Adjustment device

Abstract

The present invention relates to an adjustment device (10) for a vehicle component that is movable relative to the vehicle body, particularly for a vehicle door or vehicle flap, wherein the adjustment device (10) - A housing (24) having a slide assembly (26), wherein the slide assembly (26) can be moved between a first position and a second position by a drive unit (14), - A slide assembly (26) and an adjustment element (28) designed to be connectable to the vehicle body or a vehicle component that is movable relative to the vehicle body, -The device comprises fastening elements (36) for fastening the adjustment device (10) to the vehicle body or a vehicle component that is movable relative to the vehicle body, the fastening elements (36) being designed to be connectable to the housing (24) in a frictional and / or positive-movement manner.

Description

Technical Field

[0005] ,

[0004] , , , , , , , ,

[0003] ,

[0006] ,

[0001] The present invention relates to an adjusting device for vehicle parts that are movable relative to the vehicle body, specifically for vehicle doors or vehicle flaps.

Background Art

[0002] An adjusting device of the above type is known, for example, from German Patent No. 102011118353 (A1). An adjusting device for a vehicle tailgate is shown, and this adjusting device includes a spindle drive. The spindle drive has two spindle tubes that can be fitted into each other in a nested manner.

[0003] German Patent No. 102019214037 (A1) also relates to a spindle drive, and the spindle drive is connected to a pressure piston via a section tube. The section tube is frictionally fastened to the spindle nut of the spindle drive. Other adjusting devices using spindle drives are actually known. Such spindle drives usually have a number of individual components, and as a result, the manufacture of such spindle drives can lead to chain tolerances that can contribute to an increase in noise generation, especially when vibrations associated with corresponding vibrations or tolerances are transmitted to the vehicle body or vehicle parts that are movable relative to the vehicle body.

Summary of the Invention

[0004] In view of such a background, an object of the present invention is to specify an adjusting device for vehicle parts that are movable relative to the vehicle body, and the adjusting device enables good tolerance compensation especially during assembly, thereby reducing noise generation during operation. An object of the present invention is also to specify a vehicle equipped with such an adjusting device.

[0005] According to the present invention, this object is achieved with respect to the adjusting device according to the subject matter of claim 1 and with respect to the vehicle according to the subject matter of claim 15.

[0006] Specifically, this objective is achieved by an adjustment device for a vehicle component that is movable relative to the vehicle body, particularly for a vehicle door or vehicle flap, which preferably comprises a housing having a slide assembly, the slide assembly being moved between a first position and a second position by a drive unit. Furthermore, adjustment elements are provided, which are designed to be connectable to the slide assembly and to the vehicle body or a vehicle component that is movable relative to the vehicle body. The present invention can also provide fastening elements for fastening an actuator to the vehicle body or a vehicle component that is movable relative to the vehicle body, which are designed to be connectable to the housing in a frictional and / or positive-movement manner.

[0007] The adjustment elements are designed to be connectable, in particular, to the slide assembly and to the vehicle body or to vehicle components that are movable relative to the vehicle body.

[0008] The ball joint connection, in particular, allows for the linkage and movement of the adjustment element around a pivot axis that extends, for example, through a ball bolt, perpendicular to the longitudinal axis of the adjustment element. In particular, the pivot axis of the adjustment element also extends through a slide assembly.

[0009] The present invention has the advantage that separate fastening elements allow for tolerance compensation when mounting the adjustment device to a vehicle. The fact that the fastening elements can be connected to the housing in a frictional and / or positive-action manner also facilitates mounting. In particular, mounting templates are not required. Rather, the position of the housing relative to the fastening elements can be adjusted to compensate for tolerances before the frictional and / or positive-action engagement is established. Thus, manufacturing tolerances, in particular tolerance chains, can be easily and simply compensated when mounting the adjustment device to a vehicle. This reduces tensile and acoustic disturbances that may arise from the transmission of vibrations to the vehicle body.

[0010] In a preferred embodiment of the adjustment device according to the present invention, the housing is provided to have at least one receptacle for guiding fastening elements along the longitudinal direction of the housing. Such guides for fastening elements allow for particularly easy tolerance compensation during installation. In particular, the fastening elements can be fastened or secured at different positions along the receptacle, and as a result, the optimal position of the adjustment device can be found for a particular vehicle.

[0011] Preferably, the fastening element comprises at least one guide device for insertion into the receptacle. Such a guide device facilitates the mounting of the fastening element to the housing of the adjustment device. At the same time, such a guide element can ensure that twisting of the fastening element relative to the housing of the actuator is avoided.

[0012] The guide device preferably includes a first guide element and a second guide element.

[0013] Such a double guide on the housing of the guide device ensures particularly good force absorption. Therefore, the tilt moment and other forces that occur laterally with respect to the longitudinal axis of the adjustment device can be easily absorbed and compensated by the guide device.

[0014] The dual guide can be further improved by inserting the first and second guide elements into the receptacle on opposite sides of the housing in the cross-sectional view.

[0015] In a preferred embodiment, the housing receptacle has at least two longitudinal grooves corresponding to a first guide element and a second guide element. Thus, the fastening element can have at least two guide elements corresponding to the longitudinal grooves. In this way, two-point bearing of the fastening element on the housing of the actuator is achieved, which provides particularly high stability while keeping component and material costs to a minimum. For example, the housing receptacle may also have three or more longitudinal grooves corresponding to the corresponding number and positions of guide elements on the fastening element.

[0016] In a more preferred embodiment of the adjustment device according to the present invention, the guide elements are arranged parallel to each other. In particular, the parallel arrangement of at least two guide elements allows the fastening elements to move along the housing. This mobility is advantageous to compensate for manufacturing tolerances of the adjustment device during installation and to make installation as easy as possible. Preferably, the fastening elements are finally secured only when the housing of the actuator and the fastening elements are precisely aligned with each other, i.e., when the corresponding manufacturing tolerances and tolerance chains are compensated.

[0017] It is also advantageous if at least one guide element is conical at its first end and at its second end. Multiple guide elements or at least one guide element should cooperate advantageously with at least one longitudinal groove of the receptacle on the housing. A conical or frustoconical shape at the end of the guide element is advantageous for easily connecting the guide element to the longitudinal groove. In this way, the guide element is automatically centered within the longitudinal groove. In addition, insertion of the guide element into the longitudinal groove is facilitated. Overall, such a design makes installation considerably easier, thereby speeding up the entire installation process. For example, each guide element of the fastening element has a conical shape at its first end and at its second end.

[0018] The guide element may also have a preloading element for generating a preload on the fastening element against the housing. The preloading element can, in particular, act as an anti-rotation mechanism, i.e., it can prevent the guide element from twisting within the receptacle or longitudinal groove. This prevents the fastening element from tilting when mounted in the housing, thereby facilitating mounting.

[0019] Generally, fastening elements may have preloading elements in the form of longitudinally formed ribs for contact with the housing. In particular, additional preloading elements can be provided formed outside the guide elements on the fastening element. Such preloading elements can be used as tolerance compensation or preloading elements for the housing, thereby eliminating rattle noise due to mechanical play during vehicle operation. This makes it easier to move the fastening element along the housing before it reaches its final position and is fixed, especially for mounting. Additional preloading elements on fastening elements can also be used to provide tolerance compensation. For this purpose, the fastening element may be made from, for example, a plastic material, and as a result, the preloading elements formed on the fastening element have a certain elasticity to compensate for housing tolerances. In either case, preloading elements on fastening elements have the additional advantage of reducing the transmission surface for vibration transmission, thereby minimizing acoustic disturbances caused by the adjustment device.

[0020] In a more preferred embodiment of the adjustment device according to the present invention, the fastening element is secured to the housing by crimping a receptacle having an inserted guide element. Thus, the fastening element can initially be firmly connected to the housing by the guide element and longitudinal groove, and the fastening element is movable along the longitudinal groove. During installation, this mobility is advantageously utilized to optimally align the fastening element with respect to the housing. Once the fastening element is precisely aligned with respect to the housing, final fixation can be achieved by crimping the longitudinal groove. The longitudinal groove can be reshaped to form an additional firm engagement with the guide element, and this additional firm engagement also acts in the longitudinal direction of the longitudinal groove. In other words, the fastening element is firmly fixed in place relative to the housing. The crimping is particularly easy to perform, thus facilitating installation of the adjustment device on the vehicle while simultaneously compensating for tolerances.

[0021] Alternatively or additionally, the fastening elements can be secured to the housing by riveting. Therefore, instead of reshaping the housing by crimping the longitudinal grooves, it is possible to provide a riveted connection between the fastening elements and the housing. However, in addition to crimping the longitudinal grooves using guide elements, a riveted connection can also be provided. A riveted connection is also easily established and cost-effective. Furthermore, a riveted connection provides particularly stable fastening of the fastening elements to the housing.

[0022] The housing can be made from an aluminum profile or have an extruded profile containing aluminum. On the one hand, such a housing is particularly stable, and on the other hand, it has a low mass, which is advantageous for lightweight construction in vehicle structures. The use of aluminum profiles, especially extruded profiles made from aluminum, is more cost-effective, especially in continuous production.

[0023] In a more preferred embodiment of the present invention, the fastening element may have a threaded portion having a funnel-shaped feed section for fastening to a vehicle body or a vehicle component that is movable relative to the vehicle body. Therefore, the threaded portion may, for example, receive a screw or a threaded rod to connect the fastening element to a vehicle body or a vehicle component that is movable relative to the vehicle body in a manner that is easily and detachably connected.

[0024] A further embodiment of the adjustment device advantageously provides that the fastening elements are manufactured by an injection molding process. In other words, the fastening elements can be formed by injection-molded parts. Preferably, the threaded portion of the fastening element has an overmolded nut. The nut is preferably overmolded with a plastic material. The nut itself can be made of metal. Using an overmolded nut as part of the threaded portion is advantageous because it allows the use of standardized components, particularly the nut, thereby reducing the overall cost of the components. At the same time, a nut made of a metal material provides high stability, while the overmolding provides acoustic isolation. Vibrations generated in the adjustment device are hardly transmitted, or at best only attenuated, to the body or vehicle parts that are movable relative to the body by the plastic material of the overmolded nut.

[0025] According to a further advantageous embodiment of the adjustment device, the fastening element comprises a retaining means for cables, particularly a cable clip. For example, a power cable, a sensor cable, or a fluid transport cable can be secured to the fastening element by the retaining means.

[0026] Equivalent aspects of the present invention relate to a vehicle equipped with the adjustment device described above. The present invention relates to an adjustment device for a vehicle component that is movable relative to the vehicle body, particularly for a vehicle door or a vehicle flap.

[0027] The present invention will be described below with reference to several embodiments. The same, similar or analogous components are denoted by the same reference numerals. The drawings, the description and the claims include a combination of a number of features. A person skilled in the art may also consider these features individually and combine them to form more advantageous combinations as appropriate. Therefore, the individual or plural embodiments can be advantageously combined with each other.

Brief Description of the Drawings

[0028] The drawings are as follows. [Figure 1] A side sectional view of an exemplary embodiment of an adjustment device according to the present invention. [Figure 2] A side view of the adjustment device of FIG. 1. [Figure 3] A spatial view of the housing of a further exemplary embodiment of an adjustment device according to the present invention. [Figure 4] A sectional view of the housing of the adjustment device of FIG. 3. [Figure 5] A spatial view of a slide assembly having an articulated adjustment element of a further exemplary embodiment of an adjustment device according to the present invention. [Figure 6] Shows a cross section of the slide assembly of FIG. 5. <​​​​​​​​​​​​​​​​​​​​​​This is a spatial diagram of a joint bearing in a further exemplary embodiment of the adjustment device according to the present invention. [Figure 15] Figure 14 shows a cross-sectional view of the joint bearing. [Figure 16] This is a spatial diagram of a joint bearing in a further exemplary embodiment of the adjustment device according to the present invention. [Figure 17] Figure 16 shows a cross-sectional view of a joint bearing having a joint bolt and a retaining plate. [Figure 18] This is a spatial diagram of a joint bearing in a further exemplary embodiment of the adjustment device according to the present invention. [Figure 19] A cross-sectional view of a housing with a cover, representing a further exemplary embodiment of the adjustment device according to the present invention, is shown. [Figure 20] Figure 19 shows an enlarged detail view X of the housing with the cover. [Figure 21] Figure 19 is a spatial diagram of the housing with a cover. [Figure 22] This is a spatial diagram of a seal arrangement in a further exemplary embodiment of the adjustment device according to the present invention. [Figure 23] Figure 22 shows a cross-sectional view of the seal arrangement. [Figure 24] This is a side cross-sectional view of a further exemplary embodiment of the adjustment device according to the present invention, having two positions for the slide assembly. [Figure 25] This is a spatial diagram of a slide assembly having an articulated adjustment element, representing a further exemplary embodiment of the adjustment device according to the present invention. [Figure 26] Figure 25 shows a cross-sectional view of the slide assembly located within the housing. [Figure 27] This is a perspective view of a housing for an adjustment device according to the present invention, according to a further preferred exemplary embodiment, having fastening elements for connection to a vehicle. [Figure 27A] This is a further perspective view of the housing of the adjustment device according to the present invention, according to an additional embodiment. [Figure 28A] This is a perspective view of the fastening element corresponding to the fastening element of the adjustment device shown in Figure 27. [Figure 28B] Figure 27 is a perspective rear view of the fastening element of the adjustment device shown. [Figure 29] Figure 28A is a cross-sectional view of the fastening element. [Figure 30] Figure 28A is a perspective view of the fastening element from below. [Figure 31] This is a perspective view of a slide assembly having an articulated adjustment element according to a preferred exemplary embodiment of the adjustment device according to the present invention. [Figure 32] Figure 31 shows a vertical cross-section passing through the end of an adjustment element formed using a ball bolt. [Figure 32A] Figure 31 shows a horizontal cross-section passing through the end of an adjustment element formed using a ball bolt. [Figure 32B] Figure 32A shows a horizontal cross-section where the adjustment element has an anti-rotation mechanism for the ball bolt. [Figure 32C] Figure 32A shows a horizontal cross-section where the adjustment element has an alternative anti-rotation mechanism for the ball bolt. [Figure 33] Figure 31 is a perspective plan view of the slide assembly without articulated adjustment elements. [Figure 34] Figure 31 shows a vertical cross-section passing through the slide assembly. [Figure 34A] A ball bolt on an adjustment element according to a further exemplary embodiment of the adjustment device according to the present invention is shown. [Figure 34B] Figure 34A shows a vertical cross-section through a slide assembly with a ball bolt. [Figure 34C] Figure 34A shows a further vertical cross-section through the slide assembly with the ball bolt shown. [Figure 34D] This is a perspective view of the ball bolt of a ball head receptacle in a further exemplary embodiment of the adjustment device according to the present invention. [Figure 35] This is a perspective cross-sectional view of the housing of the adjustment device according to the present invention in the area of ​​the drive element according to a preferred exemplary embodiment. [Figure 36A] Figure 35 is a perspective view of the plastic element covering the free end of the drive element. [Figure 36B] This is a perspective view of the drive element shown in Figure 35, which has the plastic element shown in Figure 36A. [Figure 36C] Figure 36A is a cross-sectional view of the plastic element shown. [Figure 36D] This is a perspective view of a plastic element of the adjustment device according to the present invention, according to a further preferred exemplary embodiment. [Figure 37A] This is a perspective plan view of a housing for a drive unit having a storage tank for liquefied plastic material. [Figure 37B] Figure 37A is a perspective front view of the housing. [Figure 37C] Figure 37A shows a further perspective view of the housing for a drive unit having a storage tank for liquefied plastic material. [Figure 37D] Figure 37A shows a further perspective view of the housing for a drive unit having a storage tank for liquefied plastic material. [Figure 38] This is a perspective view of a bushing to be positioned between the drive element and the housing of the adjustment device. [Figure 39A] This is a perspective view of a slide assembly of an adjustment device according to the present invention, having a receiving opening for a spindle nut. [Figure 39B] This is a further perspective view of the slide assembly shown in Figure 39A, with the spindle nut inserted. [Figure 40] Figure 39B is a side view of the slide assembly when the spindle nut is inserted. [Figure 41] This is a side view of the slide assembly shown in Figure 39B, with the spindle nut inserted. [Figure 42] This is a perspective plan view of a joint bearing of an adjustment element having a two-part joint bearing insert, where the second joint bearing insert element has a centering contour. [Figure 43] Figure 42 is a perspective view of the joint bearing. [Figure 44]This is a cross-sectional view of a joint bearing having an inserted joint bolt, according to a further exemplary embodiment. [Figure 45] Figure 44 is a perspective side view of the joint bearing. [Figure 46] Figure 45 is a perspective view of the joint bearing. [Figure 47] Figure 46 is a perspective cross-sectional view of the first joint bearing insert element of a joint insert for a joint bearing. [Figure 48] Figure 46 is a perspective cross-sectional view of the second joint bearing insert element of a joint insert for a joint bearing. [Figure 49] A joint bolt for a joint bearing is shown according to a preferred exemplary embodiment. [Figure 50] This shows the retaining plate for fastening the adjustment device to the vehicle. [Figure 51] An assembly of an adjustment element having a retaining plate, a joint bolt passing through the retaining plate, and a joint bearing is shown so as to form a pivot bearing connection. [Figure 52] Figure 51 is a cross-sectional view of the assembly shown. [Figure 53] This is a perspective rear view of the housing cover of the adjustment device according to a preferred exemplary embodiment. [Figure 54] Figure 53 is a perspective side view of the end of the housing of the adjustment device, which is closed with the cover shown. [Figure 55] This is a perspective rear view of a sealing element of an adjustment device according to the present invention, according to a preferred exemplary embodiment. [Figure 56] This is a perspective front view of a sealing element according to a further preferred exemplary embodiment. [Figure 57A] Figure 55 is a perspective cross-sectional view passing through the sealing element shown. [Figure 57B] This is a perspective side view of an adjustment element with a sealing element placed on it. [Figure 58]This is a perspective front view of a housing of an adjustment device according to the present invention, according to a preferred exemplary embodiment, having an internally inserted seal arrangement. [Figure 59] Figure 58 is a perspective view of the sticker arrangement. [Figure 60] This is a perspective front view of a slide assembly of an adjustment device according to the present invention, according to a further preferred exemplary embodiment, having a compensation element for tolerance compensation. [Figure 61] Figure 60 is a side view of the slide assembly shown. [Modes for carrying out the invention]

[0029] In Figure 1, the adjustment device according to the present invention is generally indicated by reference numeral 10. The adjustment device 10 comprises a drive assembly 12 having a drive unit 14 and a drive element 16 driven by the drive unit 14. The drive element 16 is designed here as a worm, which is rotationally driven by the drive unit 14, designed as an electric motor, and meshes with a worm wheel 18. The worm wheel 18 is fixedly positioned on the spindle 20 such that the rotation of the drive element 16 causes the rotation of the worm wheel 18, and therefore causes the rotation of the spindle 20. The drive element 16 can be formed integrally with the motor shaft 42 of the drive unit, or alternatively, it can be connected to it.

[0030] The spindle 20 is screwed onto the spindle nut 22, which is positioned to be fixed to the housing 24 of the adjustment device 10 by rotation, and is therefore axially displaceable along the rotation axis R of the spindle 20 when the spindle 20 rotates.

[0031] In the illustrated embodiment of the adjustment device 10, the spindle nut 22 is part of a slide assembly 26 that is displaceable along the axis of rotation R of the spindle 20 together with the spindle nut 22 when the spindle 20 rotates. Above the slide assembly 26 in Figure 1, the aforementioned slide assembly is connected to an adjustment element 28, which is designed here as a straight door check strap. Alternatively, the adjustment element 28 may also be S-shaped, and this S-shape may extend substantially within a plane aligned parallel to the axis of rotation R of the spindle 20 and perpendicular to the drawing of Figure 1. In the illustrated embodiment, the adjustment element 28 has a circular cross-section. Alternatively, the adjustment element 28 may also be rectangular or substantially elliptical.

[0032] The adjustment element 28 is connected at its free end (shown on the left side of Figure 1) to a movable vehicle component such as a vehicle side door (not shown), or alternatively to the vehicle body (not shown). At the end opposite to the free end, the adjustment element 28 is connected to the slide assembly 26 via the pivot axis 30, allowing the adjustment element 28 to move out of the drawing plane of Figure 1, around the pivot axis 30 or around a virtual rotation axis S.

[0033] When the drive unit 14 is activated, the spindle 20 begins to rotate, thereby displacing the adjustment element 28 along the displacement axis V via the slide assembly 26, the displacement axis V coinciding with the central axis of the linear adjustment element 28 in the neutral position (shown in Figure 1) of the adjustment element 28 and the slide assembly 26 (see below for further details).

[0034] To allow a specific movement of the free end of the adjustment element in the vertical direction in Figure 1, the portion of the slide assembly 26 to which the adjustment element 28 is connected is arranged to be tiltable with respect to the spindle nut 22 in the illustrated exemplary embodiment. For this purpose, the longitudinal end of the spindle nut 22 may be provided with a curvature corresponding to the curvature of a circle, the center of which coincides with the center of the longitudinal range of the spindle nut 22 and the axis of rotation R of the spindle 20, and the radius corresponding to the distance from the center of the circle to the longitudinal end of the spindle nut 22. The remaining surface of the slide assembly 26 that contacts the spindle nut 22 may be similarly curved.

[0035] The slide assembly 26 may have at least one guide portion 32 within the area of ​​the spindle nut 22 and / or on a portion separate from the spindle nut 22, through which the slide assembly 26 is guided within the housing 24 of the adjustment device 10. In the exemplary embodiment shown in Figure 1, the slide assembly 26 has guide portions 22 corresponding to both the area of ​​the spindle nut 22 and a further portion. For reasons of symmetrical force distribution, these two guide portions may also be present on the opposite side of the slide assembly 26 (not visible in Figure 1).

[0036] To protect the interior of the adjustment device 10 from contamination, the adjustment device 10 in the illustrated exemplary embodiment includes a seal arrangement 34 located between the adjustment element 28 and the housing 24.

[0037] However, the adjustment device 10 can also generally be designed without the seal arrangement 34. In this case, it may be advantageous for the housing 24 to be provided with at least one drain hole, for example, so that any moisture that enters the housing 24 can escape.

[0038] Figure 2 shows a side view of the adjustment device 10 according to the present invention shown in Figure 1. It can be seen that the central axis M of the drive element 16 is positioned at an angle to the plane defined by the displacement axis V of the adjustment element 28 and the rotation axis R of the spindle 20 (in the neutral position of the adjustment element 28 and slide assembly 26 as shown in Figure 1). In particular, as can be seen in Figure 2, the lower portion of the drive assembly 12 in Figure 2 can therefore be displaced within the region vertically below the spindle 20. Thus, the required installation space, particularly the installation space located to the right of the drive assembly 12 in Figure 2, can be reduced.

[0039] Furthermore, the design of the adjustment device 10 according to the present invention makes it possible to replace the movable attachment of the housing 24 of the adjustment device 10 to the vehicle body or movable vehicle part with a rigid fastening, thereby eliminating additional space requirements.

[0040] The adjustment device 10 shown in particular is intended to be mounted on a movable vehicle component. In the illustrated exemplary embodiment, the drive assembly 12 is positioned in front of the adjustment device 10, where front is understood to be the side of the adjustment device 10 facing the free end of the adjustment element 28. However, due to limited installation space on the movable vehicle component, it may be advantageous to provide a reversed arrangement of the drive assembly 12. In other words, due to space constraints, it may be advantageous to position the drive assembly 12 behind the adjustment device 10, facing away from the free end of the adjustment element 28. In this case, the angled arrangement of the central axis M of the drive element 16 shown in Figure 2 can be omitted, and a more compact design can be achieved. A further advantage of this reversed arrangement of the drive assembly 12 is that it allows for the design of the adjustment device 10 on both sides of the vehicle, i.e., the left and right sides of the vehicle, with the same structure and in a simple manner. It is sufficient to simply rotate the assembly by 180°.

[0041] The basic structure and function of these two embodiments, which differ in the arrangement of the drive unit 12, are essentially the same.

[0042] Preferred markings are provided for the adjustment device 10 so that it can be clearly identified even when installed, without the need to remove it from the vehicle or side door, for example, by a factory employee. However, since these markings should not be visible to the vehicle's end customer / driver, the adjustment element 28 can be advantageously labeled on the side wall facing away from the vehicle's passenger compartment when installed. When installed, this side wall of the adjustment device 28 faces, for example, the side door and is not visible to the vehicle's end customer. If the adjustment device 10 is tilted 180° and positioned on the other side of the vehicle, the markings are also located on the side wall of the adjustment element 28 facing away from the passenger compartment.

[0043] A further advantageous labeling method is to label the adjustment element 28 with a suitable lacquer, which can only be visualized using a suitable light source. For example, a UV varnish that is only visible using a UV lamp can be used.

[0044] Figure 3 shows a housing 24 of a further exemplary embodiment of the adjustment device 10 according to the present invention, which substantially corresponds to the adjustment device 10 described above. The housing 24 of this embodiment is preferably an aluminum section tube, has an open profile structure, and has longitudinal notches or longitudinal grooves 37 at least at corner points 35. To create additional fastening points of the adjustment device 10 in a simple manner, fastening elements 36 adapted to the section tube are provided, which fasten to the housing 24 by friction connections and / or confirmation-dynamic connections. The fastening elements 36 can be fastened, for example, by rivets 33 or screws. As can be seen in Figure 4, which shows a cross section of the housing 24 having the fastening elements 36, the fastening elements 36 have plate-like sub-elements on which fastening bolts 31 are formed or fastened. The plate-like sub-elements and fastening bolts 31 extend in a direction perpendicular to the longitudinal axis of the adjustment device 10. The arm-shaped portion of the fastening element 36 surrounds the upper side of the housing 24, and the fastening element 36 engages with three of the longitudinal grooves 37 and fastens to one of the longitudinal grooves 37 as described above. The fastening element 36 allows for additional fastening points that can be flexibly adapted to the installation space.

[0045] Figures 5 and 6 show a slide assembly 26 having an articulated adjustment element 28 of a further exemplary embodiment of the adjustment device 10 according to the present invention, which substantially corresponds to the adjustment device 10 described above.

[0046] The adjustment element 28 is connected to the slide assembly 26 by a ball joint connector, which comprises a ball bolt 38 fixedly connected to the adjustment element 28 and a ball socket 40 formed within the slide assembly 26. As can be seen in Figure 6, the ball socket 40 is provided integrally with the slide assembly 26, preferably made of a plastic material. The ball bolt, preferably provided as a cold-formed part, can be connected to the adjustment element, which may be provided as a press-formed part, in a positive manner, or in positive and negative manner, by a reforming process, preferably by riveting. To facilitate fastening the ball bolt 38, a pin-shaped fastening element (not shown) can be provided, which penetrates the slide assembly 26 and fixes the ball head of the ball bolt 38 within the ball socket 40, thereby allowing the ball bolt 38 to rotate with as little play as possible. For this purpose, the slide assembly 26 has a through hole 39, as shown in Figure 6, for example.

[0047] Figure 7 shows a detail of a side cross-section of a further exemplary embodiment of the adjustment device 10 according to the present invention, which substantially corresponds to the adjustment device 10 described above.

[0048] In this exemplary embodiment, the drive unit 14 is also an electric motor, and its motor shaft 42 or drive unit 16 is mounted in a manner that it is axially preloaded within a drive housing 84 connected to the housing 24. In this regard, it should be noted that the drive housing 84 is considered to be part of the housing 24 and may be formed integrally with the housing 24. Here, the motor shaft 42, which is formed integrally with the drive element 16, rests on an axial motor shaft preload assembly. The assembly shown in Figures 8 to 10 comprises a plastic element 46 for the motor shaft 42 having a spherical segment shape, convex, concave or planar contact surface; a screw 48 that can be screwed into the drive housing 84, rests on the plastic element 46, and is connected in a manner that it is anchored to the plastic element 46 by two undercuts 41; and a spring element 50 positioned or enclosed between the plastic element 46 and the screw 48.

[0049] On the one hand, the axial preload, i.e., the screwing in of the screw 48, can reduce the chain tolerance of the individual components, and as a result, it is possible to prevent or minimize the resulting noise. On the other hand, the enclosed spring element 50 enables temperature compensation, and as a result, a constant preload force on the motor shaft 42, and therefore quiet operation of the motor, is possible over all temperatures.

[0050] Figures 11 to 13 show a slide assembly 26 on which a spindle nut 22 is located, representing a further exemplary embodiment of the adjustment device 10 according to the present invention, substantially corresponding to the adjustment device 10 described above.

[0051] As can be seen in Figures 11 to 13, the spindle nut 22 of the exemplary embodiment has two different outer circumferences 43 and 45 in cross-section, with a common center M, and the spindle nut 22 can be tilted within the slide assembly 26 and simultaneously support a torsional moment. The first outer circumference 43 is provided to be larger than the second outer circumference 45. The inner contour 47 of the slide assembly 26 is adapted to it and has a similar inner surface. A transition surface 49 between the outer circumferences 43 and 45 also allows for limiting the tilting motion. In particular, damage to the spindle drive must be eliminated if the adjustment device 10 is not handled correctly. Therefore, the spindle nut 22 must be positioned in a tiltable manner within the slide assembly 26, and the tilting function must not adversely affect the torque absorption required for the function within the slide assembly 26. The different outer circumferences 43 and 45 of the spindle nut and the adapted inner contour 47 of the slide assembly 26 ensure that torque support is provided through the second outer circumference 45 of the spindle nut despite the tilting function.

[0052] Figures 14 to 18 show, in spatial or cross-sectional views, several further embodiments of the adjustment device 10 according to the present invention, which substantially correspond to the adjustment device 10 described above.

[0053] At its end facing away from the slide assembly 26, the adjustment element 28 (only partially shown) has a joint bearing 52 with a joint bearing insert 60, and the joint bearing 52 is connected to the retaining plate 56 by a joint bolt 54 shown in Figure 15. The exemplary embodiments shown in Figures 14 to 18 all have in common that the joint bearing 52 has means for compensating for angular errors in fastening the retaining plate.

[0054] For fastening, the retaining plate 56 (also called an angle plate) is fastened to the vehicle (vehicle door or body). Twisted fastening of the retaining plate 56 affects the geometry of coordinated movement and causes misalignment of the system. To avoid the complex mounting of the retaining plate 56 by template, angular errors in the area of ​​the joint bearing 52 can be compensated according to the present invention so that this error does not have any further effect on the subsequent system.

[0055] Figures 14 and 15 show further exemplary embodiments. The joint bearing 52 of the adjustment element 28 has a joint bearing insert 60, which in this exemplary embodiment is manufactured by overmolding or welding the joint bearing 52. As can be seen from the figures, the joint bearing insert 60 has crush ribs 58 with a comb structure on the upper and lower sides, which makes it possible to compensate for angular errors in the axial direction. If the retaining plate 56 is screwed in incorrectly, compensation is achieved by deformation of the crush ribs 58. Before that, the comb structure stabilizes the system, and as a result the angle plate 56 cannot be arbitrarily twisted when screwed in without the need to use a template.

[0056] Figure 16 shows a further exemplary embodiment, in contrast to the exemplary embodiment described above, in which the joint bearing insert 60 has a corrugated wear or centering contour 59 on its bottom surface, which allows angular errors to be compensated radially. If the retaining plate 56 is screwed in incorrectly, compensation is achieved by the wear of the contour. A detailed description of the centering contour 59 can be found in the exemplary embodiments described below, as shown in Figures 42 to 47.

[0057] According to further exemplary embodiments shown in Figures 17 and 18, the joint bearing insert 60 may be formed in two parts and comprise a first joint bearing insert element 61 and a second joint bearing insert element 62. The first joint bearing insert element 61 and the second joint bearing insert element 62 may be connected, for example, in a rigidly coupled or positively coupled manner. Figure 17 shows a threaded connection between the joint bearing insert elements 61 and 62. This connection has the advantage of being independent of the thickness of the joint bearing 52 of the adjustment element 28.

[0058] In contrast, Figure 18 shows a bayonet connection between joint bearing insert elements 61 and 62.

[0059] Alternatively, a strong joint connection of the joint bearing insert elements 61 and 62 is possible, in which case, for example, ultrasonic welding can be used to connect the two joint bearing insert elements 61 and 62.

[0060] As already described in the exemplary embodiment shown in Figure 3, the housing 24 may be a section tube that is closed by a cover 64 on the side facing away from the drive assembly 12.

[0061] According to further exemplary embodiments of the present invention shown in Figures 19 to 21, the cover 64 can be fixed to the section tube without additional components. For this purpose, the cover 64 made of a plastic material has molded domes 66 which engage with longitudinal notches / longitudinal grooves 37 at the corners 35 or sides of the housing 24 and are fixed by reshaping the housing 24. The cover 64 has at least three, preferably seven, domes 66.

[0062] The reshaping of the housing 24 can be seen in Figure 20, which shows an enlarged detail view of the housing 24 within the area of ​​the longitudinal groove 37. The reshaping is performed, for example, by pins, which deform the material of the longitudinal groove 37 in the direction of the dome 66, and as a result the dome 66 is fixed in a manner that it is anchored to the housing 24.

[0063] Further exemplary embodiments of the present invention shown in Figures 22 and 23 illustrate a seal arrangement 34 of an adjustment device 10 according to the present invention, which substantially corresponds to the adjustment device 10 described above. The adjustment element 28 typically has a rectangular cross-section and protrudes from the housing in a manner sealed by the seal arrangement 34. The seal arrangement 34 is advantageously designed as a bellows sleeve combined with a rod wiper and has a fastening portion 67, a wiper portion 69 positioned axially movable on the adjustment element 28, and a bellows portion 68 located between them. The fastening portion 67 is clamped between the housing 24 and a drive housing 84 connected to the housing 24, and the wiper portion 69 is sealed and rests on the aforementioned adjustment element using an opening 78 that is adapted to the cross-section of the adjustment element 28.

[0064] The bellows portion 68 of the seal arrangement 34 is configured to follow the pivotal, tilting, and pendulum motions of the adjustment element 28, and to ensure axial stability for the wiping effect.

[0065] Figure 24 shows a side cross-sectional view of a further exemplary embodiment of the adjustment device according to the present invention, in which the slide assembly 26 is shown at two end positions.

[0066] As already mentioned above, the housing 24 is also a section tube and is closed by a cover 64 on the side facing away from the drive assembly 12. The cover 64 shown herein further has a discharge opening 70 at the end position of the slide assembly 26 facing the cover 64, which can be sealed by a piston geometry 72 positioned on the slide assembly 26. Despite the existing sealing measures, it is not possible to prevent water from entering the adjustment device 10 within the area of ​​the adjustment element 28. Therefore, it is advantageous if, when the vehicle door is opened, the infiltrated water can be discharged from the adjustment device 10 through the drain opening 70. The piston geometry 72 positioned on the slide assembly 26 seals the drain opening 70 when the vehicle door is closed. For this purpose, the piston geometry 72 has a radial seal, which seals the discharge opening 70 or a projection 71 molded on the cover 64 at the end position.

[0067] Further advantageous exemplary embodiments of the adjustment device 10 according to the present invention, substantially corresponding to the adjustment device 10 described above, are shown in Figures 25 and 26. The slide assembly 26 shown in Figure 25 has at least first and second guide portions 32 (32A, 32B) for guiding within the housing 24, and the guide rail 74 is fixed to the guide portions 32 in either case substantially without play. Optionally, a third guide portion 32C may be provided on the slide assembly 26.

[0068] The housing 24 has a prismatic sliding surface or guide surface 77 for guiding the slide assembly 26, and a corresponding prismatic sliding surface or guide surface 75 is formed on each guide rail 74, which is pressed, for example, onto the guide portion 32 without play.

[0069] To enable the sliding surface 75 to be guided on the guide surface 77 of the housing 24 with as little play as possible, at least one of the two guide rails 74 has an automatically adjusting play reduction mechanism.

[0070] The reduction of the automatically adjusting play between the slide assembly 26 and the housing 24 can be achieved, for example, by a spring-loaded adjustment element 76 mounted perpendicular to the displacement direction of the slide assembly 26. The spring element 80 used for this purpose can be adapted to the application and load conditions without any structural changes to the slide assembly or guide.

[0071] This arrangement makes it possible to create a linear guide with virtually no play in the slide assembly 26, as well as a defined constant friction torque between the slide assembly 26 and the housing 24.

[0072] In other words, it becomes possible to create a linear guide with virtually no play in the slide assembly 26, as well as a defined constant friction torque between the slide assembly 26 and the housing 24, thereby enabling the full or partial achievement of the required retaining force of, for example, a vehicle door. A further advantage of applying friction to this point of action of the adjustment device 10 is a uniform base load, which leads to quieter operation of the entire system.

[0073] According to further embodiments not shown, the guide rail 74 may also be molded onto the slide assembly 26 by a two-component injection molding process.

[0074] When using suitable materials, it is also conceivable to form the slide assembly 26 integrally with the guide rail 74.

[0075] Figure 27 shows a housing 24 of the adjustment device 10 according to the present invention according to a further preferred exemplary embodiment. The housing 24 is preferably formed as an extruded product of aluminum. The housing 24 has a receptacle 37A in the form of a longitudinal groove 37, the receptacle 37A can be formed integrally with the extruded product. The receptacle 37A or longitudinal groove 37 is distributed on the housing 24 and preferably symmetrically aligned with respect to the vertical center plane of the housing 24. In particular, the longitudinal groove 37 extends parallel to each other. Fastening elements 36 are provided for fastening the adjustment device 10 to a vehicle, for example, a vehicle part that is movable relative to the body of the vehicle, or to the body of the vehicle itself. The fastening elements 36 are designed substantially similarly to the fastening elements shown in Figure 3 and are similarly used as additional fastening points for the adjustment device 10. Specifically, the fastening elements 36 have a guide device 37B having a plurality of guide elements 37C, 37D, 37E. In effect, the guide elements 37C, 37D, and 37E are pin-shaped and extend beyond the end face of the fastening element 36. The guide elements 37C, 37D, and 37E have an outer contour that substantially corresponds to the inner contour of the longitudinal groove 37, so that the guide elements 37C, 37D, and 37E can be guided in a sliding manner within the longitudinal groove 37. The fastening element 36 is inserted into the longitudinal groove 37, or generally into the receptacle 37A, and can move along the receptacle 37A and the longitudinal groove 37. Therefore, the fastening element 36 can be displaced along the housing 24.

[0076] Figure 27A shows a further perspective view of the housing 24 of the adjustment device 10 according to the present invention according to an additional embodiment. The housing 24 is formed as an extruded product of aluminum and has a receptacle 37A in the form of a longitudinal groove 37. The fastening element 36 comprises a guide device 37B and a plurality of guide elements 37C, 37D, 37E. In addition, the fastening element 36 comprises a retaining means 37I for cables. The retaining means 37I provides an opening for inserting a cable clip. The cable clip typically has an evergreen-like locking means, which can be inserted into the opening, allowing the cable holder of the cable clip to carry one or more cables.

[0077] As can be clearly seen in Figures 28A and 28B, an embodiment of the fastening element 36 comprises an arm-shaped sub-element 36C extending over the upper side of the housing 24 (Figure 27). At its free end, the arm-shaped sub-element 36C has a first guide element 37C of the guide device 37B. The arm-shaped sub-element 36C is used as a connecting element between guide elements 37D and 37C to absorb larger force loads. In the transition region between the trapezoidal sub-element 36D and the arm-shaped sub-element 36C of the fastening element 36, a second guide element 37D is positioned on the side facing the housing 24. Similarly, a third guide element 37E is provided at the end of the trapezoidal sub-element 36D opposite to the arm-shaped sub-element 36C. Thus, as a whole, the fastening element 36 has three guide elements 37C, 37D, and 37E, which together form the guide device 37B.

[0078] The guide members 37C, 37D, and 37E are pin-like in shape and have a substantially cylindrical outer contour. Each guide element 37B comprises a first end 37F and a second end 37G. The first end 37F and the second end 37G preferably have a conical taper. Specifically, the first end 37F and the second end 37G are each frustoconical. The taper formed therein allows the guide elements 37C, 37D, and 37E to be easily inserted into the longitudinal groove 37 during assembly.

[0079] To achieve lateral stabilization of the guide elements 37C, 37D, and 37E within the longitudinal groove 37, preloading elements 37H in the form of ribs are preferably provided on the guide elements 37C, 37D, and 37E, extending at least partially along the corresponding guide elements 37C, 37D, and 37E. The preloading elements 37H extend parallel to the longitudinal axes of the guide elements 37C, 37D, and 37E. As can be seen in Figure 28B, further preloading elements 37H in the form of ribs can be provided on the rear surface of the trapezoidal sub-element 36D. The ribs on the trapezoidal sub-element 36D preferably rest on the flat outer surface of the housing 24 and are therefore used as tolerance compensating elements or preloading elements for the housing 24, thereby eliminating rattle noise caused by mechanical play during vehicle operation. A threaded portion 36A is formed within the trapezoidal sub-element 36D to connect the fastening element 36 to the vehicle component and / or the vehicle body. The threaded portion 36A is equipped with, for example, a female thread that can cooperate with a screw. To facilitate the insertion of a screw into the threaded portion 36A, a funnel-shaped supply portion 36B opens into the threaded portion 36A.

[0080] The two fastening elements 36 shown in Figures 28A and 28B are substantially similar to each other. However, the fastening elements 36 may differ from each other in detail. For example, the arm-shaped sub-element 36C of the fastening element 36 as shown in Figure 28A has a substantially outward curved, i.e., concave curve. However, in an exemplary embodiment of the fastening element 36 as shown in Figure 28B, the arm-shaped sub-element 36C is partially curved inward. The fastening element 36 as shown in Figure 28B is shown, for example, in combination with the housing 24 of Figure 27. Figure 30 also shows the fastening element 36 shown in Figure 28B in a further perspective view.

[0081] Figure 29 shows a cross-sectional view of the fastening element 36 shown in Figure 28A. Specifically, Figure 29 again shows that guide elements 37C, 37D, and 37E can be positioned at different locations on the fastening element 36. For clarity, the guide element positioned on the free longitudinal end of the arm-shaped sub-element 36C is referred to as the first guide element 37C. The guide element positioned in the transition portion between the arm-shaped sub-element 36C and the trapezoidal sub-element 36D is referred to as the second guide element 37D. The third guide element 37E is a guide element located at the end of the trapezoidal sub-element 36D opposite to the arm-shaped sub-element 36C. The arrangement of the first guide element 37C, the second guide element 37D, and the third guide element 37E shown in relation to the fastening element 36 shown in Figure 29 also applies to exemplary embodiments of the fastening element 36 shown in Figures 28B and 30.

[0082] Figure 31 shows a slide assembly 26 to which an adjustment element 28 is articulated. The articulation between the adjustment element 28 and the slide assembly 26 is preferably made via a ball bolt 38. The adjustment element 28 is coupled via the ball bolt 38, particularly to the upper side of the slide assembly 26. Specifically, the ball bolt 38 engages with the areas of the guide portions 32A and 32B of the slide assembly 26.

[0083] The design of the ball bolt 38 can be clearly seen in the cross-sectional view of Figure 32. The ball bolt 38 is preferably fixed, and especially fixed by rotation, to the adjustment element 28. The ball bolt 38 passes through a through-opening of the adjustment device 28 and is axially fixed within this through-opening in a positive-movement manner relative to the hole axis. The ball bolt 38 can be fixed to the adjustment element 28 by friction connection and / or positive-movement connection, for example, by welding, so as not to rotate relative to the adjustment element 28. At the lower end, the ball bolt 38 forms a partially spherical outer contour. This partially spherical outer contour engages with the corresponding ball socket 40 in the slide assembly 26. The ball bolt 38 is preferably fitted into the ball socket 40 in a positive-movement but movable manner. This fitting allows the adjustment element 28 to be both pivotable and tiltable relative to the slide assembly 26. This mobility is advantageous for compensating for any tension that may arise due to the movement of the adjustment element 28, ensuring quiet movement of the adjustment device.

[0084] Figures 32A, 32B, and 32C show different modifications of fastening the ball bolt 38 to the adjustment element 28. In all cases, the adjustment element 28 with the ball bolt 38 is shown in a horizontal section view. The horizontal section substantially passes through the longitudinal central axis of the adjustment element 28 and through the center of the through hole through which the ball bolt 38 passes.

[0085] In the exemplary embodiment shown in Figure 32A, the through-hole of the adjustment element 28 has a circular inner surface through which the ball bolt 38 passes. The ball bolt 38 also has a circular outer surface in this region. Therefore, the ball bolt 38 can be mounted and positioned on the adjustment element 28 in a rotatable sliding manner so that rotation between the adjustment element 28 and the ball bolt 38 is possible. Alternatively, it is possible to create a rigidly coupled connection that prevents rotation. For example, the ball bolt 38 can be welded to the adjustment element 28.

[0086] However, in the exemplary embodiment shown in Figure 32B, rotation is prevented by a mechanically provided anti-rotation mechanism 39A. The anti-rotation mechanism 39A preferably has a toothed outer contour on the fastening portion of the ball bolt 38, which forms a press-fit connection with the inner contour of the through-hole of the adjustment element 28. Alternatively, the adjustment element 28 may have a notched inner contour or a toothed inner contour, so that the notches or teeth of the ball bolt 38 cooperate with the notches or teeth of the adjustment element 28, thus forming the anti-rotation mechanism 39A.

[0087] Another possibility for the anti-rotation mechanism shown in Figure 32A is to provide a minimum clearance fit between the ball bolt 38 and the adjustment element 28. In its original state, the ball bolt 38 preferably has a cylindrical extension, which extends from the partially spherical portion of the ball bolt 38 and is inserted through the opening of the adjustment element 28. Subsequently, the cylindrical portion of the ball bolt 38 is reshaped, thus forming a rivet, which on the one hand leads to a firm fixation along the hole axis of the ball bolt 38, and on the other hand, the diameter of the ball bolt 38 increases by compression, and the cylindrical portion of the ball bolt 38 is pushed radially into the hole of the adjustment element 28.

[0088] The exemplary embodiment shown in Figure 32C shows a ball bolt 38 having a trefoil-shaped contour in the region of the adjustment element 28. Therefore, the cross-sectional geometry of the portion of the ball bolt 38 extending from the partially spherical portion substantially corresponds to a rounded triangle. This contour can be easily pushed into the adjustment element 28 and provides an anti-rotation mechanism by the trefoil-shaped contour 39B.

[0089] As an alternative to the modifications shown in Figures 32A, 32B, and 32C, the ball bolt 38 and the adjustment element 28 can also be formed integrally or monolithically.

[0090] Figure 33 shows a ball socket 40 formed within the slide assembly 26, specifically in the areas of the guide portions 32A and 32B of the slide assembly 26. The ball socket 40 is formed integrally with the slide assembly 26. The ball socket 40 may be provided with at least one pocket 40A designed to receive lubricant. Specifically, the ball socket 40 preferably has multiple pockets 40A, which are substantially introduced as notches within the ball socket 40. Furthermore, the ball socket 40 may have at least two lateral bearing tabs 40B on which a ball bolt 38 can be placed. Preferably, each bearing tab 40 is separated by two pockets 40A. The bearing tabs 40B are located at least within the lower portion 40C of the ball socket 40 (Figure 34).

[0091] Figure 34 clearly shows the arrangement of the ball bolt 38 within the ball socket 40. It can be seen that the spherical portion of the ball bolt 38 engages with the ball socket 40. The pockets 40A, each positioned between at least two lateral bearing tabs 40B, allow for lubrication, thereby ensuring that the ball connection provided by the ball pin 38 and the ball socket 40 is well lubricated and permanently fitted without wear.

[0092] Preferably, at least one fastening element 39C is provided to hold the ball bolt 38 within the ball socket 40, the fastening element 39C securing the ball bolt 38 inserted into the ball socket 40. The fastening element 39C is preferably made of metal, particularly steel. The fastening element 39C can be designed to penetrate at least partially through the slide assembly 26 and the ball socket 40. Specifically, two parallel fastening pins or bolts that secure the ball bolt 38 within the ball socket 40 can be provided as the fastening element 39C. The fastening pins are inserted laterally into the first guide portion 32A of the slide assembly 26 and can contact the ball bolt 38 in the transition region between the spherical portion of the ball bolt 38 and the connection portion to the adjustment element 28. As can be clearly seen in Figure 34, the fastening element 39C thus prevents the ball bolt 38 from separating from the ball socket 40.

[0093] Figures 34A to 34D show further embodiments of the arrangement of the ball bolt 38 within the ball socket 40. According to this alternative embodiment, the ball socket 40 may have a surface including a lubricating plastic material. For example, a separate ball head receptacle 40D made of a lubricating plastic material may be provided. This ball head receptacle 40D may have a flexible element 40F to improve the mounting and fastening of the ball bolt 38 within the ball head receptacle 40D and within the ball socket 40, and can absorb compressive and tensile forces acting on the ball bolt 38. To securely fasten the ball head receptacle 40D within the slide assembly 26, for example, a locking means 40E can be provided, which can be locked within a suitable undercut 40G of the slide assembly 26. Alternatively or additionally, fastening elements 39C, in this case two fastening pins, used in the above embodiments may be inserted.

[0094] In the illustrated embodiment, the ball head receptacle 40D surrounds a metal, preferably steel, ball head of a ball bolt 38 having a flexible element 40F. The flexible element 40F is arm-shaped. As can be seen in Figure 34C, a fastening pin passes through the slide assembly 26 to prevent the ball head from coming out of the ball head receptacle 40D. Because the fastening pin rests on a corresponding notch 39D of the flexible element 40F, a kind of sandwich structure (steel-plastic-steel) is advantageously created, and the plastic material of the ball head receptacle 40D is subjected only to compressive loads. This connection allows for a playless or near-playless position of the ball bolt 38 within the slide assembly 26, while simultaneously having very little friction. The fastening pins are positioned parallel to each other, and the distance between the opposing inner edges of the fastening pins is less than the maximum ball diameter of the ball head. Therefore, even if the plastic material of the ball head receptacle 40D is damaged, the steel-to-steel connection ensures that the ball head is securely held within the slide assembly 26.

[0095] Figure 34D shows the arrangement of two fastening pins aligned parallel to each other. The fastening pins are located within notches 39D on the ball head receptacle 40D. The notches 39D are located above the flexible element 40F, and the ball head receptacle 40D surrounds the ball head of the ball bolt 38.

[0096] In Figure 35, a cross-sectional view shows the drive element 16, which is integrally mounted with the motor shaft 42, positioned on or within the housing 24 or drive housing 84. It should be noted again that the drive housing 84 is considered part of the housing 24 and can be optionally formed integrally with the housing 24. The drive element 16 has a free end 16A extending from the end of the worm of the drive element 16 that meshes with the worm wheel 18. The drive element 16 is preferably preloaded axially via the axial end 16A to compensate for high tolerances of the drive element 16 or the motor shaft. Specifically, the drive element 16 is therefore mounted in a manner that is preloaded axially with respect to the drive housing 84.

[0097] For this purpose, the plastic element 46 is preferably positioned between the free end 16A of the drive element 16 and the drive housing 84. The plastic element 46 is shown in detail in Figure 36A. Specifically, the plastic element 46 may contain an elastomer and therefore can function as an elastic damping element. The plastic element 46 is preferably housed in a sleeve 46A positioned between the free end 16A of the drive element 16 and the drive housing 84. The arrangement of the sleeve 46A between the drive housing 84 and the drive element 16 or its free end 16A can be clearly seen in Figure 35. Furthermore, in Figure 36B, the axial play of the drive element 16 or motor shaft is symbolically represented by a double arrow. This axial play can vary considerably within a series due to manufacturing tolerances, making tolerance compensation advantageous. The axial play is indicated by a double arrow extending parallel to the axial direction A of the drive element 16.

[0098] In the cross-sectional view of Figure 36C, a sleeve 46a is shown, which has a recess 46B on the side facing away from the drive element 16. The recess 46B is preferably annular, and the plastic element 46 is received within the recess. The depth of the recess 46B is dimensioned to be less than the diameter of the plastic element 46. In this way, the plastic element 46 protrudes axially A beyond the edge of the sleeve 46A. The depth of the recess 46B can be adjusted via a rib 46D that protrudes upward from the bottom of the recess 46B. The upper side of the rib 46D, together with the edge of the sleeve 46A, forms a support 46C that defines the depth of the recess 46B. This recess is preferably less than the diameter of the plastic element 46. Thus, the rib 46D forms a support 46C for the plastic element 46 in the recess 46B. The ribs 46D are arranged radially, as can be seen in Figure 36D. Rib 46D extends from a central extension 46E, which is provided for clamping the plastic element 46 in the center. The central extension 46E is substantially frustoconical (Figure 36C). Starting from the bottom 46C of the recess 46B, the central extension 46E tapers toward the edge of the sleeve 46A. At the front end of the central extension 46E, there is an axial stop 47A that defines the end stop of the axial play of the drive element A relative to the drive housing 84 4.

[0099] The sleeve 46A is preferably positioned to be fixed to the drive housing 84 by rotation. For this purpose, a rotation prevention mechanism 46G can be provided on the side 46F of the sleeve 46A. The rotation prevention mechanism 46G can be designed to correspond to a corresponding stop in the drive housing 84. Specifically, the rotation prevention mechanism 46G can be molded as a ridge or rib that firmly engages with a corresponding notch in the drive housing 84. The axial preload between the drive housing 84 and the drive element 16 can also be achieved in an alternative manner. Generally, a bearing space 16C is provided between the drive element 16, particularly its free end 16A, and the drive housing 84. When the assembly of the sleeve 46A and the plastic element 46 is used as a preloading device to achieve the axial preload of the drive element 16 to the drive housing 84, the assembly of the sleeve 46A and the plastic element 46 is positioned within this bearing space 16C, as can be seen particularly in Figure 37C of an exemplary embodiment described later.

[0100] However, in alternative modifications (Figures 37A to 38), it is assumed that the bearing space 16C is filled with a curable plastic material. Therefore, the axial preload is achieved by introducing the plastic material into the bearing space 16C in a liquid state after the drive element 16 has been inserted into the drive housing 84, where it is cured. This compensates for the tolerance between the drive element 16 and the drive housing 84. For this purpose, it is preferably assumed that a bushing 16D is positioned at the free end 16A of the drive element 16. Such a bushing 16D is shown in Figure 38. The bushing 16D has an axial mounting portion 16G that is directly connected to the drive element 16. On the opposite side of the axial mounting portion 16G, the bushing 16D has a toothed extension 16E. Specifically, the toothed extension 16E is positioned to face outward from the drive element 16 in the direction of the bearing space 16C. In other words, the toothed extension 16E protrudes into the bearing space 16C. A sealing element 16F, such as an O-ring or a molded seal, is positioned between the tooth-like extension 16E and the axial mounting portion 16G, and extends circumferentially around the bushing 16D. The tooth-like extension 16E and the axial mounting portion 16G preferably have a plurality of ribs on their outer circumference, and these ribs secure the sealing element 16F in the axial direction.

[0101] The axial preload is achieved by the bushing 16D, in which the bearing space 16C is filled with plastic material after the bushing 16D is inserted into the drive housing 84 together with the drive element 16. The liquefied plastic material fills the space between the bearing space 16C and the toothed extension 16E. When filling with the liquid plastic material, air can escape through the space between the toothed extensions 16E, thus preventing the undesirable formation of air pockets and ensuring a uniform distribution of the liquid plastic material within the upper part of the bushing 16D. A sealing element 16F in the form of an O-ring prevents the liquid plastic material from flowing out of the upper part of the bushing 16D and escaping from the bearing space 16C. As the plastic material in the bearing chamber 16C hardens, the axial preload of the drive element 16 is created. At the same time, a secure and dynamic connection is achieved between the hardened plastic material and the toothed extension 16E, resulting in the creation of an anti-rotation mechanism between the drive housing 84 and the bushing 16D. Because the drive element 16 adheres to high tolerances, it is impossible to reliably determine the amount of plastic material that must be introduced into the bearing space 16C over a series of times. In this regard, preferably in this modification, it is assumed that the drive housing 84 is also adapted accordingly so that the curable plastic material can be introduced into the bearing space 16C. The corresponding drive housing 84 is shown in Figures 37A and 37B. The drive housing 84 comprises a storage tank 84B. The storage tank 84B is preferably located outside the drive housing 84. Specifically, the storage tank 84B may be substantially designed as a ball-shaped pocket outside the drive housing 84. At the bottom of the storage tank 84B, there is preferably an opening 84A connected to the bearing space 16C. Thus, the curable plastic material can be introduced into the bearing space 16C via the storage tank 84B and the opening 84A. When the curable plastic material is introduced into the bearing space 16C, the air in the bearing space 16C is simultaneously displaced. To allow air to escape, the storage tank 84B has an outlet opening 84C at its bottom.Air escapes from the bearing space 16C through the outlet opening 84C, and as a result, the aforementioned bearing space can be fully filled with the curable plastic material. The storage tank 84B is used as a reservoir or excess storage for the curable plastic material that remains as residue when the bearing space 16C is filled. In this way, a uniform amount of curable plastic material can be introduced to fill the bearing space 16C, and the amount of curable plastic material that can actually be introduced into the bearing space varies due to the component tolerances of the drive element 16. The excess portion of the curable plastic material is then stored in the storage tank 84B, where it hardens.

[0102] Figures 39A to 41 show the mounting of the spindle nut 22 within the slide assembly 26 according to a preferred exemplary embodiment. Generally, the spindle nut 22 is mounted in a tiltable manner within the slide assembly 26. Specifically, the spindle nut 22 is mounted so as to be tiltable around a tilt axis K which is aligned perpendicular to the rotation axis R of the spindle 20. The rotation axis R is shown in Figures 39A and 39B. The tilt axis K is shown in Figures 39B, 40, and 41.

[0103] As shown in the side view of Figure 41, the spindle nut 22 has a first outer circumference 43 and a second outer circumference 45 in its cross-section. The first outer circumference 43 and the second outer circumference 45 each have a common center M on the inclination axis K. The first outer circumference 43 is larger than the second outer circumference 45. Corresponding to the two outer circumferences 43, 45, the slide assembly 26 has corresponding inner contours 44. Specifically, the slide assembly 26 has inner contours 44 corresponding to the first outer circumference 43 and the second outer circumference 45, allowing the first outer circumference 43 and the second outer circumference 45 to be guided during the inclination motion of the spindle nut 22 around the inclination axis K.

[0104] In particular, it is assumed that the inner contour 44 has a first partial surface 44A corresponding to the first outer circumference 43. Furthermore, a second partial surface 44B corresponding to the second outer circumference 45 is provided on the inner contour 44. A transition surface 44C is provided between the first partial surface 44A and the second partial surface 44B. The transition surface 44C connects the first partial surface 44A to the second partial surface 44B.

[0105] The transition surface 44C is designed to restrict the tilting motion around the tilt axis K. Due to the different outer circumferences of the spindle nut 22, the transition surface 44C acts as a stopper for the tilting motion of the spindle nut 22. When the spindle nut 22 is at its maximum tilt, the aforementioned spindle nut rests on the transition surface 44C. This state is shown in Figure 40. It can be seen that the spindle nut 22 is fully tilted and therefore in contact with the transition surface 44C. In this state, the spindle nut 22 can be inserted into the corresponding nut receptacle of the housing 24. As shown in Figure 41, as soon as the spindle nut 22 is deflected from its maximum tilt, i.e., as soon as it is aligned with the spindle 20, the contour, in particular the transition surface 44C, fixes the spindle nut 22 against displacement of the slide assembly 26 within the housing 24. In other words, the inner contour 44 of the slide contour acts as a bayonet lock 22A for the spindle nut 22. For this purpose, the bayonet lock 22A has a first stop 22B formed on the first side 26A of the slide assembly 26. A second stop 22C is formed on the second side 26B of the slide assembly, which is also part of the bayonet lock 22A. The first stop 22B and the second stop 22C, which together form the bayonet lock 22A, can be clearly seen in Figure 39A. In particular, it is assumed that the first stop 22B and the second stop 22C are positioned diagonally opposite each other with respect to the slide assembly 26. Therefore, at its maximum inclination position, the spindle nut 22 can be inserted laterally into the slide assembly 26 (Figures 39B and 40). When the spindle nut 22 is positioned in the slide assembly 26 and deflected from the maximum inclination position, the first stop 22B and the second stop 22C prevent the spindle nut 22 from moving laterally out of the slide assembly 26.

[0106] Preferably, the first stopper 22B and the second stopper 22C are manufactured integrally with or monolithically with the slide assembly 26. In particular, the slide assembly 26 having the stoppers 22B and 22C can be manufactured by an injection molding process or by forming an injection molded part.

[0107] Figure 42 shows the end of the adjustment element 28 opposite to the slide assembly 26. The adjustment element 28 has a joint bearing 52 at the end opposite to the slide assembly 26, which is designed to be fastened to a vehicle component or vehicle body. For this purpose, the joint bearing 52 has a joint bearing insert 60, which encloses the joint bearing 52 of the adjustment element 28 internally and forms a receptacle 60A for a joint bolt 54, which is shown in more detail in Figure 49. The joint bearing insert 60 can basically be formed integrally or monolithically. However, it is advantageous if the joint bearing insert 60 comprises a first joint bearing insert element 61 and a second joint bearing insert element 62. The first joint bearing insert element 61 and the second joint bearing insert element 62 can be connected to each other in a rigidly coupled or confirmably coupled manner. The two-part design of the joint bearing insert 60 has the advantage that the first joint bearing insert element 61 can be inserted into the joint bearing 52 from the first side, while the second joint bearing insert element 62 can be inserted into the joint bearing 52 from the second side. The joint bearing insert elements 61 and 62 can be connected to each other within the joint bearing 52 in order to jointly form the joint bearing insert 60. Preferably, the joint bearing insert 60, in particular the first joint bearing insert element 61 and the second joint bearing insert element 62, are formed from a plastic material. The plastic material may have elastic properties in particular. It is particularly preferable if the centering contour 59B includes a plastically deformable material, such as a plastic material. The centering contour 59B is used in particular to compensate for angular errors between the adjustment element 28 and the vehicle part or body. Such angular errors may occur between the vehicle part and the body due to the sum of all tolerance chains and should be compensated for by the degrees of freedom of movement in the corresponding tilt and inclination directions.At the same time, the joint bearing insert is for supporting the tightening torque of the screws on the retaining plate 56 without requiring a mounting template. However, the advantage of not using a mounting template is that assembly can be carried out particularly quickly and easily. In this regard, the centering contour 59B can be sealed in the desired manner during the process of further application to initially support the tightening torque and allow freedom of movement in the corresponding tilt and inclination directions, thus providing considerable simplification during the installation of the adjustment device in the vehicle.

[0108] The centering contour 59B may have a plurality of projections 59A that align with the joint bolt 54. If an angular error occurs during assembly, the individual projections 59A of the centering contour 59B will flex accordingly, thus allowing the bolt to be aligned within the joint bearing insert 60. Therefore, the joint bearing insert 60 having the centering contour 59B ensures that an inclined arrangement between the joint bolt 54 and the adjustment element 28 is permitted, or that the pivotal movement of the adjustment element 28 relative to the joint bolt 54 is not impaired.

[0109] Referring to Figure 43, it can be assumed that the joint bearing insert 60 has a clamping unit 60E for clamping a joint bolt 54 that can be inserted into the bolt receptacle 60A. The clamping unit 60E may have an elastic clamping element 60F positioned on the edge of the joint bearing insert 60. As can be seen in Figure 43, the clamping unit 60E can be inserted into the upper region of the first joint bearing insert element 61. The joint bearing insert 60 substantially comprises a bolt receptacle 60A having an insertion opening through which the spherical portion 54C of the joint bolt 54 can be inserted. Similarly, a clamping unit 60E is provided to prevent the joint bolt 54 from detaching from the bolt receptacle 60D. The aforementioned clamping unit is inserted into the first joint bearing insert element 61 above the bearing 60G shown in Figure 44, and therefore prevents axial movement of the joint bolt 54 from the bolt receptacle 60A.

[0110] Figure 44 shows a cross-sectional view of how the joint bolt 54 is coupled to the joint bearing insert 60 via the bearing 60G. Furthermore, from Figure 44, it can be seen that the joint bolt 54 not only passes through the joint bearing 52 but also extends through the retaining plate 56, thereby creating a connection between the retaining plate 56 and the adjustment element 28. This is again shown in the perspective view of Figure 45. In addition, from Figures 42 to 48, it can be seen that the joint bearing insert 60 has a snap-fit ​​connector element 60H that can in any case secure a sealing element 82 used, for example, to seal an opening in vehicle sheet metal. As an example, Figure 57B shows such a sealing element 82 held on the adjustment element 28 by the snap-fit ​​connector element 60H.

[0111] Figures 47 and 48 show two joint bearing insert elements 61 and 62 in detail. With respect to the first joint bearing insert element 61 (Figure 47), the axial AR is shown. It can be seen that the projection 59A is formed as a rib extending parallel to the axial AR. The joint bearing insert 60 has a continuous bolt receptacle 60A that can receive a joint bolt 54. A bayonet connector is preferably provided to connect the joint bolt 54 to the joint bearing insert 60. The joint bolt 54 inserted into the bolt receptacle 60A can be positioned by the bayonet connector.

[0112] Figures 47 and 48 also show that the joint bearing insert 60, and in particular the joint bearing insert elements 61 and 62, each have a first lock lug 60B and a second lock lug 60C, which are positioned opposite each other on the edge of the joint bearing insert 60 or the corresponding joint bearing insert elements 61 and 62. The lock lugs 60B and 60C are used as bayonet connectors for securing the spherical portion 54C of the joint bolt 54. A joint bolt 54 having the spherical portion 54C is shown in Figure 49.

[0113] The first lock lug 60B and the second lock lug 60C may be formed adjacent to the bearing 60D, which is located inside the bolt receptacle 60A and receives at least a partially spherical portion 54C of the joint bolt 54. The bearing 60D is preferably formed corresponding to the spherical portion 54C of the joint bolt 54. Thus, the joint bolt 54 preferably has two bulges 54A arranged to face away from each other, which are designed to correspond to the first lock lug 60B and the second lock lug 60C. In this way, a bayonet connection is created between the joint bolt 54, in particular the bulges 54A, and the lock lugs 60B, 60C. Designs having only one lock lug 60B are also conceivable and cannot be excluded within the scope of the present invention.

[0114] The bolt receptacle 60A within the joint bearing insert 60 may have at least one notch 60D used as a lubricant reservoir. The notch 60D is shown as an example in Figure 46. Figure 47 shows that the notch 60D is preferably located within the first joint bearing insert element 61.

[0115] Figure 49 shows a retaining bolt 54 having a spherical portion 54C, where one of the two bulges 54A can be seen within the spherical portion 54C. At the upper end, the retaining bolt 54 has a retaining plate opposing contour 54B. The shape of the retaining plate opposing contour 54B corresponds to the inner contour of the retaining plate contour 56A of the retaining plate 56. The retaining plate 56 is shown in Figure 50. In particular, it can be seen that the retaining plate 56 has two through openings, one of which is formed using the retaining plate contour 56A. The retaining plate contour 56A is substantially designed as an elliptical inner contour that engages in a confirmatory manner with the corresponding elliptical outer contour of the retaining plate opposing contour 54B. Thus, the retaining bolt 54 can be fixed in place so as not to rotate and connected to the retaining plate 56 using a defined basic alignment.

[0116] Figure 51 shows the connection between the adjustment element 28 and the retaining plate 56. At the end opposite to the slide assembly 26, the adjustment element 28 has a joint bearing 52, and a joint bearing insert 60 is positioned within the joint bearing 52. The retaining bolt 54 passes through the retaining plate 56, through the bolt receptacle 60A of the joint bearing insert 60, and then engages with a second through-opening in the retaining plate 56. In addition, the open position of the bayonet lock is visible in the arrangement shown in Figure 51. This is illustrated by the cross-sectional view in Figure 52. In this position, the joint bolt 54 can move axially within the joint bearing insert 60. This is the mounted position. Subsequently, by rotating the retaining plate 56 containing the joint bolt 54, the bayonet lock is locked, and therefore, axial movement of the joint bolt 54 relative to the joint bearing insert 60 is prevented.

[0117] With respect to the joint bearing insert 60, in all exemplary embodiments, the first joint bearing insert element 61 and the second joint bearing insert element 62 can be connected to each other in a manner that is either firmly or securely coupled. In the case of a firmly coupled connection, it is particularly preferable that the first joint bearing insert element 61 and the second joint bearing insert element 62 can be connected to each other by a screw connection. For this purpose, the first joint bearing insert element 61 may have, for example, a male thread that cooperates with the corresponding female thread of the second joint bearing insert element 62.

[0118] Figures 53 and 54 show further exemplary embodiments relating to the closure of the housing 24 of the slide assembly 26 by a cover 64. The housing 24 is preferably designed as an extruded product and therefore has an open axial end. Thus, a cover 64 is provided to prevent both moisture and dust from entering the housing 24. Specifically, the housing 24 has a housing opening 24C (Figure 27) that can be sealed by the cover 64. The cover 64 preferably has projections 64A that can be connected to the receptacle 37A of the housing 24. Thus, the projections 64A, in their basic contour, preferably correspond to the guide elements 37C, 37D, and 37E of the guide device 37B, and as a result, the projections 64A can be inserted into the longitudinal grooves 37 of the receptacle 37A. Preferably, a plurality of such projections 64A are formed on the cover 64. In particular, the number of projections 64A preferably corresponds to the number of longitudinal grooves 37 of the housing 24. In the specific exemplary embodiments shown in Figures 53 and 54, seven projections 64A are provided, each cooperating with seven longitudinal grooves 37. To facilitate insertion of the projections 64A into the longitudinal grooves 37, the projections 64A preferably have a conical or frustoconical taper at their free ends. Furthermore, it can be assumed that the cover-side projections 64A include preloading elements 64H in the form of ribs formed longitudinally along the projections 64A. The preloading elements 64H, similar to the preloading elements 37H, are preferably formed monolithically with the projections 64A. The projections 64A may also be formed monolithically with the cover 64. To secure the cover 64 to the housing 24, it can be assumed that the longitudinal grooves 37 are crimped in the area into which the projections 64A are inserted. By crimping the longitudinal groove 37, that is, by reshaping it, a secure connection to the protrusion 64A is created, and therefore the cover 64 is firmly attached to the housing 24.

[0119] Figure 53 also shows that the cover 64 has a drainage opening 64C. Since it is not possible to completely prevent moisture from entering the housing 24, particularly condensation, the drainage opening 64C is provided. The aforementioned drainage opening allows moisture to be discharged from the housing 24. As already described in relation to Figure 24, the slide assembly 26 preferably has a piston geometry 72 whose outer contour corresponds to the inner contour of the drainage opening 64C, and as a result the piston geometry 72 seals the drainage opening 64 at the end position of the slide assembly 26. For this purpose, it is advantageous to assume that the piston geometry 72 has a radial seal 73.

[0120] The preloading element 64H on projection 64A is used, on the one hand, to compensate for tolerances and thus to ensure a secure, rattle-free fastening of the cover 64. At the same time, the preloading element 64H provides preload, which also reduces any rattle noise.

[0121] The cover 64 further comprises a collar 64B, which surrounds the longitudinal end of the housing 24 with its outer circumference, thus further inhibiting the intrusion of moisture into the housing 24. In this respect, the collar 64B is water-repellent.

[0122] Figures 55 to 57B show an embodiment of the adjustment device 10 in which a sealing element 82 is located on the adjustment element 28. The sealing element 82 can be fastened to the adjustment element 28 by a snap-fit ​​connector 60H, particularly as shown in Figure 48. The sealing element 82 is used, in particular, to seal a first cavity, preferably a vehicle cavity, that receives a joint bearing 52. Specifically, the sealing element 82 is used to seal the opening of the first cavity. The sealing element 82 can be locked into the joint bearing insert 60 by the snap-fit ​​connector 60H. The sealing element 82 completely surrounds the adjustment element 28 to ensure a good seal between the adjustment element 28 and the opening of the first cavity. Additionally or alternatively, the sealing element 82 can be movable relative to the vehicle body and provided for sealing a second cavity of the body or vehicle component in which the adjustment device 10 is located.

[0123] As can be seen in Figure 55, the sealing element 82 has a first sealing lip 82A that rests directly on the adjustment element 28. Furthermore, a second sealing lip 82B is provided, positioned along the circumferential direction of the sealing element 82. The second sealing lip 82B seals against the opening of the vehicle cavity. Generally, the sealing element 82 comprises a base body 82D extending within the base plane G. Furthermore, a central body 82E is provided, which surrounds the adjustment element 28 and includes the first sealing lip 82A. The central body 82E is oriented along the longitudinal direction L of the adjustment element 28. The longitudinal direction L of the adjustment element 28 can be seen in Figure 57B.

[0124] In Figure 57A, it is clearly visible that the base surface G of the base body 82D and the longitudinal direction L of the adjustment element 28 are positioned at angles different from 90° to each other. This involves the oblique alignment of the central body 82E with respect to the plane containing the second seal lip 82B. This inclination or oblique arrangement is particularly advantageous for sealing the vehicle cavity that receives the joint bearing 52. The adjustment device is preferably used to operate a vehicle door or vehicle flap that is positioned obliquely to the vehicle body when open. This angular alignment may be compensated for by the oblique arrangement of the second seal lip 82B with respect to the central body 82E, and as a result, the seal element 82 ensures a permanently good seal.

[0125] Figure 57A also shows that the seal element 82 has a locking arrangement 82C that cooperates with the snap-type connecting element 60H of the joint bearing insert 60 to create a secure and dynamic connection between the seal element 82 and the joint bearing insert 60. Furthermore, the central body 82E can be positioned off-center on the base body 82D.

[0126] Figures 58 and 59 also show a seal arrangement 34 (already shown in Figure 22) that completely encloses the adjustment element 28 and protects the inside of the housing 24 from environmental influences. The seal arrangement 34 has fastening portions 67 that can fasten the seal arrangement 34 to the housing 24. Furthermore, a bellows portion 69 is provided to ensure the mobility of the seal arrangement 34. In particular, the tilting movement of the adjustment element 28 relative to the housing 24 can therefore be compensated. Furthermore, a wiper portion 68 is provided that slides along the adjustment element 28 but at the same time forms a sliding seal.

[0127] Preferred markings are provided for the adjustment device 10 so that it can be clearly identified even when installed, without the need to remove it from the vehicle or side door, for example, by a factory employee. However, since these markings should not be visible to the vehicle's end customer, either in place of or in addition to the adjustment element 28, the sealing element 82 can, advantageously, be labeled on the side wall facing away from the vehicle's passenger compartment when installed. When installed, this side wall of the sealing element 82 faces, for example, the side door and is not visible to the vehicle's end customer / driver. If the adjustment device 10 is tilted 180° and positioned on the other side of the vehicle, the markings are also located on the side wall of the sealing element 28 facing away from the passenger compartment.

[0128] A further advantageous labeling method is to label the sealing element 28 with a suitable lacquer, which can only be visualized using a suitable light source. For example, a UV varnish that is only visible using a UV lamp can be used.

[0129] Figures 60 and 61 show exemplary embodiments of an adjustment device 10 in which a slide assembly 26 has two guide portions 32. The first left guide portions 32A, 32B are opposite the second right guide portion 32B. The guide portions 32A, 32B are used to guide the slide assembly 26 within the housing 24. Each of the two guide portions 32A, 32B is assigned a guide rail 74A, 74B that is positioned without play. Each of the guide rails 74A, 74B has a prismatic shape and thus forms a prismatic sliding surface or guide surface 75, which cooperates with the sliding surface or guide surface 77 of the housing 24 (see Figure 26). In particular, the guide rails 74A, 74B preferably have a trapezoidal outer contour on the side facing the inner surface of the housing. In addition to two opposing guide portions 32A, 32B and their respective assigned guide rails 74A, 74B, a third guide portion 32C can be provided to guide the slide assembly 26 within the housing. Thus, the three guide portions 32A, 32B, and 32C can substantially form a three-point sliding bearing within the housing 24. The third guide portion 32C also preferably has a guide rail 74C. Each of the guide rails 74A, 74B, and 74C is positioned without play on the guide portions 32A, 32B, and 32C assigned to them. It is also possible that one of the guide rails 74, 74A, and 74B is formed integrally with the corresponding guide portion 32A, 32B, and 32C.

[0130] In the exemplary embodiments shown in Figures 60 and 61, at least one of the guide rails 74A, 74B, and 74C, particularly the guide rail 74B of the second guide portion 32B, has an auto-adjustable play reduction means. Preferably, the opposite guide rail 74B may also have such an auto-adjustable play reduction means. Each auto-adjustable play reduction means preferably comprises an elastic spring element 80 as shown in Figure 26. The elastic spring element 80 can act on a compensation element 76 designed to be relatively movable between at least one guide rail 74 and a prismatic guide surface 77 in the form of a corresponding sliding surface of the housing 24. The compensation element 76 may specifically comprise a first compensation element 76A and a second compensation element 76B, which are formed independently of each other. The compensation elements 76A and 76B are preferably arranged along the guide rails 74A, 74B, and 74C, offset and spaced apart from each other in the longitudinal direction. The compensation elements 76, 76A, and 76B are preferably preloaded by the spring element 80, pressing against the inner guide surface 77 of the housing 24, thereby achieving tolerance compensation. Therefore, the slide assembly 26 is well guided within the housing 24, and noise generation due to play is avoided. In addition to the absence of play, the prismatic design can provide improved stability of the slide assembly 26 within the housing 24, resulting in uniform linear motion independent of external forces. This is based on the principle of a physical wedge, where a small holding force of the spring element 80 holds a large displacement force.

[0131] Furthermore, the compensation element 76, which is preloaded onto the housing 24 by the spring element 80, is used as a defined linear brake on the moving axis of the adjustment element 28 by a defined friction / braking force that works in coordination with the adjustment device 10. The friction generated therein dampens the entire system of the adjustment device 10, allowing for better control by external control and thereby avoiding noise generation. Because the system design is simple and modular, the spring element 80 can be easily replaced and designed to suit the specific requirements of the adjustment device 10. Similar to the embodiments shown in Figures 25 and 26, this embodiment allows for substantially playless linear guiding of the slide assembly 26 and a defined constant friction torque between the slide assembly 26 and the housing 24, as well as the ability to fully or partially achieve the required retaining force of, for example, a vehicle door. Thus, the friction introduced into the slide assembly 26 can replace a separate brake, such as a magnetic brake, in the area of ​​the drive unit 14. A further advantage of adding friction at this point of action of the adjustment device 10 is a uniform base load, which leads to quieter operation of the entire system.

[0132] Each compensation element 76, 76A, and 76B may also have an assembly step 76C so that the slide assembly 26 can be inserted into the housing 24. The assembly step 76C displaces the compensation elements 76, 76A, and 76B inward against the spring force of the spring element 80 when the slide assembly 26 is inserted into the housing 24, and then the spring element 80 places them on the guide surface 77 inside the housing 24. On the side facing away from the guide surface 77, each compensation element 76 may additionally have a locking pin 81 for securing the ball bolt 38 inserted into the ball socket 40. Thus, the locking pin 81 can substantially form a fastening element 39C that holds the partially spherical portion of the ball bolt 38 in the ball socket 40 (Figure 34). In this way, the compensation element 76 provides a dual function: on the one hand, tolerance compensation for the slide assembly in the housing 24, and on the other hand, fastening of the ball bolt 38 in the ball socket 40.

Claims

1. An adjustment device (10) for a vehicle component that is movable relative to the vehicle body, particularly for a vehicle door or vehicle flap, A housing (24) having a slide assembly (26), wherein the slide assembly (26) can be moved between a first position and a second position by a drive unit (14), The slide assembly (26) and the adjustment element (28), which is designed to be connectable to the body of the vehicle or a vehicle component that is movable relative to the body of the vehicle, An adjustment device (10) comprising a fastening element (36) for fastening the adjustment device (10) to the body of a vehicle or a vehicle component that is movable relative to the body of the vehicle, wherein the fastening element (36) is designed to be connectable to the housing (24) in a frictional and / or positive-movement manner.

2. The adjustment device (10) according to claim 1, wherein the housing (24) has at least one receptacle (37A) for guiding the fastening element (36) along the longitudinal direction (L) of the housing (24).

3. The adjustment device (10) according to claim 2, wherein the fastening element (36) comprises at least one guide device (37B) for insertion into the receptacle (37A).

4. The adjustment device (10) according to claim 3, wherein the guide device (37B) has a first guide element (37C) and a second guide element (37D).

5. The adjustment device (10) according to claim 4, wherein the first guide element (37C) and the second guide element (37D) can be inserted into the receptacles (37A) located on both sides of the housing (24) in a cross-sectional view.

6. The adjustment device (10) according to claim 4 or 5, wherein the receptacle (37A) of the housing (24) has at least two longitudinal grooves (37) corresponding to the first guide element (37C) and the second guide element (37D).

7. The adjustment device (10) according to any one of claims 4 to 6, wherein the guide elements (37C, 37D) are arranged parallel to each other.

8. The adjustment device (10) according to any one of claims 1 to 7, wherein at least one guide element (37C, 37D, 37E) is formed conically at a first end (37F) and a second end (37G).

9. The adjustment device (10) according to any one of claims 1 to 8, wherein the guide elements (37C, 37D, 37E) have a preloading element (37H) for generating a preload on the fastening element (36) to the housing (24).

10. The adjustment device (10) according to any one of claims 1 to 9, wherein the fastening element (36) is fixed to the housing (24) by crimping a receptacle (37A) having inserted guide elements (37B, 37C, 37D, 37E).

11. The adjustment device (10) according to any one of claims 1 to 10, wherein the fastening element (36) is fixed to the housing (24) by riveting.

12. The adjustment device (10) according to any one of claims 1 to 11, wherein the housing (24) is made from an aluminum profile.

13. The adjustment device (10) according to any one of claims 1 to 12, wherein the fastening element (36) has a threaded portion (36A) having a funnel-shaped supply portion (36B) for fastening to the body of a vehicle or a vehicle part that is movable relative to the body of a vehicle.

14. The adjustment device (10) according to claim 13, wherein the fastening element (36) is manufactured by an injection molding process, and the threaded portion (36A) has an overmolded nut.

15. The adjustment device (10) according to any one of claims 1 to 14, wherein the fastening element (36) comprises a cable holding means (37I), particularly a cable clip.

16. A vehicle (200) having an adjustment device (10) for a vehicle component that is movable relative to the body of the vehicle, particularly for a vehicle door or a vehicle flap, according to any one of claims 1 to 15.

Images