DE102006055293A1 - Bearing arrangement for independent suspension with adjustment mechanism for active lane adjustment - Google Patents

Abstract

The invention relates to a bearing bush arrangement for an independent wheel suspension (1) of a motor vehicle with a bearing bush (16) rotatably connecting a steering wheel (2) to a wheel carrier (7) of the independent wheel suspension and an adjusting mechanism actuated by an actuator (24) by a relative distance in Vehicle transverse direction (y) between the wheel carrier (7) and the handlebar (2) is adjustable by means of the bearing bush.

Description

The The present invention is in the field of suspension technology and relates to a bearing bushing arrangement for an independent suspension of a Motor vehicle with a bearing bush for the storage of a Radträgerlenkers on the wheel carrier and a cooperating with the bearing bush adjustment mechanism for active track adjustment.

State of the art

In a conventional one independent suspension can through the use of a hinged on the wheel guide arm the track of the rear wheel when rebounding and rebounding, as well as when it occurs of longitudinal and lateral forces be specified. The track adjustment depends in particular from the axle geometry and the forces acting on the rear wheel.

generally known can by the track adjustment of the rear wheels, the self-steering behavior of the motor vehicle, so that the vehicle in particular while cornering or when braking can be stabilized. For example, can the occurrence of vehicle instability under load changes or at a braking on a roadway with different coefficients of friction characterized counteracted that the rear wheels when driving straight or cornering be brought into toe.

In In practice, it is necessary to the track control caused by track control the rear wheels to adapt certain, typically occurring driving situations, as exemplified above. However, in it can be different driving situations, in particular at a different driving speed, the driving experience and / or driving safety through the track adjustment in unwanted Way impaired become.

Around To fix this problem, an "active" track adjustment is necessary as a "passive" track adjustment by means of a track link no driving situation-dependent, in particular speed-sensitive, variability the track adjustment allowed.

task

In contrast there is the object of the present invention is a driving situation-dependent, in particular speed-sensitive, variability the track adjustment in an independent suspension of a motor vehicle to enable to the problems associated with a passive lane adjustment to avoid.

These Task is according to the proposal of the invention by a bearing bush arrangement for one independent suspension a motor vehicle with the features of the independent claim solved. advantageous Embodiments of the invention are indicated by the features of the subclaims.

According to the invention is a Bushing arrangement for an independent suspension a motor vehicle shown. The independent suspension is used for Mehrfachanlenkung a wheel carrier at the vehicle substructure, possibly with the interposition of a Subframe.

The Inventive bearing bush arrangement comprises a bearing bush, which a link for articulating the wheel carrier on Vehicle underbody, possibly with the interposition of a subframe, with the wheel carrier the independent suspension rotatable (in particular pivotable) connects. For example, includes the bushing for this purpose two together by an elastic material connected, concentric sleeves, one of them with the wheel carrier and the other connected to the handlebar at respective connecting portions is.

Farther comprises the bearing bush arrangement according to the invention an actuatable by an actuator and with the bearing bush cooperating adjusting mechanism, through a relative distance in the vehicle transverse direction between the wheel and the handlebar by means of the bearing bush is adjustable.

For example For this purpose, an adjustment mechanism is provided by the the connecting portions, which are two by an elastic material interconnected, concentric sleeves with wheel carrier and Connect the handlebar, be moved in the vehicle transverse direction relative to each other can.

Provided, that cooperating with the adjusting mechanism (adjustable) Bushing in the vehicle longitudinal direction offset from a track adjustment axis of the wheel carrier is arranged, is through a change the relative distance in the vehicle transverse direction between the handlebar and wheel carrier at the same time causes the wheel carrier to the Spurverstellachse is rotated, so by changing the relative distance in vehicle transverse direction between the handlebar and wheel carrier the Track of the wheel carrier (or Rads) changed can be.

According to the invention can therefore advantageously the track of the wheel carrier (or wheel) according to a particular driving situation in the desired manner by means of the bearing bush and the adjustable by an actuator and cooperating with the bearing bush adjustment mechanism be actively adjusted to thereby increase the driving safety and improve the driving feel in the desired manner in all the driving situations occurring. In particular, a swerving of the vehicle can be prevented or delayed with a correspondingly fast control. Furthermore, intervention of an ESP control may be delayed or prevented (ESP = Electronic Stability Program).

at The actuator may in particular be an electromechanical or electro-hydraulic adjustment mechanism. Advantageous is the actuator to press of cooperating with the bearing bush adjustment mechanism in the bearing bush integrated.

at an advantageous embodiment of the bearing bush arrangement according to the invention can by the cooperating with the bearing bush adjustment mechanism a relative distance in the vehicle transverse direction between a rotation axis the bushing around which the handlebar connected to the bearing bush is rotatable, and the wheel carrier be adjusted.

Especially, but not exclusively, In the above-mentioned case, the adjusting mechanism comprises in an advantageous manner Way an eccentric mechanism which the wheel carrier or alternatively handlebar in a horizontal axis of rotation of the bearing bush Direction (that is in vehicle transverse direction) with the bearing bush (mechanical) coupled and in a direction perpendicular to the axis of rotation of the bearing bush vertical direction (this means in the direction of the vehicle height) (mechanical) not coupled (decoupled).

The Locations of the bushing arrangement relate to the ordinary Installation position of the bearing bush in the independent suspension of one on a horizontal Roadway located motor vehicle, wherein the axis of rotation the bushing substantially parallel to the vehicle longitudinal direction is.

For example includes such an eccentric mechanism for mechanical coupling of the wheel carrier or alternatively the handlebar in (horizontal) vehicle transverse direction with the bearing bush at least one eccentric (outside its center of gravity) rotatably mounted disc ("eccentric disc"), which within a recess slidably disposed.

For example the eccentric disc is connected to the bearing bush for this purpose, while the slot within a connected to the handlebar device or formed by the handlebar shaped handlebar section. alternative could the Eccentric disc to be connected to the handlebar while the slot inside a component connected to the bearing bush or of the bearing bush molded bearing bush section is shaped. A coupling of wheel carrier or alternatively handlebar and bushing is thus only by slidably guided in the slot Eccentric. The example, oval or rectangular shaped slot includes in ordinary Way a long (or longest) and a short (or shortest) Dimension.

to Achieving the desired Coupling properties, the slot is oriented so that its long (or longest) Dimension substantially in the direction of the vehicle height (vertical) and its short (or shortest) Dimension oriented essentially in the vehicle transverse direction (horizontal) is. In addition, the slot is sized so that its long (or longest) Dimension longer than the eccentric is, in such a way that the eccentric rotatable mounted eccentric disc can perform a full turn (360 °), without this in the vertical direction, a force on the slot exercise forming structure or component. Will the distance between the eccentric pivot of the eccentric disc and its center of gravity as eccentricity e, so it means that in the vertical direction oriented long (or longest) dimension the slot at least twice the eccentricity e longer than the corresponding dimension of the eccentric disc in the vertical direction is. On the other hand, the slot is sized so that its short (or shortest) Dimension of the dimension of the eccentric disc in the vehicle transverse direction corresponds, so if the rotatably mounted eccentric a full turn (360 °), in Vehicle transverse direction for coupling bearing bush and handlebar or alternatively wheel carrier always a force on the elongated hole forming structure or component the eccentric disc is exercised. Advantageously, each end face of the bearing bush a so eccentric disc arranged.

The Invention also extends to an independent suspension with a bearing bush arrangement as described above.

Of Furthermore, the invention extends to a motor vehicle, the with such independent suspensions Is provided.

embodiment

The Invention will now be explained in more detail with reference to an embodiment, wherein Reference to the attached Drawings is taken. Show it

1 a schematic perspective View obliquely from above of an independent suspension for a rear wheel of a motor vehicle with a bearing bush arrangement according to the invention with an adjustable bearing bush for mounting the wheel carrier to an H-arm handlebar;

2 a schematic perspective view obliquely from above on the bearing bushing arrangement of the adjustable bearing bush for mounting the wheel carrier on the H-arm arm of 1 ;

3 a sectional view of the bearing bush arrangement of 2 according to section line AA;

4 a sectional view of the bearing bush arrangement of 2 according to section line BB;

5 a schematic perspective view obliquely from above on the bearing bushing arrangement of 2 without eccentric disc and slider;

6 a schematic perspective side view of the bearing bush arrangement of 2 without eccentric disc and slider;

7 Sectional views of the bearing bush arrangement of 2 according to section line AA with rotated by 180 ° relative to each other eccentric discs.

First, reference is made 1 taken, wherein a schematic perspective view of an independent suspension for a rear wheel of a motor vehicle is shown with a Lagerbuchsenanorndung with an adjustable bearing bush for mounting the wheel carrier on a H-arm handlebar.

Accordingly comprises an independent suspension for a rear wheel of a motor vehicle, which in total with the reference number 1 is designated a total of the reference number 2 designated lower H-arm arm, which consists of a substantially in the vehicle longitudinal direction (x) extending trailing arm section 3 and a substantially in the vehicle transverse direction (y) extending wishbone section 4 is composed.

The H-arm handlebar 2 is with its trailing arm section 3 by means of two link bearings on a wheel carrier 7 pivotally mounted, namely designed as a bearing bush first link bearing 6 and designed as a bearing bush or joint second link bearing 5 , About the wishbone section 4 is the H-arm handlebar 2 on the vehicle side with a trained example as a bearing bush or joint arm bearing on the subframe 8th (Or alternatively on the vehicle body) about a substantially parallel to the vehicle longitudinal direction (x) lying pivot axis mounted pivotally (in 1 not shown). The vehicle-side arm bearing of the wishbone section 4 allows an inclusion or rebound movement of the rear wheel. The subframe 8th is rigid or elastic over a plurality of bushings 9 on in 1 not shown substructure of the vehicle body stored.

In the independent suspension of 1 has the trailing arm section 3 of the H-arm handlebar 2 a curved room shape. It is about a trained example as a bearing bush or joint arm bearing 10 stored on the vehicle body of the vehicle body. Due to the special shape of the trailing arm section 3 of the H-arm handlebar 2 is the pivot axis of the link bearing 10 directed so that it is employed in the direction of the vehicle outside, so occupies a non-zero angle to the vehicle longitudinal direction (x). Due to this special shape of the trailing arm section 3 and in particular the position of the pivot axis of the link bearing 10 and its extension direction in the vehicle longitudinal direction (x), and a compliance of the wishbone section 4 , can be achieved in an advantageous manner that when exposed to longitudinal and lateral forces a displacement of the center of the wheel carrier 7 to the rear, with the result that the rear wheel is pressed in toe. Advantageously, it can be counteracted by this passive adjustment of the rear wheel of a Nachspurverstellung the rear wheel.

The independent suspension 1 from 1 further comprises an upper wishbone 11 which extends substantially in the vehicle transverse direction (y). Towards the center of the vehicle is the upper wishbone 11 via an example designed as an elastic bushing or joint arm bearing 12 on the subframe 8th pivoted. The handlebar bearing 12 allows a pivoting movement of the upper arm 11 about a substantially parallel to the vehicle longitudinal direction (x) lying pivot axis, so that an input or rebound movement of the rear wheel is possible. Radträgerseitig is the upper wishbone 11 by a running example, as a bearing bush or joint arm bearing 13 on the wheel carrier 7 pivoted.

The wheel carrier side arm bearing 13 of the upper control arm 11 and the wheel carrier side second link bearing 5 of the H-arm handlebar 2 Together form a Vorspurverstellachse 14 , As indicated by the arrow, can by pivoting the wheel carrier to the Vorspurverstellachse 14 the toe of the rear wheel are adjusted. Although not shown in the embodiment shown, it is inventively preferred if the radträgersei tiger handlebar bearing 13 of the upper control arm 11 and the wheel carrier side second link bearing 5 of the H-arm handlebar 2 are arranged in alignment approximately in a vertical line, so that the Vorspurverstellachse 14 is directed approximately vertically, with the result that the toe of the rear wheel without simultaneous generation or change of camber is adjustable.

In the independent suspension of 1 includes the wheel carrier side first link bearing 6 of the H-arm handlebar 2 an adjustable by means of an adjusting bearing bush 16 with integrated actuator. For articulation to the wheel carrier 7 becomes the with the trailing arm section 3 of the H-arm handlebar 2 rigidly connected bearing bush 16 of forks 44 . 45 a fork section 15 held over a Radträgerstrebe 17 rigid with the wheel carrier 7 connected is. Using the handlebar bearing 6 is the wheel carrier 7 pivotable about an approximately in the vehicle longitudinal direction (x) extending pivot axis.

By the adjustable by means of the adjustment bearing bush 16 with integrated actuator for actuating the adjusting mechanism, the distance in the vehicle transverse direction (y) between the trailing arm section 3 of the H-arm handlebar 2 and the wheel carrier 7 be changed, as in 1 illustrated by the double arrow. If the distance in the vehicle transverse direction (y) between the trailing arm section 3 of the H-arm handlebar 2 and the wheel carrier 7 is changed, at the same time the wheel carrier 7 around the toe adjustment axis 14 turned so that the toe can be adjusted.

The adjusting mechanism is an eccentric mechanism driven by an electric motor for coupling the wheel carrier 7 with the bearing bush 16 which is described below with reference to the 2 to 7 is explained in more detail.

The bearing bush 16 includes a rigid with the trailing arm section 3 of the H-arm handlebar 2 connected outer sleeve 18 , an inner sleeve 19 and one between the outer sleeve 18 and the inner sleeve 19 arranged elastic rubber layer 20 , which serves in a conventional manner to allow concentric rotational movements of outer and inner sleeves.

Inside the inner sleeve 19 is one with a flange section 46 provided hollow shaft 21 provided, which via pivot bearings 22 rotatable on a clamping sleeve 23 is stored.

Between the inner sleeve 19 and the clamping sleeve 23 there is an electric motor 24 whose stator is connected to the inner sleeve 19 rigidly connected and its rotor with the hollow shaft 21 is rigidly connected. Using the electric motor 24 can the hollow shaft 21 in a rotational movement around the clamping sleeve 23 be offset.

The hollow shaft 21 is over its flange section 46 with a transmission gear 25 , For example, a planetary gear or a so-called harmonic drive gear, rigidly connected, which in turn via a connection structure 27 rigid with a first eccentric disc 26 connected is. The transmission gearbox 25 usually serves to reduce the rotational speeds of the electric motor ("reduction"), so that the first eccentric disc 26 can be rotated or positioned very accurately with a relatively low speed.

The first eccentric disc 26 is at a connecting section 28 positive, force or frictionally engaged with the clamping sleeve 23 connected, giving a torque of the first eccentric disc 26 on the clamping sleeve 23 can be transferred. Because the clamping sleeve 23 further at a connecting portion 29 with a second eccentric disc 30 is positively, positively or frictionally connected, is a torque of the first eccentric 26 over the clamping sleeve 23 also on the second eccentric disc 30 transfer. One for transmitting the torque from the first eccentric disc 26 on the second eccentric disc 30 required preload is through a through the two eccentric discs 26 . 30 and the clamping sleeve 23 penetrating clamping screw 31 which by a nut 32 secured, guaranteed. Thus, both eccentric discs 26 . 30 through the electric motor 24 be driven (rotated) in synchronism. A rotation axis of the two eccentric discs 26 . 30 is here by the central axis 35 the clamping screw 31 specified.

To the two eccentric discs 26 . 30 with the clamping screw 31 and the nut 32 to be able to brace, are in the two eccentric discs 26 . 30 each non-centered (eccentric) to the disk center points arranged hollow cylindrical holes 33 . 34 provided by which the clamping screw 31 is guided through. Due to the eccentric position of the holes 33 . 34 be the two eccentric discs 26 . 30 not about their respective focal points (centers), but rotated about eccentric pivot points.

The two eccentric discs 26 . 30 are by means of pivot bearings 36 . 41 each with sliders 37 . 38 connected, which in oblong holes 39 . 40 run, in turn, in the forks 44 . 45 of the fork section 15 the wheel carrier strut 17 are formed.

As in particular by the two 3 and 4 can be seen is, are the oval slots 39 . 40 each formed so that they extend with their long dimension substantially in the vertical z-direction (in the direction of the vehicle height) and with their short dimension substantially in the horizontal y-direction (in the vehicle transverse direction). Here, the length of the long dimension of the slot corresponds at least to the sum of the diameter of the eccentric disc with slider and the double eccentricity. On the other hand, the length of the short dimension of the slot corresponds to the diameter of the eccentric disc with slider. In this respect, the two eccentric discs 26 . 30 with their respective sliders 37 . 38 in each case in the associated slots 39 . 40 fitted in that they have the slots 39 . 40 fill in the horizontal y-direction (in the vehicle transverse direction), but in the vertical z-direction (in the direction of the vehicle height) can be moved with play.

From the forks 44 . 45 each support noses 42 . 43 from, which up to the inner sleeve 19 rich, the inner sleeve 19 support, and thus the trailing arm section 3 of the H-arm handlebar 2 against the wheel carrier 17 in the vertical z-direction (in the direction of the vehicle height) support.

In 5 is a schematic perspective view obliquely from above on the bearing bushing arrangement of 2 without eccentric disc 30 , Pivot bearing 36 and slider 38 shown. This is the result in the fork 45 recessed slot 40 recognizable in which the slider 38 the eccentric disc 30 is movable in the vertical z-direction. In addition, those of the fork 45 protruding column nose 43 and the inner sleeve 19 recognizable.

6 shows a schematic perspective side view of the bearing bush arrangement of 2 without eccentric disc 30 , Pivot bearing 36 and slider 38 so that's in the fork 45 recessed slot 40 that from the fork 45 protruding support noses 43 and the inner sleeve 19 are recognizable. Moreover, in 6 the marked with the letter e eccentricity of the pivot bearing of the eccentric disc 30 located.

In 7 are two different sectional views of the bearing bush arrangement of 2 shown according to the section line AA. The two sectional views differ in that the eccentric discs 26 . 30 are rotated in synchronism by 180 ° relative to each other. Due to the eccentric bearing of the two eccentric discs 26 . 30 with the eccentricity e are the eccentric discs 26 . 30 with a rotation of 180 ° each by twice the eccentricity 2e shifted in the y-direction (essentially in the vehicle transverse direction). Because the eccentric discs 26 . 30 in the oblong holes 39 . 40 in the y-direction in each case completely rest, this displacement in the y-direction of the eccentric discs 26 . 30 around the route 2e completely on the wheel carrier strut 17 transfer. A shift in the Radträgerstrebe 17 in z-direction (in the direction of the vehicle height) does not take place here, since a corresponding movement of the eccentric discs 26 . 30 through the oblong holes 39 . 40 is recorded.

1

independent suspension

2

H-arm link

3

Trailing arm section

4

Wishbone section

5

link bearings

6

link bearings

7

wheel carrier

8th

subframe

9

bearing bush

10

link bearings

11

wishbone

12

link bearings

13

link bearings

14

Vorspurverstellachse

15

fork portion

16

bearing bush

17

Radträgerstrebe

18

outer sleeve

19

inner sleeve

20

rubber layer

21

hollow shaft

22

pivot bearing

23

clamping sleeve

24

electric motor

25

up gear

26

eccentric

27

connecting structure

28

connecting portion

29

connecting portion

30

eccentric

31

clamping screw

32

nut

33

drilling

34

drilling

35

central axis

36

pivot bearing

37

slide

38

slide

39

Long hole

40

Long hole

41

pivot bearing

42

support lug

43

support lug

44

fork

45

fork

46

flange

Claims (13)

Bearing arrangement for a single wheel suspension ( 1 ) of a motor vehicle with a handlebar ( 2 ) with a wheel carrier ( 7 ) of the independent suspension rotatably connecting bearing bush ( 16 ) and one of an actuator ( 24 ) operable adjusting mechanism by the a relative distance in the vehicle transverse direction (y) between the wheel carrier ( 7 ) and the handlebar ( 2 ) is adjustable by means of the bearing bush. Bearing arrangement according to claim 1, wherein the actuator is an electro-mechanical or electro-hydraulic Actuator is. Bearing arrangement according to one of claims 1 to 2, wherein the actuator ( 24 ) in the bushing ( 16 ) is integrated. Bearing arrangement according to one of claims 1 to 3, wherein by the Verstellmechanimsus a relative distance in the vehicle transverse direction (y) between an axis of rotation ( 35 ) of the bearing bush ( 16 ) and the wheel carrier ( 7 ) can be adjusted. Bearing arrangement according to one of claims 1 to 4, wherein the adjusting mechanism comprises a motor-driven eccentric mechanism ( 21 . 22 . 25 . 27 . 26 . 41 . 37 . 39 . 44 . 23 . 30 . 36 . 38 . 40 . 45 ), which the wheel carrier ( 7 ) or handlebars ( 2 ) in the vehicle transverse direction (y) with the bearing bush ( 16 ) and the wheel carrier ( 7 ) or handlebars ( 2 ) in the direction of the vehicle height (z) from the bearing bush ( 16 ) decoupled. Bearing arrangement according to claim 5, wherein the eccentric two eccentrically rotatably mounted and actuated by the actuator eccentric discs ( 26 . 30 ) which, within the other, consists of wheel carriers ( 7 ) or handlebars ( 2 ) shaped recesses ( 39 . 40 ) are arranged, wherein the recesses are shaped so that the eccentric discs ( 26 . 30 ) abut the recesses in the vehicle transverse direction (y) and in the direction of the vehicle height (z) within the recesses can be moved with play. Bearing arrangement according to claim 6, wherein the eccentric discs ( 26 . 30 ) via a rotary connecting element ( 23 ) are rotatably connected to each other. Bearing arrangement according to one of claims 6 to 7, wherein the recesses ( 39 . 40 ) within a fork-shaped fork portion ( 15 ) of the wheel carrier ( 7 ) or handlebar ( 2 ) are formed. Bearing arrangement according to one of claims 6 to 8, wherein the recesses ( 39 . 40 ) are formed in the form of elongated holes. Bearing arrangement according to one of claims 1 to 9, wherein the handlebar ( 2 ) on a rearwardly extending Radträgerstrebe ( 17 ) on the wheel carrier ( 7 ) is articulated. Bearing arrangement according to one of claims 1 to 10, wherein the handlebar a H-arm handlebar with a substantially in the vehicle longitudinal direction (x) extending trailing arm section ( 3 ) and at least one substantially in the vehicle transverse direction (y) extending wishbone section ( 4 ). independent suspension with a bearing bush arrangement according to one of claims 1 to 11th Motor vehicle with independent wheel suspensions according to claim 12.