ADJUSTING UNIT AND SETTING DEVICE FOR SETTING A RELATIVE POSITION OF COMPONENTLY LOCATED COMPONENTS

Description

[0001] The invention relates to an adjustment unit of the type specified in the preamble of claim 1 and to an adjustment device for adjusting a relative position of components mounted against each other according to claim 7.

[0002] A vehicle's chassis is a complex system of components that connect the vehicle body to the road surface via the wheels. Typically, each wheel is connected to the vehicle body via multiple control arms, allowing for relative movement between the body and the wheel. These control arms are usually attached to the wheel via bearings. On the body side, the control arms can be connected to the body, a component attached to the body, or a steering gear via bearings. Specifically, the control arms serve as a connection that enables correct wheel alignment relative to the vehicle body, ensuring safe and comfortable handling. Adjusting the position of the control arms, particularly the body-side bearings, in the lateral direction of the vehicle allows for adjustments to the toe or camber over the suspension travel.

[0003] Adjustment devices for toe or camber adjustment of chassis or wheel suspensions of motor vehicles are known. For the prior art, reference is made to DE 41 15 110 C2, DE 44 37 661 A1, US 5 398 411 A and EP 2 783 947 A1, from which adjustment devices are known in which a bearing of a control arm is fastened in a double-shear bearing holder or between two support arms using a bearing bolt and a nut, wherein the bearing bolt is mounted in an elongated hole of the respective support arm. Guides are located on both sides of the elongated holes on the support arms, between which a spacer element, in particular an eccentric disc, is arranged. To adjust the control arm, the bearing bolt can be moved or rotated within the elongated holes after loosening a nut or the like.can be adjusted, causing a displacement of the bearing in the transverse direction of the vehicle, for example to effect a relative movement between a steering linkage and a section of the body or a wheel carrier.

[0004] Document US 5 398 411 A discloses an adjustment unit according to the preamble of claim 1.

[0005] EP 1 932 692 A1 discloses a joint device for connecting a steering linkage to a vehicle body, comprising a rubber-metal bearing through which a bearing pin is inserted, the longitudinal axis of which defines the joint axis. The steering linkage is bolted to the vehicle body via two mounting sections, each having an elongated hole and formed integrally with the bearing pin. The mounting sections extend in a plane inclined at a predetermined angle to the joint axis. A spacer element, designed as a cam element, is arranged in one of the elongated holes. The relative position of the steering linkage to the vehicle body can be adjusted by rotating the spacer element.

[0006] DE 10 2015 016 493 A1 discloses a bearing arrangement for a vehicle's wheel suspension, in which a control arm is articulated about a pivot axis on a vehicle body, e.g., a subframe, by means of a rubber-metal bearing. The rubber-metal bearing is mounted in a control arm bracket designed as a separate component, which is connected to the vehicle body via a connecting flange and screw connections to an adjusting unit. The screws pass through elongated holes on the subframe side, the longitudinal extent of which defines an adjustment direction of the pivot axis, in particular for adjusting the camber behavior of the wheel suspension relative to the body-side supporting structure.

[0007] German patent DE 102014 201 876 A1 relates to an adjustment device for the toe and / or camber adjustment of a wheel guidance element, which is connected via a bearing on one side to the vehicle body and on the other side to a wheel carrier of a wheel of the motor vehicle. One of the respective bearings has an adjustment element designed as an eccentric, which has an eccentric shaft adjustable by means of an actuator. Individual wheel adjustment is possible by rotating the eccentric shaft.

[0008] German patent application DE 10 2014 226 536 A1 describes a two-part control arm for a vehicle's wheel suspension. The two control arm sections are connected to each other via fasteners and a length adjustment device. The length adjustment device is an eccentric screw that passes through an elongated hole in each control arm section. A spacer element, such as an eccentric washer, is located at the elongated hole and guided in a guide. When the eccentric screw is turned, the positive guidance causes the screw shaft to shift in or against the longitudinal axis of the control arm, thus changing the relative position of the two control arm sections. The length of the control arm can therefore be adjusted to set the toe and / or camber.

[0009] WO 2016 041 706 A1 discloses a track rod or steering linkage for a vehicle, comprising a tube connected to a joint via an adjusting sleeve. The adjusting sleeve is screwed into the end of the tube in a first direction of rotation and screwed to a shaft of the joint via an internal thread running in the opposite direction to this first direction of rotation. By rotating the adjusting sleeve relative to the tube and the shaft, axial adjustment of the tube relative to the joint is possible. The adjusting sleeve has a meandering or sinusoidal slot extending in the axial direction. A clamp presses the end of the tube, with the adjusting sleeve interposed, against the outer circumference of the shaft. This fixes the tube, the adjusting sleeve, and the shaft in their relative positions.

[0010] German patent application DE 10 2015 101 438 A1 describes an adjustment device. A spacer assembly, adjustable via a spacer element, comprises a joint with a bushing bearing enclosed by two bearing lugs. The bushing bearing has a through-hole arranged concentrically to the bearing axis. A spacer element, designed as a cam, is received in the through-hole and has a continuous cam bore whose cam axis is eccentric to the bearing axis. A screw located in the cam bore penetrates the bearing lugs and engages with the cam bore in such a way that rotation of the screw about the first cam axis causes the cam in the bushing to rotate about the bearing axis. In this way, the bearing lugs move relative to the bearing axis, thereby allowing the distance between the components of the assembly to be adjusted.

[0011] DE 33 29 350 A1 discloses a device for adjusting the camber of a McPherson strut suspension, in which the steering knuckle is held between mounting flanges by two bolted connections. One of these bolted connections is designed as an adjustment device. The camber is adjusted by means of a nut that is positively engaged in a bore running obliquely through the steering knuckle. The adjustment mechanism is thus based on the specific geometry of the steering knuckle and the interaction of the nut, bolt, and bore.

[0012] The disadvantage of adjustment mechanisms is that they are usually component-intensive and expensive designs, often integrated into complex welded structures, resulting in limited flexibility. Furthermore, they are typically installed in hard-to-reach areas with limited space, where many different components are housed, making assembly difficult.

[0013] The invention is based on the objective of further developing an adjustment unit of the type specified in the preamble of claim 1 in such a way as to reduce the disadvantages of the previously known solutions.

[0014] This problem is solved by the characterizing features of claim 1 in conjunction with its preamble features and by claim 7.

[0015] Furthermore, the invention relates to an adjustment device for adjusting the distance between components mounted against each other according to claim 7.

[0016] The dependent claims constitute advantageous further developments of the invention.

[0017] In a known manner and according to the invention, an adjustment unit comprises a rubber-metal bearing having an inner core extending along the bearing axis of the rubber-metal bearing. The inner core has a passage extending longitudinally along the inner core, which serves to receive a bearing bolt, which may, for example, be designed as a screw with a partial thread.

[0018] According to the invention, an adjustable spacer element is arranged in the embodiment. The spacer element can, for example, be designed as a cam element. The spacer element has an opening that is also designed to receive the bearing pin. In the installed state of the rubber-metal bearing, the bearing pin passes through the inner core and the spacer element. The spacer element extends along a longitudinal axis that defines a connection axis of the rubber-metal bearing and extends parallel to the bearing axis.

[0019] By adjusting the spacer element, the connecting axis and the bearing axis can be adjusted relative to each other. For example, rotating the bearing bolt around its longitudinal axis causes the connecting axis to be adjusted relative to the bearing axis, or conversely, the connecting axis to rotate around the bearing axis. This results in an adjustment of the bearing position. In this way, for example, a rubber-metal bearing used to connect a control arm to a subframe can be adjusted, particularly laterally, to adjust the toe and / or camber.

[0020] The spacer element is movably arranged in the direction of extension of the bushing. In the installed state of the bearing, the spacer element is axially adjusted linearly along the connection axis, causing a deflection of the inner core transversely to the connection axis. The inner core of the rubber-metal bearing extends coaxially to the bearing axis, which is essentially arranged in a plane parallel to the connection axis. The spacer element is linearly movable within the bushing of the inner core along the longitudinal axis of the bushing. Simultaneously, in the installed state of the adjustment unit, the spacer element moves linearly along the connection axis. This linear movement of the spacer element causes a translational deflection of the inner core transversely to the connection axis.In other words, the linear movement of the spacer element causes a translational displacement of the bearing axis and thus of the entire rubber-metal bearing within the plane. This translational displacement of the inner core allows the entire rubber-metal bearing to be moved over an adjustment path extending perpendicular to the connection axis.

[0021] The adjustment unit can be used, for example, as a bearing for connecting components. Consequently, the relative position of these components can be varied via the adjustment unit. Thus, the adjustment unit can be used, for example, to compensate for production-related tolerances between components mounted against each other or to adjust wheel alignment parameters.

[0022] The adjustment unit advantageously has a small installation space requirement, which corresponds to the installation space requirement of a conventional bearing.

[0023] Furthermore, the adjustment unit can be retrofitted into joints. For example, a conventional rubber-metal bearing pressed into a joint can be replaced by the adjustment unit. The adjustment unit can be marketed, for example, as an optional extra or as a suspension tuning kit.

[0024] According to a preferred embodiment, the spacer element is arranged in the inner core in a rotationally fixed manner. The spacer element is located in the opening of the inner core and can have a shorter longitudinal extent than the opening. The opening and the spacer element can have an essentially complementary shape to each other, which prevents rotation of the spacer element relative to the inner core. For example, the opening and the spacer element each have a hexagonal shape, with the opening and the spacer element being precisely matched to each other. The spacer element can, for example, be designed as a standard hexagonal nut, and the inner core can be formed with a hexagonal opening by an extrusion process. Advantageously, the adjustment unit is inexpensive and can be manufactured with minimal effort.

[0025] It is also conceivable that the opening is designed as an essentially rectangular recess and the spacer element, for example, has a cube shape, with the spacer element having two parallel cube edges that are precisely aligned within the opening to prevent the spacer element from rotating relative to the opening. Furthermore, the spacer element is integrated into the inner core of the rubber-metal bearing in a space-saving manner and protected from dust and dirt.

[0026] According to a preferred embodiment, the inner core has a longitudinal axis that runs at an angle to the bearing axis. The inner core is geometrically designed such that it has a slope relative to the bearing axis. This means that the respective axes of the core and the rubber-metal bearing are arranged at an angle to each other, which can be, for example, 5° to 30°. The angle can particularly be 8°.

[0027] The inner core of the rubber-metal bearing can, for example, have the aforementioned hexagonal opening, designed such that its longitudinal axis runs at an angle to the bearing axis. The spacer element, which may have a shorter longitudinal extent than the opening, is linearly displaceable within the opening. In the installed state, the spacer element is linearly adjusted along the connection axis, which is defined by the opening of the spacer element. The positive guidance of the spacer element, both along the connection axis and within the opening, which extends at an angle to both the bearing axis and the connection axis, has the effect that a displacement of the spacer element deflects the inner core of the rubber-metal bearing translationally, with the direction of action being perpendicular to the connection axis.In other words, the linear adjustment of the spacer element causes a translational deflection of the inner core and thus of the entire bearing relative to the connecting axis.

[0028] According to an alternative embodiment, the spacer element is displaceable along at least one guide rail arranged on the inner core, the guide rail extending at an angle to the bearing axis in the longitudinal direction of the feedthrough. In this embodiment, the feedthrough can be designed, in particular, as a right-angled recess extending in the axial direction of the rubber-metal bearing. The feedthrough can be arranged coaxially to the bearing axis. A cube-shaped spacer element is, for example, arranged in the feedthrough in a rotationally secure manner relative to the inner core. A guide rail is arranged on the inner core, which, for example, is designed as a groove or the like to guide the spacer element. The guide rail can, for example, have a profile.

[0029] The guide rail extends longitudinally along the bushing at an angle to the bearing axis. This angle can be, for example, 8°. The spacer element is adjustable along the guide rail in the longitudinal direction of the bushing. Displacement of the spacer element along the guide rail, while simultaneously being guided along the connection axis, causes a translational deflection of the inner core of the rubber-metal bearing transversely to the connection axis. In this way, the entire rubber-metal bearing is displaced transversely to the connection axis.

[0030] Overall, the direction of the translational deflection of the inner core, and thus of the rubber-metal bearing, is perpendicular to the connection axis. Advantageously, the direction of action can be flexibly adjusted by changing the orientation of the adjustment unit or the alignment of the rubber-metal bearing of the adjustment unit.

[0031] The geometry of the inner core can be flexibly adapted to the requirements of the adjustment unit or the requirements of a joint connection. Thus, the adjustment unit can be used with particular flexibility by changing the inner core, i.e., by selecting the appropriate geometry of the inner core.

[0032] Preferably, the spacer element has at least one guide element that is received in the guide rail. The guide element can, for example, be designed as a guide pin or the like. The guide rail and the guide element can, for example, have complementary profiles. The guide element securely guides the linearly adjustable spacer element along the guide rail, and the spacer element is displaceable along the guide rail like a mounted carriage. The guide element displaces the bearing core translationally along the direction of action, i.e., transversely to the connection axis.

[0033] Preferably, the spacer element is designed with an internal thread. This internal thread engages, in particular, with an external thread of the bearing bolt, and the linear adjustment of the spacer element along the connection axis is effected by screwing the spacer element onto the bearing bolt. The spacer element has an internal thread that, in particular, has the same dimensions as an external thread of the bearing bolt to be accommodated. The internal thread can engage with the external thread in such a way that screwing the spacer element onto the bearing bolt causes a linear movement of the spacer element along the connection axis or longitudinal axis of the bearing bolt. The spacer element is simultaneously guided along the bearing bolt or along the connection axis and in the guide, which runs at an angle to the connection axis, thereby displacing the inner core.This results in a translational deflection of the inner core or bearing axis relative to the connecting axis.

[0034] Furthermore, the invention relates to an adjustment device for setting the relative position of two components mounted relative to each other, wherein one of the components has a bearing receptacle and the other a bearing holder. The bearing receptacle is encompassed in a manner known per se by the bearing holder arranged on the other component, which is designed as a double-shear connection, for example with fork-like support arms, receiving arms, bearing lugs, or the like. The adjustment unit comprises an adjustment unit, a bearing bolt, and a nut that can be screwed onto the bearing bolt.

[0035] According to the invention, the adjustment device comprises an adjustment unit as described above. The adjustment unit is designed with a rubber-metal bearing. The rubber-metal bearing is fixed in the bearing holder by means of the bearing bolt and nut. The bearing bolt, which can, for example, be designed as a screw with a partial thread, passes through the rubber-metal bearing, the spacer element, and the bearing holder and can be secured to the bearing holder by means of the screw-on nut. In the installed state of the adjustment device, the linear adjustment of the spacer element along the connecting axis causes a translational deflection of the inner core transverse to the connecting axis, thereby allowing the relative position of the mounted components to be adjusted.

[0036] The adjustment device advantageously allows for the setting of a relative position between opposing components over large adjustment ranges, while the installation space requirement of the adjustment device advantageously remains the same compared to a conventional double-shear bearing connection. Compared to adjustment devices known from the prior art, the adjustment device requires less installation space and is advantageously easy to mount in space-constrained, difficult-to-access areas.

[0037] The adjustment device can be used at any bearing point that has a double-shear joint or bearing connection. For example, it can be used to connect a drive unit to the subframe.

[0038] In particular, the adjustment device in the chassis can be used at kinematic points that have a double-shear joint or bearing connection. For example, a control arm can be connected to a subframe via the adjustment device, whereby the wheel position parameters, such as the toe and / or camber angle, can be influenced and adjusted via the adjustment device.

[0039] Due to the differently adjustable orientation or alignment of the bearing, the adjustment device is advantageously direction-independent. This makes it suitable, for example, for achieving different vehicle ride heights with identical wheel position parameters and the same gradients of change of the wheel position parameters over the suspension travel.

[0040] The adjustment device also allows for easy compensation of production-related tolerances in the components to be joined.

[0041] Furthermore, the adjustment device offers advantages in automated vehicle production. For example, with automated axle adjustment, the translational deflection of a screw-fitting machine is eliminated, thus reducing assembly time.

[0042] The adjustment mechanism and the calibration unit allow for a high degree of flexibility in the development of, for example, a vehicle or similar product. For instance, if design changes are made, such as to the components being joined, the direction of travel of the adjustment mechanism can be easily changed by altering the bearing orientation. Furthermore, only the inner core of the calibration unit's bearing needs to be modified, without altering an entire component, such as a complete subframe assembly.

[0043] Preferably, the bearing bolt is operatively connected to the inner core via the spacer element in order to deflect the inner core over an adjustment path transverse to the connecting axis. An external thread of the bearing bolt engages with an internal thread of the spacer element. Rotating the bearing bolt causes the spacer element to move along the bearing bolt over a linear path. A rotational movement of the bearing bolt causes a linear movement of the spacer element along the bearing bolt. The spacer element is guided in the opening of the inner core, the opening having a slope or angle relative to the connecting axis and the bearing bolt. Through the interaction of the positive guidance of the spacer element both in the guide rail and along the bearing bolt, the linear movement of the spacer element causes a translational movement of the inner core, with the direction of action extending transversely to the bearing bolt.This means that the bearing axis can be deflected across a path perpendicular to the connecting axis, allowing for adjustment of the relative position of the mounted components via the adjustment mechanism. The advantage of this mechanism is that the relative position of the mounted components can be adjusted simply by rotating the bearing bolt. This eliminates the need for additional, complex, and sometimes expensive structures, such as welded bearing mounts or subframes. As a result, assembly and manufacturing costs are reduced.

[0044] Preferably, the adjustment range is adjustable as a function of the axial displacement of the spacer element. Due to the geometry of the guide rail, the adjustment range of the inner core relative to the connecting axis is directly proportional to the relative position of the spacer element along the connecting axis. Alternatively, the adjustment range is adjustable as a function of the number of rotations of the bearing bolt. Depending on the number of rotations of the bearing bolt, the spacer element can be displaced by a precise adjustment range relative to the connecting axis. In this way, the adjustment range can be adjusted to approach an end stop.

[0045] Further advantages and application possibilities of the present invention will become apparent from the following description in conjunction with the embodiment shown in the drawing.

[0046] In the drawing, this means: Fig. 1 an adjustment unit according to the invention; Fig. 2 an adjustment unit according to the invention arranged in a bearing receptacle of a handlebar; Fig. 3 a handlebar on which an adjustment device according to the invention is arranged; Fig. 4 an auxiliary frame and a handlebar which are mounted relative to each other via an adjustment device according to the invention; Fig. 5 a sectional view of an adjustment device according to the invention with a spacer element in the center position; Fig. 6 a sectional view of an adjustment device according to the invention with a deflected spacer element; and Fig. 7 a sectional view of an adjustment device according to the invention with a deflected spacer element;

[0047] In Fig. 1 An adjustment unit according to the invention, designated in its entirety by the reference numeral 10, is shown.

[0048] The adjustment unit 10 has a rubber-metal bearing 11. The bearing 11 has an inner core 12, which is connected to an outer sleeve 16 via an elastomer body 14. The inner core 12 of the bearing 11 is essentially cylindrical and extends in the direction of the bearing axis L. The inner core 12 has a passage 18, which is designed as an essentially rectangular, continuous recess 18 extending in the axial direction of the bearing 11.

[0049] In the opening 18, a spacer element 20 is arranged, which has a through-hole 22 for receiving a bearing bolt 24 (not shown). The through-hole 22 is formed with an internal thread (also not shown). The through-hole 22 defines a connection axis A of the bearing 11, which runs parallel to the bearing axis L. In this case, the connection axis A and the bearing axis L overlap. The spacer element 20 is cube-shaped and is arranged in the through-hole 18 of the inner core 12 by means of two parallel edges 26, 28 to prevent the spacer element 20 from rotating relative to the inner core 12.

[0050] The spacer element 20 is linearly adjustable or movable within the bushing 18 in the direction of extension of the bearing 11. The spacer element 20 is guided in a guide rail 32 by a guide element 30, which is, for example, designed as a guide pin 30. The guide rail 32 is arranged on an inner wall 13 of the inner core 12 and can, in particular, be designed as a groove, notch, or channel in the inner wall 13. It is also possible that the guide rail 32 is designed, for example, as a separate, rail-like component 32. The guide rail 32 extends at an angle to the bearing axis L in the longitudinal direction of the bushing 18. That is, the guide rail 32 has a slope relative to the bearing axis L.

[0051] In this case, the inner core 12 has a further guide rail 33 opposite the guide rail 32. The two guide rails 32, 33 are essentially identical in design and run parallel to each other.

[0052] The spacer element 20 is linearly adjustable within the bore 18 along the longitudinal axis of the bore 18. When the adjustment unit 10 is installed, the linear movement of the spacer element 20 is forced along the connection axis A, causing a translational deflection of the inner core 12 and thus of the entire bearing 11 transversely to the connection axis A.

[0053] It is also conceivable that the bushing 18, for example, has a hexagonal shape and extends longitudinally along the bearing 11 at an angle to the bearing axis L, with the bearing axis L and the longitudinal axis of the bushing 18 essentially lying in the same plane. In this alternative embodiment, the spacer element 20 has a hexagonal shape complementary to the bushing 18. The spacer element 20 is linearly movable within the bushing 18, with the longitudinal axis of the bushing 18 having a slope or angle relative to the bearing axis L. Due to the positive guidance of the spacer element 20 along the connection axis A, the spacer element displaces the inner core 12 of the bearing 11 translationally, with the direction of action of the displacement being transverse to the connection axis A.

[0054] Fig. 2 represents a control arm 34 of a vehicle, which is formed at each of its ends with a first bearing receptacle 36 and a second bearing receptacle 38. In the present case, the first bearing receptacle 36 contains a bearing as shown in Fig. 1 The adjustment unit 10 shown is arranged, via which the control arm 34 can be connected, for example, to a subframe 40 (not shown). The adjustment unit 10 has a guide rail 32, which is oriented such that the direction of movement of the inner core 12 runs along the longitudinal axis of the control arm. In the installed state of the control arm 34, a 90° rotation of the bearing allows, for example, the adjustment of wheel position gradients, such as the toe and / or camber angle changes over a suspension travel.

[0055] In Fig. 3 is a wishbone 34 after Fig. 1 The figure shows an adjustment device according to the invention, which is designated in its entirety by reference numeral 50, arranged on the control arm 34. The adjustment device 50 comprises an adjustment unit 10, which is received in the first bearing receptacle 36 of the control arm 34 and is fixed to a double-shear bearing bracket 52 via a bearing bolt 24. The adjustment unit 10 is concealed behind the bearing bracket 52 in a space-saving manner and advantageously has the same installation space requirement as a conventional rubber-metal bearing 11, via which a control arm 42 can be connected to a subframe 40.

[0056] In Fig. 4 The diagram shows the connection of the control arm 34 to a subframe 40 via the adjustment device 50. The subframe 40 has two longitudinal members 42 extending in the longitudinal direction X of the vehicle, which are connected to each other via two cross members 44 extending in the transverse direction Y of the vehicle. The direction of travel is indicated by F. Several bearing brackets 46, 52 for attaching wheel guidance elements are arranged laterally on the subframe 40, of which only one control arm 34 is shown.

[0057] The adjustment device 50 according to the invention is arranged in a connection area of ​​the subframe 40, which is difficult to see and / or access due to limited installation space. The bearing 11 of the adjustment device 50 is attached to the double-sheared bearing bracket 52 of the subframe 40 via a screw connection using a bearing bolt 24. By rotating the bearing bolt 24, a simple adjustment of the distance between the subframe 40 and the control arm 34 in the transverse direction Y of the vehicle is possible, for example, to change wheel alignment parameters such as toe and / or camber.

[0058] The adjustment device 50 is not limited to use in wheel suspensions. It can also be used, for example, to mount a component on the subframe 40.

[0059] Fig. 5 represents a cross-section of the adjustment device 50 according to Fig. 3 The adjustment device 50 is shown obliquely from above along the connection axis A. It comprises an adjustment unit 10, which has a bearing 11 that is received in a bearing receptacle 36 of the control arm 34. The bearing receptacle 36 is encompassed by a double-shear bearing bracket 52, which has two bearing lugs 54, 56. The bearing 11 and the bearing lugs 54, 56 are penetrated by a bearing bolt 24, which, for example, has a partial thread and is fixed in the bearing bracket 52 by means of a nut 58. The bearing bolt 24 rests against a connection axis A of the bearing 11.

[0060] The inner core 12 of the bearing 11 is designed with a substantially rectangular opening 18. A guide rail 32, designed in particular as a groove, is arranged in the opening 18 on the inner core 12. The guide rail 32 extends longitudinally along the opening 18, at an angle to the bearing axis L and thus to the connecting axis A. That is, the guide rail 32 has a slope relative to both the bearing axis L and the connecting axis A.

[0061] A cube-shaped spacer element 20 is guided in the guide rail 32 by means of at least one guide element 30. For example, a guide element 30, designed as a guide pin 30, is arranged on the spacer element 20 and is guided in the guide rail 32.

[0062] The spacer element 20 has an opening 22 in which the bearing pin 24 is received. Here, the spacer element 20 is shown in a central position in the axial longitudinal direction of the bearing 11. In this case, the bearing axis L and the connection axis A are superimposed. The opening 22 is formed with an internal thread (not shown) that engages with an external thread of the bearing pin 24. The bearing pin 24 is screwed into the internal thread, and rotation of the bearing pin 24 causes the spacer element 20 to move axially along the bearing pin 24. The nut 58 of the bearing pin 24 is not yet tightened. Due to the positive guidance of the spacer element 20 along the bearing pin 24, the guide element 30 displaces the inner core 12 over an adjustment path transverse to the connection axis. This means that the inner core 12 and thus the entire bearing 11 can be displaced transversely to the bearing bolt 24.Once the desired adjustment range of bearing 11, and thus of the control arm, relative to the subframe (not shown here) is reached, the nut 58 of the bearing bolt 24 is tightened. The force then flows again via the end faces of the inner core 12.

[0063] Fig. 6 und Fig. 7 The adjustment device 50 is shown in each case. Fig. 5 The spacer element 20 is arranged in differently deflected positions along the bearing bolt 24. The adjustment device 50 shown here is intended in particular for camber or toe correction. When the bearing bolt 24 is rotated, the positive guidance of the spacer element 20 along the bearing bolt 24 and the interaction of the guide element 30 (not shown) with the guide rail 32 result in a displacement of the inner core 12 of the bearing 11 transversely to the bearing bolt 24 or to the connecting axis A. This displacement of the inner core 12 changes the relative position of the inner core 12 and of the entire bearing 11 with respect to the connecting axis A, which abuts the bearing bolt 24. This, in turn, changes the position of the control arm 42 relative to the bearing lugs 54, 56 of the bearing bracket 52, which is, for example, arranged on a subframe 40.

[0064] Due to the geometric design of the guide rail 32, the displacement of the handlebar 34 as a function of the position of the spacer element 20 along the bearing bolt 24 can be successively adjusted according to the number of revolutions of the bearing bolt 24, so that the approach of the handlebar 24 to a respective end stop is easy to recognize.

[0065] In the manner described, the distance between the control arm 34 and the subframe 40 (not shown) can be adjusted by turning the bearing bolt 24. Thus, in the Fig. 6 a distance between the handlebar and the auxiliary frame 40 (not shown) is reduced by deflecting the spacer element 20 in one direction, whereas in Fig. 7 The distance between the handlebar 34 and the subframe 40 is increased by deflecting the spacer element 20 in the opposite direction.

Claims

1. Adjustment unit (10) comprising a rubber / metal bearing (11) having a bearing axis (L), wherein the rubber / metal bearing (11) has an inner core (12) which extends along the bearing axis (L), wherein the inner core (12) is constructed with a passage (18) which extends in the longitudinal direction of the inner core (12), characterized in that in the passage (18) there is arranged a spacer element (20) which has an aperture (22) for receiving a bearing pin (24), wherein the aperture (22) extends along a longitudinal axis which defines a connection axis (A) of the rubber / metal bearing (11), and wherein the connection axis (A) and the bearing axis (L) can be adjusted relative to each other by means of an adjustment of the spacer element (20), wherein the spacer element (20) is movably arranged in the extent direction of the passage (18), wherein in the installed state of the rubber / metal bearing (11) an axial adjustment of the spacer element (20) along the connection axis (A) is carried out and brings about a translational deflection of the inner core (12) transversely relative to the connection axis (A).

2. Adjustment unit according to claim 1, characterized in that the spacer element (20) is arranged in a torsion-resistant manner in the inner core (12).

3. Adjustment unit according to either claim 1 or claim 2, characterized in that the passage (18) of the inner core (12) has a longitudinal axis which extends at an angle with respect to the bearing axis (L).

4. Adjustment unit according to either claim 1 or claim 2, characterized in that the spacer element (20) can be displaced along at least one guide rail (32, 33) which is arranged on the inner core (12), wherein the guide rail (32, 33) extends at an angle with respect to the bearing axis (L) in the longitudinal direction of the passage (18).

5. Adjustment unit according to claim 4, characterized in that the spacer element (20) has at least one guiding element (30) which is received in the guide rail (32, 33).

6. Adjustment unit according to any one of claims 1 to 5, characterized in that the spacer element (20) is constructed with an inner thread.

7. Adjustment device (50) comprising an adjustment unit (10), a bearing pin (24), a nut (58) which can be screwed onto the bearing pin (24), and two components (34, 40) which are supported against each other, wherein one of the components (34, 40) which are supported against each other has a bearing receiving member (36) and the other has a bearing holder (52), wherein the bearing receiving member (36) is surrounded by the bearing holder (52) which is arranged on the other component (40) in each case, characterized in that the adjustment unit (10) is constructed according to any one of claims 1 to 6, wherein the rubber / metal bearing (11) is received in the bearing receiving member (36) and the rubber / metal bearing (11), the spacer element (20) and the bearing holder (52) are passed through by the bearing pin (24) which can be secured to the bearing holder (52) by means of the nut (58) which can be screwed on.

8. Adjustment device according to claim 7, characterized in that the bearing pin (24) is actively connected to the inner core (12) by means of the spacer element (20) in order to deflect the inner core (12) over an adjustment path transversely with respect to the connection axis (A).

9. Adjustment device according to claim 8, characterized in that the adjustment path can be adjusted in accordance with an axial distance of the spacer element (20).

10. Adjustment device according to claim 8, characterized in that the adjustment path can be adjusted in accordance with a number of revolutions of the bearing pin (24).