface 21 of the inner ring 18 so that this inner ring 18 firmly against the abutment on the control arm 5 is strained.

This can be used to generate a radial preload, ie the inner ring 18 relative to the outer ring 16 be braced, whereby the bearing is braced radially as a whole, so therefore an absolute backlash is realized at the same time high bias. This bias is appropriate, as about the rolling bearing 14 Any moments that act on the z-axis (vertical axis) or the y-axis (horizontal axis) on the wheel bearing carrier to be supported.

At the preload of the rolling bearing 14 through the clamping screw put the inner ring parts 18a . 18b of the inner ring 18 to each other. By a corresponding dimension of the axial width of the voltage applied to the clamping screw inner ring parts 18a . 18b the bearing preload can be influenced. Here is according to 2 a - realized in the sense of a power flow - series connection: screw head, first inner ring part 18a / second inner ring part 18b / Abutment or support surface on the control arm.

You can see the outer ring 16 and the inner ring 18 designed so that the rolling elements 19 lie in an O arrangement. Now projects the support directions, as shown by the dashed lines A, in the rolling bearing 14 and there on the bearing axis L, which is formed by the clamping screw not shown in detail, so there is a very wide support base S, as shown by the double arrow.

As a result of this support base, the torques around the y- and / or z-axis are transmitted via the articulated connection over a large axial length 4 supported. This support offers the possibility to absorb very high moments. The support base itself is obviously wider than the geometric width of the bearing. The rolling bearing 14 builds narrower than it is able to support.

While 2 a symmetrical design of the rolling bearing 14 shows, shows 3 an asymmetrical design of the rolling bearing also designed here as a tapered roller bearing 14 ,

This also has an outer ring 16 on, which also here essentially has a V-shaped cross-sectional shape and in the receptacle 15 of the wheel bearing carrier 2 , which is profiled in this area accordingly, is included.

Also provided is an inner ring 18 , which also consists of two inner ring parts 18a and 18b which, in turn, is preferably one fold forming parts is.

The inner ring 18 is again via a clamping screw shown here 22 with the wishbone 5 in the local screw receptacle 20 screwed. About the clamping screw 22 Here, too, the tension of the rolling bearing 14 ,

The tension is here in contrast to 2 - in the sense of power flow - equal to a parallel connection of the inner ring parts 18a . 18b accomplished. When tightening the clamping screw, the head of the clamping screw is first on the inner ring part 18a and transmits the forces on the rolling elements and the inner ring part 18b on the abutment on the wishbone. Upon further tightening of the clamping screw comes the head of the clamping screw 22 on the cylindrical band of the inner ring 18b to the plant. Upon further tightening, there is a parallel connection of the over the inner ring parts 18a . 18b on the abutment on the transverse bearing forces transmitted.

Obviously, an asymmetric bearing design is realized here after the two inner ring parts 18a and 18b different geometry are.

While the 2 and 3 each describe embodiments in which the respective outer ring 16 always with the wheel bearing carrier 2 connected, it would be equally conceivable the outer ring 16 with the wishbone 5 , which then has a corresponding ring receptacle to connect and the respective inner ring 18 with the wheel bearing carrier 2 , which then has a corresponding screw receptacle to screw about a clamping screw.

Finally, it should be noted that the rolling bearing 14 Of course, it can be sealed on both sides. On the open side, this can for example by means of a bearing cap, in the outer ring 16 or in the recording 15 is caulked on the wheel bearing carrier, be realized while in the area to the wishbone 5 towards a suitable sealing element not shown here can be arranged.

apparent Thus, using a inventively provided bearing with sliding or rolling bearing sections in O arrangement an extremely effective support around the vertical and transverse axes (z and y axis) can be achieved, the axially required Space is not too big, so that with particular advantage the steering angle as a result of use not the bearing of the invention impaired becomes.

D. h., larger maximum Steering angle with the same realized stiffness compared to the State of the art can be realized or greater rigidity at given maximum steering angle.

The Use of a bearing in O arrangement forms one as described very wide support - at the same time narrow construction -, in particular the use of a rolling bearing, in particular in the form of a tapered roller bearing, is preferred because such bearings have very high load ratings and usually have low friction moments, so that the response is sensitive. Execution the respective bearing rings as simple forming parts of the Furthermore, a cost-effective storage production to.

1

Swivel wheel bearing unit

2

Wheel carrier

3

Upper admission

4

articulation

5

wishbone

6

bearing seat

7

Wheel bearings

8th

outer ring

9

pivot

10

inner ring

11

rolling elements

12

brake disc

13

drive shaft

14

roller bearing

15

bearing seat

16

outer ring

17

inside

18

inner ring

19

rolling elements

20

screw receptacle

21

bearing surface

22

clamping screw

L

bearing axle

S

support base

X axis

y-axis

(Horizontal axis)

z-axis

(Vertical axis)

Claims (11)

Wheel bearing unit of a motor vehicle, comprising a wheel bearing carrier and a wishbone hingedly connected thereto in the manner of a hinge joint, characterized in that the articulated connection ( 4 ) by means of a sliding or rolling bearing ( 14 ) is formed in O arrangement. Wheel bearing unit according to claim 1, characterized in that the rolling bearing ( 14 ) is a tapered roller bearing, a Schrägtonnenlager or angular contact ball bearings. Wheel bearing unit according to claim 2, characterized in that the tapered roller bearing kegelför having mige or cylindrical rolling elements. Wheel bearing unit according to at least one of the preceding claims, characterized in that the sliding or rolling bearing ( 14 ) an inner ring ( 18 ), which via a bearing axis (L) forming the clamping screw ( 22 ) with the wheel bearing carrier ( 2 ) or the wishbone ( 5 ) connected is. Wheel bearing unit according to claim 4, characterized in that the inner ring ( 18 ) via the clamping screw ( 22 ) relative to the outer ring ( 16 ) is clamped to produce a bearing preload. Wheel bearing unit according to at least one of the preceding claims, characterized in that the inner ring ( 18 ) is a one-part forming part, or of two inner ring parts ( 18a . 18b ), which are each formed parts. Wheel bearing unit according to at least one of the preceding claims, characterized in that the sliding or roller bearing ( 14 ), in particular the oblique roll, skew-barrel or ball-bearing, is a symmetrical or asymmetrical bearing. Wheel bearing unit according to at least one of the preceding Claims, characterized in that the wheel bearing carrier is arranged sprung Wheel bearing unit according to at least one of the preceding Claims, characterized in that the wheel bearing carrier in such a way with a wheel bearing connected is that the wheel bearing carrier at a pivoting the wheel bearing and / or a Radverschwenkung not mitverschwenkt becomes. Wheel bearing unit according to claim 9, characterized in that on the wheel bearing carrier ( 2 ) Bearing mounts ( 6 ) and at the wheel bearing ( 7 ), in particular on an outer ring ( 8th ) of the wheel bearing ( 7 ), Bearing journals ( 9 ), which bearing receptacles ( 6 ) and journals ( 9 ) are interconnected such that the wheel bearing ( 7 ) about a vertical axis z pivotally relative to the wheel bearing carrier ( 2 ) is stored. Wheel bearing unit according to claim 9 or 10, characterized in that the bearing receptacles ( 6 ) and the journals ( 9 ) are arranged such that a vertical axis z formed thereby passes through a wheel supported by the wheel bearing.