EP4240599A1

EP4240599A1 - Trailer coupling with a brake device

Info

Publication number: EP4240599A1
Application number: EP21802305.9A
Authority: EP
Inventors: Jonathan Charles Edwards; John Charles Murphy
Original assignee: Westfalia Automotive GmbH
Current assignee: Westfalia Automotive GmbH
Priority date: 2020-11-03
Filing date: 2021-10-28
Publication date: 2023-09-13
Also published as: WO2022096378A1; DE102020134914A1

Abstract

The invention relates to a trailer coupling for a motor vehicle (90), comprising a coupling arm (20). The coupling arm (20) has a coupling element (27), in particular a coupling ball (27A), and is pivotally mounted on a mounting (11), which is fixed or can be fixed to the motor vehicle (90), between a use position (G) and a non-use position (N) by means of a pivot bearing (30). In the use position (G), which is provided for suspending a trailer (AK) or securing a load carrier (LT) to the coupling element (27) of the coupling arm (20), the coupling arm (20) protrudes further rearwards from the rear (95) of the motor vehicle (90) than in the non-use position (N), which is provided for when the coupling arm (20) is not in use, wherein the mounting (11) has a pivot bearing section (32A) for the pivot bearing (30), and a coupling arm bearing element (50) which supports the coupling arm (20) is pivotally mounted on the pivot bearing about a pivot axis (D). The trailer coupling (10) has a brake device (70) for braking a pivoting movement of the coupling arm bearing element (50) with respect to the mounting (11) during the pivoting movement between the use position (G) and the non-use position (N), said brake device having a braking body (72) and a braking contour (71) for interacting with the braking body (72). The braking body (72) and the braking contour (71) slide against each other during the pivoting movement of the coupling arm bearing element (50) between the use position (G) and the non-use position (N) and brake the pivoting movement. The braking contour (71) and the braking body (72) are designed such that the braking contour (71) and the braking body (72) exert at least two different braking forces onto the coupling arm bearing element (50) during the pivoting movement between the use position (G) and the non-use position (N).

Description

Trailer coupling with a braking device

The invention relates to a trailer coupling for a motor vehicle with a coupling arm, the coupling arm having a coupling element, in particular a coupling ball, and being pivotably mounted on a holder which is or can be attached to the motor vehicle by means of a pivot bearing between a use position and a non-use position, the coupling arm being in the position of use for attaching a trailer or attaching a load carrier to the coupling element of the coupling arm protrudes further to the rear in front of a rear end of the motor vehicle than in the non-use position provided for when the coupling arm is not in use, the holder having a pivot bearing section for the pivot bearing, on which a Coupling arm bearing element is mounted pivotably about a pivot axis, the trailer hitch having a braking device for braking a pivoting movement of the coupling arm bearing element with respect to the holder at the S pivoting movement between the use position and the non-use position, which has a brake body and a brake contour for interaction with the brake body, the brake body and the brake contour sliding along one another during the pivoting movement of the coupling arm bearing element between the use position and the non-use position and braking the pivoting movement.

Such a trailer hitch is explained, for example, in EP 1 621 371 A2. An end face of a sealing element of the hitch slides in the pivoting adjustment or pivoting movement of the coupling arm bearing element relative to the holder along an opposite surface, whereby a certain braking effect is achieved. However, the basic function of the sealing element is a sealing of the swivel bearing and not the braking function.

Proceeding from this, it is the object of the invention to provide an improved trailer hitch.

To solve this problem, a trailer hitch of the type mentioned at the outset provides for the brake contour and the brake body to be designed in such a way that the brake contour and the brake body exert at least two different braking forces on the coupling arm bearing element during the pivoting movement between the position of use and the position of non-use.

A pivoting movement between the use position and the non-use position includes, for example, a pivot movement from the use position to the non-use position and/or a movement from the non-use position to the use position.

The pivoting movement between the use position and the non-use position takes place in particular after leaving a fixing position of the coupling arm bearing element or in a release position of the coupling arm bearing element. In the fixing position, the coupling arm is fixed in place with respect to the carrier using, for example, a fixing device. In the release position, the clutch arm bearing element is movable with respect to the carrier between the use position and the non-use position. The braking contour exerts the at least two different braking forces in the release position of the fixing device or the coupling arm bearing element with respect to the carrier, i.e. when the coupling arm bearing element that is movable or rotatable or pivotable per se is adjusted between the use position and the non-use position. It is particularly preferred if the coupling arm bearing element is immovable with respect to the carrier along the pivot axis. This non-displaceability can be permanent, ie the pivot bearing supports the coupling arm bearing element with respect to the carrier along the pivot axis immovable, but pivotable about the pivot axis. However, it is also possible that the immovability is present only in the release position, ie that the coupling arm bearing element is mounted displaceably with respect to the carrier between the fixing position and the release position along the pivot axis, but is immovable with respect to the pivot axis in the release position.

An individual braking effect can thus be achieved, so that, for example, before the use position or the non-use position is reached, the braking effect or braking force is smaller, but in an intermediate section of the adjustment movement or the pivoting path, in particular when the coupling arm assumes a lower intermediate position between the non-use position and the use position , a higher braking effect than in the non-use position and / or use position is achievable.

The holder is designed for attachment to the motor vehicle in such a way that the pivot axis of the pivot bearing is oriented such that the coupling arm is preferably at a greater distance from a road surface in the non-use position than in the use position. For example, the holder is held in a corresponding inclined position on a support, in particular a cross member, which can be mounted or is mounted on the rear of the motor vehicle.

It goes without saying that several braking contours can be present, along which the braking body slides during the adjustment between the position of use and the position of non-use. The braking contours can have angular distances from one another, for example. For example, clearance sections can be provided between the brake contours, in which the brake body is not in engagement with a brake contour.

A braking effect of the braking device can be achieved and/or individually adjusted by a number of measures, which can be provided individually and in combination with one another. It is advantageous if at least one frictional engagement surface is provided on the brake body and/or the brake contour to provide a braking force by frictional engagement. For example, the brake body slides frictionally along the brake contour. Braking surfaces or friction surfaces can be provided on the brake body and the brake contour.

Furthermore, a braking effect can be achieved by elastic deformation of a base material of the brake body and/or the brake contour. It is advantageously provided that the brake body and/or the brake contour are elastically deformable to provide the braking forces, in particular in the sense of a flexing and/or a compression of the brake body or the brake contour or both.

The deformation can, for example, include or consist of a compression of the base material of the brake body and/or the brake contour. Furthermore, the deformation can also include or consist of a flexing deformation. In this case, for example, a section on which the brake contour is arranged is deflected in a direction away from the brake body when the brake body slides along the brake contour. For example, a wall on which the brake contour is arranged is deformed by the brake body. However, it is also possible for the brake body to be deformed by the brake contour, for example to be compressed or bent away from the brake contour.

The braking contour or the braking body can be formed, for example, by a braking element which exclusively fulfills a function of the braking device. For example, a frictional surface and/or an elastically deformable contour, for example made of rubber, elastic plastic or the like, can be arranged as a separate component on the holder or clutch arm bearing element and fulfill the function of the brake body or the brake contour.

The brake body and the brake contour are in braking engagement with one another along a contact path that extends in a ring shape around the pivot axis. To achieve the different braking forces, the contact path is, for example, shorter than a path of movement of the brake body, which the brake body runs through when the clutch arm bearing element is adjusted between the non-use position and the use position.

The braking contour can have geometrically different sections in order to influence the braking effect.

It is advantageously provided that the braking contour has contact surfaces arranged one behind the other with respect to the contact path for contact with the braking body, which protrude to different extents in the direction of the braking body and/or have different widths

For example, the brake contour can have a first section and a second section, which have contact surfaces of different widths when the brake body is in engagement with the respective section. Furthermore, the first section can protrude further in the direction of the brake body than the second section.

Furthermore, sections can be provided on the brake contour, along which the brake body slides with higher friction than on other sections, so that the braking effect is higher. For example, it can be provided that the brake contour has contact surfaces arranged one behind the other with respect to the contact path for contact with the brake body, which have different friction properties from one another. For example, one contact surface can be provided with a rubber coating or a soft, frictional coating, while the other contact surface allows the brake body to slide along more easily.

The brake body can be in one piece with the clutch arm bearing element or can be firmly connected to the clutch arm bearing element.

The brake contour is preferably arranged on a sealing element of the trailer hitch. Advantageously, it is provided that the brake body is held on the clutch arm bearing element so that it cannot rotate, and the brake contour, in particular a sealing element having the brake contour, is held on the holder so that it cannot rotate. The clutch arm bearing element, on the other hand, can be rotated relative to the brake contour or the sealing element in this embodiment. However, it is also possible that the brake body is arranged in a rotationally test manner on the holder and the brake contour or the sealing element is arranged in a rotationally test manner on the clutch arm bearing element.

The brake body is, for example, a body that protrudes radially outward with respect to the pivot axis and/or a body that extends radially, in particular a stop body.

It is advantageously provided that the brake body is formed by a stop body or is arranged on a stop body, the stop body limiting a pivoting movement of the coupling arm bearing element relative to the holder.

A preferred concept provides that a clearance section is provided between the braking contour and a pivot stop associated with the non-use position or the use position, in which the braking body is not braked or is braked less than in the area of the brake contour. In particular, it is advantageous if the brake body is completely released from the brake contour or the sealing element in the clearance section.

Advantageously, it is provided that a clearance section assigned to the position of use is longer than a clearance section assigned to the position of non-use, or vice versa. Due to the longer clearance section, the pivoting movement is slowed down less. The longer clearance section serves, for example, to enable the coupling arm or the coupling arm bearing element to optimally reach the respective end position, ie the position of non-use or the position of use. Thus, for example, a fixing device can develop its effect better or more easily, in which a fixing element in a form-fitting receptacle or fixing receptacle in the respective position of use tion or non-use position intervenes. It can only engage in the form-fitting receptacle when the fixing element is opposite the form-fitting receptacle in the use position or the non-use position. Optimum positioning of the fixing element with respect to the form-fit receptacle can be achieved by the length or design of the clearance sections.

In a movement segment between the end positions, i.e. the use position and the non-use position, in particular in the area of a lower intermediate position between the aforementioned positions, the braking effect of the braking device is advantageously greater than in the area of the use position and/or the non-use position. Thus, for example, the coupling arm can be braked by the brake device, ie the brake body, which is in engagement with the brake contour, when it assumes an intermediate position projecting downwards in front of a bumper of the motor vehicle. This measure helps to minimize the risk of injury to an operator.

A preferred concept provides that a slide-on section, in particular a ramp and/or an inclined surface, is arranged between the brake contour and at least one clearance section, on which the brake body can slide, starting from the clearance section, onto the brake contour.

As already explained, it is advantageous if the trailer hitch has a sealing element for sealing the trailer hitch, in particular the swivel bearing of the trailer hitch and/or the braking device. The sealing element thus fulfills the function of sealing the trailer hitch or sealing a component of the trailer hitch, for example sealing the swivel bearing.

A preferred concept provides that the sealing element is provided and designed for sealing the pivot bearing.

The sealing element preferably serves to seal the or a braking device for braking a pivoting movement of the coupling arm bearing element with respect to the holder during the pivoting movement between the use position and the non-use position. The braking device is arranged in an interior space of the sealing element that is sealed against environmental influences by the sealing element.

The sealing element is connected to the coupling arm bearing element in a rotationally fixed manner with respect to the pivot axis, for example, while it is mounted pivotably about the pivot axis with respect to the pivot bearing section. However, it is also possible for the sealing element to be connected to the holder in a rotationally fixed manner with respect to the pivot axis and for it to be rotatable about the pivot axis with respect to the coupling arm bearing element.

The sealing element is preferably designed in the manner of a tube or a cuff. The sealing element preferably extends around the pivot axis.

The sealing member preferably has a peripheral wall that extends around the pivot axis.

The peripheral wall advantageously extends between sealing portions that are longitudinally spaced with respect to the pivot axis. Advantageously, one sealing section rests in the sealing seat on the holder and the other sealing section in the sealing seat on the coupling arm bearing element.

The interior space sealed off by the sealing element is advantageously delimited by a peripheral wall extending around the pivot axis and by the sealing sections which are spaced apart in relation to the pivot axis.

The sealing sections are preferably ring-shaped.

A sealing section of the sealing element preferably has a sealing contour for form-fitting engagement with a counter-sealing contour of the holder or the coupling arm bearing element, or is designed as a sealing contour. The sealing contour can be designed, for example, as a sealing projection or engagement section which forms a counter-sealing contour, in particular an annular ge, seal seat engages on the holder or coupling arm bearing element. Alternatively, a sealing projection can be provided on the holder or coupling arm bearing element as a counter-sealing contour, which projection engages in an in particular ring-shaped seal receptacle, ie a sealing contour, of the sealing section of the sealing element. A sealing projection of the sealing element preferably protrudes radially inwards or radially outwards with respect to the pivot axis into a sealing receptacle on the holder or coupling arm bearing element. A sealing projection on the holder or coupling arm bearing element preferably protrudes radially inwards or radially outwards with respect to the pivot axis into a sealing receptacle on the sealing element.

A sealing section can additionally and/or alternatively also have a form-fitting contour or be designed as a form-fitting contour which is held in a form-fitting manner on the holder or coupling arm bearing element. The form-fitting hold can, for example, form an anti-twist safeguard for the sealing element on the holder or coupling arm bearing element with respect to the pivot axis. A form-fitting hold of the sealing element on the holder or coupling arm bearing element can also provide that a sealing projection and a sealing receptacle, one component of which is arranged on the sealing element and the other component on the holder or coupling arm bearing element, engage in one another in a form-fitting manner, but can be rotated relative to one another about the pivot axis.

Furthermore, it is advantageous if a sealing section is held in a materially bonded manner and/or by gluing on the holder or coupling arm bearing element.

It is also possible for a sealing section to be held in a press fit on the holder or coupling arm bearing element.

It is advantageously provided that the sealing element is held and/or clamped by means of a retaining ring with a component of the holder or coupling arm bearing element in a press fit. The retaining ring is, for example, radially on the outside arranged the sealing element and clamps the sealing element with the holder or the clutch arm bearing element.

The brake contour can be arranged at any point on the sealing element or in relation to the sealing element.

A preferred exemplary embodiment provides that the brake contour or the brake body is arranged on the or a sealing element for sealing the trailer hitch. On the one hand, the sealing element thus fulfills the function of sealing the trailer hitch, for example sealing the pivot bearing, and on the other hand it provides one of the components of the brake body or brake contour.

For example, a section on which the braking contour is arranged is a wall of the sealing element. In particular, this section or a wall of the sealing element on which the braking contour is arranged is an end wall which extends around the pivot axis, in particular in the form of a ring. The end wall preferably extends transversely, in particular approximately at right angles transversely, to the pivot axis.

The braking contour is advantageously provided by the material of the sealing element, in particular by an elastic material of the sealing element. The material of the sealing element is preferably rubber, elastic plastic or the like. Thus, the material of the sealing element can develop a correspondingly high frictional force in interaction with the brake body.

The braking contour is preferably in one piece with the sealing element. However, it is also possible for the brake contour to consist of a body or material attached to the sealing element.

The brake body is advantageously non-elastic and/or made of metal. It is possible for the brake body to be made of a material that has higher friction than metal, for example plastic. It is also possible that the Brake body is provided with a friction coating. The coating can, for example, develop higher friction on the brake contour and thus a better braking effect.

It is advantageous if the braking contour is arranged on a wall section of the sealing element which can be compressed and/or deformed by the braking body and/or deformed into a displacement cavity facing away from the braking body. The displacement cavity can be provided, for example, on the coupling arm bearing element or on the holder. However, it can also be formed, for example, by the surroundings of the trailer hitch, into which the wall section can deform.

It is advantageous if the sealing element is tightly held on the holder and on the coupling arm bearing element during the pivoting movement between the non-use position and the use position, in which the brake body slides along the sealing contour. Thus, for example, an interior space of the sealing element, in which bearing surfaces of the pivot bearing are located, for example, is always sealed, even when the brake body slides along the brake contour.

It should be mentioned in the following embodiments that it is not important that the brake contour and the brake body brake with different braking forces. It does not have to be the case that the braking contour and the braking body exert at least two different braking forces on the coupling arm bearing element during the pivoting movement between the position of use and the position of non-use. Rather, the braking force can also be a constant or essentially the same braking force. It can be the case, but does not have to be the case, for the brake body or the brake contour to be arranged directly on the sealing element. They can also be provided elsewhere or on another component. In themselves, the following embodiments represent independent inventions. However, these inventions can also easily be implemented in combination with one of the aforementioned features and embodiments. In the case of the trailer hitch, it is advantageously provided that the brake contour and/or the brake body, preferably both, is or are arranged in an interior space of the trailer hitch that is sealed off by the or a sealing element. This embodiment represents an independent invention in connection with the preamble features of claim 1. Due to the brake components arranged in the sealed interior, namely brake contour and brake body, moisture or similar other environmental influences, for example, cannot or only insignificantly influence the braking effect.

An advantageous embodiment of the invention or an invention that is independent per se in connection with the preamble of claim 1 provides that the brake contour is arranged between sealing sections with which the sealing element or a sealing element for sealing the trailer hitch is tight, in particular permanently tight and/or also during kinematic loads or actuations of the coupling arm with respect to the holder, bears against the holder and close to the coupling arm bearing element. This sealing is given in particular during the entire pivoting movement between the position of use and the position of non-use. The sealing sections remain in a sealing seat on the clutch arm bearing element and on the holder even during the braking action of the braking device.

In any case, a section of the sealing element on which the brake contour is arranged is pressure-loaded or force-loaded when the brake body acts. The measures explained below provide a remedy, in particular when the section of the sealing element that has the brake contour is a wall or end wall. It is again advantageous if the braking contour and the braking body exert at least two different braking forces on the coupling arm bearing element during the pivoting movement between the position of use and the position of non-use. In the following embodiments, which can represent an independent invention per se, it is also possible that the braking contour and the braking body have essentially the same braking force during the pivoting movement between the Exercise position of use and the non-use position on the coupling arm bearing element.

An advantageous embodiment of the invention or an intrinsically independent invention in connection with the preamble of claim 1 provides that sealing sections of the sealing element, between which the brake contour is located, are clamped and/or cohesively and/or by means of an adhesive bond on at least one component are held by the coupling arm bearing element or holder and/or are positively engaged with at least one component of the coupling arm bearing element or holder and/or are sealed by means of interlocking sealing contours on the sealing element and the holder and/or the sealing element and the coupling arm bearing element. Of course, one measure can be provided for one sealing section and the other measure for the other sealing section, i. H. For example, one sealing section is firmly connected to a component of the coupling arm bearing element or holder by means of a press fit, while the other sealing section is in positive engagement and/or by means of a sealing contour in engagement with the other component of the coupling arm bearing element or holder. A sealing section of the sealing element can, for example, be fixed in a pivot-proof manner on one component of the coupling arm bearing element or holder with respect to the pivot axis and can be positively engaged with the other component of the coupling arm bearing element and holder or by means of a sealing contour and can also be pivoted or rotated relative to this other component about the pivot axis be. As mentioned, in this and the following embodiments, it is not necessarily important that the braking contour and the braking body generate different braking forces during the pivoting movement, but that it is possible for the braking force to be constant or constant during the movement between the non-use position and the use position is essentially constant.

An advantageous embodiment of the invention or an intrinsically independent invention in connection with the preamble of claim 1 provides that the brake contour is arranged on a section of the sealing element by a support contour of the holder or the coupling arm is supported bearing element. The support contour is preferably opposite the brake body when the brake contour is acted upon. So when the brake body acts on the brake contour, the supporting contour is opposite to it. For example, the brake contour is arranged between the brake body and the support body when the brake body acts on the brake contour. The support contour advantageously supports the sealing element in a direction of force parallel to the pivot axis or with a directional component parallel to the pivot axis.

An advantageous embodiment of the invention or an invention which is independent per se in connection with the preamble of claim 1 provides that the brake contour is arranged on a section of the sealing element which, in relation to a direction of force in which the brake body acts on the brake contour, is based on a positive connection between the sealing element and the holder or the coupling arm bearing element is supported. For example, an edge area of the section of the sealing element is accommodated in a form-fit receptacle provided on the holder or the coupling arm bearing element. However, a form-fitting projection can also be provided, which engages in a form-fitting manner in a form-fitting receptacle of the section of the sealing element. The two positive-locking receptacles are preferably a groove, in particular an annular groove. The positive-locking receptacle is preferably a seal receptacle on the holder or coupling arm bearing element, into which the sealing element engages, or a seal receptacle of the sealing element, into which a sealing projection of the holder or the coupling arm bearing element engages.

It is advantageously provided that the brake contour or a braking surface of the brake contour extends transversely, for example at right angles transversely or at an angle of approximately 80-90°, to the pivot axis around the pivot axis, so that the brake body has a force direction or force component parallel to the pivot axis the braking contour or the braking surface of the braking contour acts on the braking contour during its braking intervention. However, it is also possible for the brake contour to have a braking surface on which the brake body acts on the brake contour with a force component running radially to the pivot axis during its braking intervention. The brake contour thus protrudes, for example, radially inwards or radially outwards with respect to the pivot axis in the direction of the brake body, so that the latter acts on the brake contour with a radial direction of force with respect to the pivot axis during its braking intervention.

The trailer hitch advantageously has a fixing device for fixing the coupling arm at least in the position of use, the fixing device having a fixing element which, by means of a guide with respect to the coupling arm bearing element and the holder, between a fixing position in which the fixing element fixes the coupling arm bearing element in a rotationally fixed manner with respect to the pivot axis, and a release position is movably mounted in which the Kupplungarmlagerelement is rotatable with respect to the pivot axis.

The fixing element engages, for example, in a form-fit receptacle on the coupling arm bearing element or on the holder or both. The fixing element is mounted, for example, on the holder between the fixing position and the release position, in particular mounted in a displaceable manner. However, the fixing element can also easily be mounted on the coupling arm bearing element between the fixing position and the release position and, for example, engage in a form-fitting receptacle on the holder in the fixing position and be disengaged from the form-fitting receptacle in the release position.

It is advantageously provided that the fixing element in the fixing position engages in a positive-locking receptacle arranged next to the guide and separate from the guide, which has a holder-receiving section arranged on the holder and a bearing element-receiving section arranged on the coupling arm bearing element.

The basic idea here is that the fixing element is supported or can be supported in a form-fitting manner on the holder by means of the holder receiving section. When So when driving loads act on the trailer hitch, these can be absorbed via the holder-receiving section away from the guide for the fixing element. The at least one positive-locking receptacle is thus formed in a complementary manner by the holder receiving section and the bearing element receiving section.

The fixing element is preferably a bolt or bolt body. Alternatively, the fixing element can also be a rolling body, a ball or the like. There can be several fixing elements and several associated positive-locking recordings.

Furthermore, it is possible that form-fitting recordings are also present, which are present entirely on the coupling arm bearing element or on the holder bearing element, d. H. are not formed complementarily by holder-receiving section and bearing element-receiving section.

It is easily possible for a plurality of holder receiving sections to be present on the holder and/or for a plurality of bearing element receiving sections to be present on the coupling arm.

In order to form two positive-locking receptacles, however, it is not necessary for two holder-receiving sections and two bearing element-receiving sections to be present, even if this can be provided by an embodiment of the invention. For example, the following configuration is possible:

A preferred concept provides that the trailer hitch has at least two positive-locking receptacles, which are formed by providing a holder-receiving section and two bearing element-receiving sections, one of which is in two different pivot positions of the coupling arm bearing element with respect to the holder bearing element to form a positive-locking receptacle opposite the holder-receiving section, or that a bearing element-receiving section and two holder-receiving sections are present, one of which is in two different pivot positions of the coupling arm bearing element with respect to the Holder bearing element to form a form-fit recording opposite the bearing element-receiving section. For example, a holder receiving section can be assigned to the non-use position and the use position. Furthermore, the two bearing element receiving sections can be assigned to the position of non-use and the position of use.

Provision is preferably made for the bearing element receiving section and/or the holder receiving section to have an abutment surface for supporting a support surface of the fixing element. The abutment surface or the abutment surfaces and/or the support surface are preferably cylindrical surfaces or cylinder jacket surfaces. However, if the fixing element is a sphere, for example, the support surface can also have a spherical or crowned shape.

It is advantageously provided that the abutment surface and the support surface have a directional component that runs parallel to the pivot axis of the pivot bearing and/or parallel to the or a guide track or guide axis along which the fixing element on the guide is guided between the release position and the fixing position. For example, this is achieved in that the abutment surface or support surface is a cylindrical surface.

It is particularly preferred if the abutment surface and/or the support surface run parallel to the pivot axis. However, it is also possible for the abutment surface and the support surface in the fixing position, in which the fixing element engages in the positive-locking receptacle, to have a relative angle to one another which represents a self-locking action which counteracts a release movement in the direction of the release position and/or which is a maximum of 5°, in particular at most 4°, preferably at most 3°, preferably at most 2°. It is therefore possible or conceivable that, for example, the at least one abutment surface of the bearing element receiving section or the holder receiving section runs parallel to the guide axis or the pivot axis, while the support surface has an inclination of, for example, 2-5° with respect to the guide axis or pivot axis. It is also advantageous if the abutment surface has an abutment surface section on the bearing element receiving section and an abutment surface section on the holder receiving section, which are aligned with one another when the pivot bearing has a pivot position associated with the use position or the non-use position.

Furthermore, the abutment surface of the holder-receiving section preferably aligns with a guide surface of the guide for the fixing element.

It is preferred if the guide is arranged in a stationary manner on the holder or in a stationary manner on the coupling arm bearing element. Consequently, it is therefore a preferred embodiment that the fixing element or at least one fixing element is movably mounted on the holder and is only in engagement with the holder or the guide on the holder even in the release position. However, there is also an alternative embodiment in which the guide for the fixing element is arranged on the coupling arm bearing element and the fixing element is completely received and arranged in the coupling arm bearing element in the release position.

The positive-locking receptacle advantageously has an insertion opening for the fixing element, through which the fixing element penetrates into the positive-locking receptacle during the movement from the release position into the fixing position. The insertion opening is, for example, opposite an exit of the guide for the fixing element.

A further variant of the invention provides that only the bearing element receiving section or only the holder receiving section has or forms an end stop or a clamping bevel for the fixing element, against which the fixing element strikes when it moves into the form-fitting receptacle. For example, a stop wall or clamping bevel opposite the insertion opening with respect to the movement of the fixing element into the positive-locking receptacle is present in one receiving section and not in the other, e.g. only in the holder receiving section or only in the bearing element receiving section. For example, the Hal- ter-receiving section parallel to the guide axis for the fixing element and / or parallel to the pivot axis have no end stop and no clamping bevel. It is particularly advantageous that the bearing element receiving section has a clamping bevel or an end stop for the fixing element.

It is advantageously provided that in the release position the fixing element is disengaged from the bearing element receiving section and the holder receiving section of the form-fitting receptacle and/or is only engaged with the guide. Although the fixing element then remains guided by the guide, it does not engage in the positive-locking receptacle, so that the coupling arm can be pivoted between the position of use and the position of non-use.

It is in principle possible for the bearing element receiving section to be arranged at any point on the holder. However, the bearing element receiving section is preferably arranged on the pivot bearing section for the pivotable mounting of the coupling arm bearing element. For example, the bearing element receiving section is arranged on a bearing seat in which the coupling arm bearing element, in particular a bearing section of the coupling arm bearing element, is pivotably accommodated.

However, the following measure is advantageous for the guide for the fixing element, in which it is provided that the guide for the fixing element is arranged or runs in particular completely outside of the pivot bearing section or next to the pivot bearing section. For example, the guide is arranged outside of the aforesaid bearing seat of the holder or holder bearing element.

It is also advantageous if the guide has a guide channel, in particular for the fixing element or an actuating body that actuates the fixing element, which opens into the holder-receiving section of the positive-locking receptacle and/or lies opposite it. A simple and inexpensive design of the trailer hitch provides that the fixing device has only a single fixing element. In the use position and the non-use position, this fixing element can engage in one and the same positive-locking receptacle. However, it is also possible for it to engage in different positive-locking receptacles in the use position and in the non-use position, but these are formed by pivoting the coupling arm bearing element about the pivot axis to form two bearing elements that are different from one another, for example spaced apart by an angle of rotation with respect to the pivot axis -Receiving sections are opposite a single holder-receiving section that is stationary with respect to the pivot axis.

It is advantageous if the fixing element of the fixing device is spring-loaded in the direction of the fixing position by a spring arrangement.

An advantageous concept provides that the holder receiving section is open radially inwards with respect to the pivot axis and the bearing element receiving section is open radially outwards with respect to the pivot axis and in a predetermined pivoting position of the coupling arm bearing element with respect to the pivot axis to form the positive-locking receptacle. For example, the receiving sections are configured as complementary cylinder surfaces and/or cylinder surfaces that lie opposite one another in the predetermined pivoting position.

For example, the bearing element receiving portion is arranged radially outwardly on a bearing portion of the coupling arm bearing element, while the holder receiving portion is arranged radially inwardly open on an inner circumference of a bearing receptacle for the bearing portion of the coupling arm bearing element. Thus, the form-fitting receptacle formed by the two receiving sections has a maximum radial distance with respect to the pivot axis, which enables optimal torque support. Storage is preferably provided in such a way that the coupling arm bearing element is mounted on the holder so that it can only rotate about the pivot axis and/or is held on the holder so that it cannot be displaced axially with respect to the pivot axis.

The following measure represents an independent invention, but preferably an embodiment of the above invention, in which it is provided that the fixing element is slidably mounted on the guide parallel to the pivot axis between the fixing position and the release position, with the fixing element in the Fixing engages in a form-fit recording. The fixing element is, for example, displaceably mounted on the guide along a guide axis parallel to the pivot axis. The guide axis and the pivot axis are advantageously at a distance from one another. The guide axis is preferably eccentric with respect to the pivot axis. The guide axis and the pivot axis are preferably non-coaxial. In particular, the fixing element has at least one support surface running parallel to the pivot axis, which is supported or can be supported on an abutment surface running parallel to the pivot axis on the positive-locking receptacle. The positive-locking receptacle can be arranged entirely on the holder or entirely on the coupling arm bearing element. However, the above measure is also possible, in which the form-fitting receptacle is formed in a complementary manner, so to speak, by the bearing element receiving section and the holder receiving section.

Another invention that is independent per se, but preferably an embodiment of the above invention, is represented by the following measure, in which it is provided that the trailer coupling has a lubricating device with a lubricant channel running in a component of the holder or coupling arm bearing element, which has a feed opening with a check valve , in particular a grease nipple, for feeding in lubricant, the lubricant channel opening out at the pivot bearing section. For example, the feed opening is present on the holder. However, the feed opening can also be provided on the coupling arm bearing element or at another location. A preferred embodiment provides that the feed opening is arranged on a front side, in particular on a front side of a bearing shaft of the trailer hitch, which supports the coupling arm bearing element pivotably about the pivot axis and from which the coupling arm protrudes transversely. Thus, the feed opening is easily accessible. It is particularly advantageous if the feed opening is aligned with the pivot axis.

In the fixing position, the fixing element is preferably accommodated at least in sections in the guide and protrudes in front of the guide in the direction of the positive-locking receptacle.

Exemplary embodiments of the invention are explained below with reference to the drawing. Show it:

Figure 1 is a perspective oblique view of a trailer hitch in the position of use,

Figure 2 shows the trailer hitch according to Figure 1, but in the non-use position,

FIG. 3 shows a perspective exploded view of the trailer hitch according to the preceding figures

Figure 4 is a side view of the trailer coupling according to the previous figures, but without the coupling arm,

FIG. 5 shows a cross section through the trailer hitch according to FIG. 4, approximately along section line A-A in FIG. 4,s

FIG. 6 shows a sectional view through the trailer hitch according to the above figures in the position of use, with a fixing device assuming its fixing position, FIG. 7 shows a further sectional view through the trailer hitch according to the preceding figures, with the fixing device assuming its release position,

FIG. 8 shows a perspective oblique view of the trailer hitch according to the above figures obliquely from below in an intermediate position between the position of use and the position of non-use,

FIG. 9 shows a sealing element of the trailer hitch according to the above figures in a perspective oblique view with a brake contour and a brake body that can be moved along the brake contour in a first relative position to one another,

FIG. 10 shows the sealing element according to FIG. 9, the brake body having a different position relative to the brake contour, and

FIG. 11 shows the arrangement from FIGS. 9 and 10, the brake body having a further position relative to the brake contour.

A trailer hitch 10 is provided for attachment to a motor vehicle 90 or is attached to the motor vehicle 90 . The trailer hitch 10 includes a holder 11 which is attached to a support 91, in particular a cross member.

The support 91 is connected to a body 93 of the motor vehicle 90, for example by means of side supports 92, which are shown schematically. In installation position, i. H. when the bracket 91 is fixed to the motor vehicle 90, the bracket 91 is hidden under a bumper 94 of the motor vehicle 90, for example. The bumper 94, the body 93 and the side members 92 are indicated schematically.

In principle, the carrier 91 and preferably the side carriers 92 can form components of the trailer hitch 10 and/or a carrier arrangement of the trailer hitch 10 . The holder 11 has a carrier body 12, for example a holder plate or the like, which is connected to the carrier 91, for example screwed and/or welded. The carrier body 12 has a recess 13 in which the carrier 91 is accommodated.

The trailer coupling 10 comprises a coupling arm 20, at one end or free end of which a coupling element 27, for example a ball 27A, is arranged for attaching a trailer AK or coupling a load carrier LT. The coupling arm 20 is pivotably mounted about a pivot axis D with respect to the holder 11 by means of a pivot bearing 30, namely between a use position G, in which the coupling arm 20 and in particular the coupling element 27 protrude backwards in front of the bumper 94, so that a trailer or load carrier can be coupled , and a non-use position N of the coupling arm 20 that is adjusted closer to the body 93 or to a rear end 95 of the motor vehicle 90 and/or below the bumper 94 when the trailer hitch 10 is not used.

The coupling arm 20 comprises an end region 21 which is connected to the pivot bearing 30 or with which the coupling arm 20 is attached to the pivot bearing 30 . The coupling arm 20 has a curved or arcuate or U-shaped configuration, for example. For example, a section 22, on which the end area 21 is provided, and a neck section 26, at the free end area of which the coupling element 27 is arranged, form side limbs, while a section 24 arranged between sections 22 and 26 represents a base limb, which has curved sections 23 and 25 is connected to sections 22 and 26.

An eyelet 28 for a breakaway cable and a holder 29 for a trailer socket 29A are also arranged on the coupling arm 20 . The trailer socket 29A is arranged on an inner periphery of the bending portion 25, for example. The eyelet 28 is preferably arranged on a region of the coupling arm 20 which faces away from the motor vehicle 90, for example on Neck section 26, at section 24 or at the outer circumference of the curvature section 25.

The pivot bearing 30 comprises a holder bearing element 31 which is stationary with respect to the holder 11 . The holder bearing element 31 comprises a pivot bearing seat 32 on which a coupling arm bearing element 50 is pivotably mounted about the pivot axis D. The coupling arm 20 is arranged stationarily on the coupling arm bearing element 50 so that the coupling arm 20 can pivot or rotate about the pivot axis D with respect to the holder 11 by means of the coupling arm bearing element 50 .

The holder bearing element 31 is accommodated in a receptacle 14 of the holder 11 . The receptacle 14 is designed, for example, as a passage opening in which a fastening section 38B is accommodated. The fastening section 38B protrudes, for example, through the passage opening or receptacle 14 in front of the carrier body 12

A flange 34 protrudes radially outward in front of the fastening section 38B and serves to support it on the carrier body 12 of the holder 11 on which the receptacle 14 is arranged.

One possibility for fastening the holder bearing element 31 consists, for example, in screws being screwed into the carrier body 12 through an end face 36 of the flange which faces away from the fastening section 38B.

In the present case, however, a different fastening method has been selected, in that the carrier body 12 is held or clamped in a sandwich-like manner, so to speak, between the flange 34 on the one hand and an abutment body or tensioning body 97 on the other.

The clamping body 97 forms part of fastening means 96 for fastening the holder bearing element 31 to the holder 11. The clamping body 97 has an annular or partially annular shape so that it can surround the fastening section 38B in a ring-shaped manner and/or the fastening section 38B can engage in an interior space of the clamping body 97 . An annular shape or a course of the clamping body 97 corresponds approximately to the annular shape of the flange 34.

The clamping body 97 is fastened to a rear face 36A of the flange 34 facing away from the end face 36, namely by means of screws 99 which penetrate through openings or openings 98 of the clamping body 97 and are screwed into screw receptacles 38A on the flange 34. The carrier body 12 is accommodated and preferably clamped in an intermediate space 34A between the flange 34 and the clamping body 97 .

The clamp body 97 is fixed to one of a rear side of the holder support member 31 by screws 99 penetrating through holes 98 or the clamp body 97 and screwed into screw socket 38A on the rear side 38 of the holder support member 31 .

The holder bearing member 31 has a cylindrical stepped shape. The end face 36 of the flange 34 forms, so to speak, the front side from which the coupling arm bearing element 50 engages in the pivot bearing receptacle 32 and is rotatably accommodated there.

In principle, the bearing shaft 40 could be rotatably mounted on the holder bearing element 31 so that the coupling arm bearing element 50 is rotatably mounted on the holder bearing element 31 by means of the bearing shaft 40 . In the present case, however, the bearing shaft 40 is fixed in a stationary manner with respect to the holder bearing element 31, namely screwed, for example. However, it should also be mentioned that the bearing shaft 40 can be in one piece with the holder bearing element 31 or can also be connected to it with a material fit, for example glued or welded. Furthermore, it is possible that the bearing shaft 40 is pressed with the holder bearing element 31, connected by compression or the like. This also applies not only for the specific embodiment, but also for any other trailer hitch according to the invention.

The bearing shaft 40 has a bearing section 41 on which the coupling arm bearing element 50 is pivotably mounted about the pivot axis D. On opposite longitudinal end regions, the bearing shaft 40 has a flange 42 for support on the holder bearing element 31 and a fastening section 48 with a threaded section 43 for screwing on a nut 44, with the holder bearing element 31 and the coupling arm bearing element 50 in a space between the flange 42 and nut 44 are engaged and sandwiched. However, the coupling arm bearing element 50 is still rotatably mounted on the bearing shaft 40, i.e. it has rotational play with respect to the bearing disc 45.

The bearing shaft 40 is accommodated in a bearing shaft receptacle 33 of the holder bearing element 31 and is supported on one longitudinal end area of the bearing shaft receptacle 33 with the flange 42 and protrudes into the pivot bearing receptacle 32 in which it rotatably supports the coupling arm bearing element 50 .

The coupling arm bearing element 50 has a bearing section 51, which engages in the pivot bearing mount 32, and a holding section 52, which is used to hold and/or fasten the coupling arm 20 or is firmly connected to it.

A shaft receptacle 53 for the bearing shaft 40 is provided on the bearing section 51 . The bearing shaft 40 penetrates the shaft receptacle 53 and is with its attachment portion 48 on which the threaded portion 43 is provided, in front of a support surface 54 of the coupling arm bearing element 50 before.

Furthermore, the bearing shaft 40 has a support surface 49 which is flush or approximately flush with the support surface 54 .

A bearing body or a bearing disk 45 is supported and/or rotatably mounted on the support surfaces 49, 54, which in this respect also represent bearing surfaces which the threaded portion 43 protrudes. The nut 44 is screwed onto the threaded section 43 so that it fixes the clutch arm bearing element 50 to the bearing shaft 40 and to the holder bearing element 31 axially with respect to the pivot axis D via the bearing washer 45 .

It is advantageous if a securing element 46 , for example a securing washer, is arranged between the bearing washer 45 and the nut 44 . The securing element 46 counteracts a loosening of the nut 44 from the threaded section 43 .

The bearing section 51 of the clutch arm bearing element 50 is pivoted on the bearing shaft 40 .

An additional and/or alternative mounting is possible, for example, in that an outer circumference 55 of the bearing section 51 is pivotably mounted on the inner circumference or on the inner wall of the pivot bearing mount 32 . In any case, the coupling arm bearing element 50 can be supported on the pivot bearing seat 32, for example in the case of particularly heavy loads on the coupling arm 20, load surges or the like.

It is possible for the principle of optimized lubrication explained below to be implemented using a lubricating device 100 also in relation to the pivot bearing mount 32 and the outer circumference 55 of the bearing section 51 .

The lubricating device 100 comprises a lubricant channel 101, which passes through the bearing shaft 40 and has a feed section 102, at the entrance of which there is a receptacle 104, for example a screw receptacle, for a grease nipple 105, through which lubricant 112, for example grease, oil or the like, is fed in the lubricant channel 101 can be fed or stored.

For this purpose, for example, a lubricant reservoir 110 or a feeding device with a lubricant reservoir 110 is to be connected to the lubricating nipple 105 by means of a connecting element 111 (indicated schematically in FIG. 5). The lubricating nipple 105 has a ball or another similar check valve in a manner known per se, so that lubricant 112 fed into the lubricant channel 101 can be kept under pressure in the lubricant channel 101 . The lubricating nipple 105 is preferably covered or can be covered by a cover 106, for example a cap.

In the form of the grease nipple 105, a check valve 113 is thus arranged on the receptacle 104, which forms a feed opening 114 for the lubricant 112.

The supply section 102 of the lubricant channel 101 is flow-connected to one or more distribution sections 103 through which lubricant 112 can reach a gap or bearing area between the bearing shaft 40 and the clutch arm bearing element 50 . The at least one distribution section 103 opens out on the outer circumference of the bearing shaft 40, namely on the bearing section 41 or its outer circumference, so that lubricant 112 can get into the space between the bearing section 41 on the one hand and the shaft receptacle 53 of the coupling arm bearing element 50 on the other.

At least one cavity for the lubricant 112, for example a lubricant recess 47, in particular an annular cavity or lubricant recess, is preferably provided on the bearing section 41, so that a supply of the lubricant 112 for lubricating the pivot bearing of the coupling arm bearing element is available in a region of the bearing surfaces that are supported on one another and are to be lubricated 50 on the bearing shaft 40 is ready.

The distribution sections 103 run, for example, radially with respect to the bearing shaft 40 , while the feed section 102 runs axially with respect to the pivot axis D or longitudinal extension of the bearing shaft 40 . The receptacle 104 and the lubricating nipple 105 are arranged on an end face of the fastening section of the bearing shaft 40 which faces away from the bearing section 41 and has the threaded section 43 . A flange 56 is provided on the holding section 52 of the coupling arm bearing element 50 , which is opposite the flange 34 of the holder bearing element 31 , preferably provided and/or designed for support on the flange 34 of the holder bearing element 31 .

The coupling arm 20 is arranged and held on an end face 56A of the flange 56 facing away from the bearing section 51 . For example, screw receptacles 58 for screwing in screws 58A are provided on the end face 56A.

On the holding portion 52 of the clutch arm bearing member 50, a holding member 15 of the clutch arm 20 or for holding the clutch arm 20 is arranged.

The holding element 15 could, for example, be in one piece with the section 22 or end area 21 of the coupling arm 20 . Such a design is indicated in FIG.

The holding element 15 has a fastening section 16, for example a plate-like fastening section, which has a support surface 16A with which the holding element 15 is supported on the flange 56 or the end face 56A. The support surface 16A may be provided at the bottom at a seat or indentation for the flange 56 and/or be a flat surface.

Passage openings 17 for the screws 58A are provided on the fastening section 16 . The screws 58A are arranged in a ring around the pivot axis D, so that the holding element 15 is fixedly connected to the coupling arm bearing element 50 at several points around the pivot axis D. For example, an end face of the fastening section 16 rests on the end face 56A of the flange 56 .

A retaining projection 18 protrudes from the fastening section 16 and can, for example, be provided instead of the section 22 of the coupling arm 20 or can hold it. Retaining arms 19 protrude from the retaining projection 18 from, for example, at an angle, between which the section 24 of the coupling arm 20 is added. The holding arms 19 form, for example, a receiving fork or are arranged in the form of a fork. The holding arms 19 can hold the section 24 of the coupling arm 20 like a fork or like a rod.

Provision is preferably made for the coupling arm 20 or its section 24 to be welded and/or screwed to the holding arms 19 and/or to be connected in some other material-to-material manner.

Fixed pivot stops 37G and 37N are assigned to the pivot end positions or rotary end positions of the coupling arm 20 with respect to the holder 11. For example, the swing stoppers 37G and 37N are arranged on the holder 11 or on the holder supporting member 31. FIG. In the present case, the swivel stops 37G and 37N are designed as projections which protrude in front of the flange 34, in particular its end face 36. The stop body 57 is designed as a projection which protrudes radially outwards in front of the coupling arm bearing element 50, namely in the area of the flange 56.

A sealing element 60 is provided for sealing the pivot bearing 30 . The swivel stops 37N, 37G and the stop body 57 are also located in an interior space 60A sealed by the sealing element 60.

The sealing element 60 has a peripheral wall 61 which is intended to rest against the flange 34 . Abutment ribs are preferably provided on an inner circumference of the peripheral wall 61 , in particular groups of a plurality of abutment ribs, which serve to bear against the outer circumference 35 of the flange 34 .

The peripheral wall 61 and thus the sealing element 60 are connected to the flange 34 and thus to the holder bearing element 31 by means of a retaining ring 65 . The retaining ring 65 braces and/or clamps the peripheral wall 61 , in particular a sealing section 61 D of the peripheral wall 61 the flange 34. Thus, the sealing element 60 is held with the flange 94 in an interference fit.

Furthermore, the sealing section 61 D can be glued to the flange 34 using adhesive, for example, and/or welded to the flange 34, for example by heating the sealing element 60 in the area of the flange 34.

In addition, a positive hold and/or non-rotatable hold of the sealing section 61 D on the flange 34 is advantageous:

For this non-rotatable connection, it is advantageous if, as in the exemplary embodiment, the outer circumference 35 of the flange 34 and the inner circumference 61A of the circumferential wall 61 have anti-rotation contours, which in the exemplary embodiment are realized in that the outer circumference 35 and the inner circumference 61A have a polygonal shape. Consequently, the peripheral wall 61 fits positively and non-rotatably onto the flange 34 and thus onto the holder bearing element 31 . The peripheral wall 61 has a polygonal inner peripheral contour at least on the sealing section 61D, which corresponds to the polygonal outer peripheral contour of the flange 34, so that the sealing section 61D bears against the flange 34 in a form-fitting manner.

An end wall 63 protrudes from the peripheral wall 61 into an interior space of the sealing element 60 or radially inwards and is in sealing engagement or sealing contact with the clutch arm bearing element 50 .

On its radially inner, free end area or on its radially inner end face, the end wall 63 has, for example, an engagement section 64 which engages in a seal receptacle 59 of the coupling arm bearing element 50 . The engagement section 64 and the seal receptacle 59 form sealing contours 64K, 59K which engage in one another in a form-fitting manner. The engaging portion 64 forms a sealing portion 64D. The seal receptacle 59 is designed, for example, as an annular groove on the flange 56 . A design reversal is easily possible, for example on the end face or narrow side of the end wall 63 a Recording, in particular an annular groove, is provided for receiving a radially outwardly with respect to the pivot axis D in front of the flange 56 protruding, in particular annular or flange-like sealing projection. Furthermore, the radially inner end face of the end wall 63 could also rest directly with its flat side on a cylindrical outer circumference of the coupling arm bearing element 50 or a sealing lip could be provided for sealing contact.

The holding element 15 also contributes to an optimal hold of the sealing element 60 on the coupling arm bearing element 50 . For example, a portion 16B of the attachment portion 16 protrudes toward the sealing member 60 and supports it against removal in the direction of the pivot axis D away from the clutch arm bearing member 50 . The portion 16B is annular, for example. The section 16B forms, for example, an outer peripheral area of the fastening section 16 and extends around the passage openings 17 for the screws 58A. Section 16B forms a type of retaining flange, for example.

The sealing element 60 forms part of a braking device 70 which serves to brake a rotary movement or pivoting movement of the coupling arm 20 with respect to the holder 11 during the adjustment between the use position G and the non-use position N.

The braking device 70 includes a braking contour 71 which is provided by the sealing element 60 in the present case. The braking contour 71 is arranged in the inner space 60A of the sealing element 60 . The stop body 57 of the coupling arm bearing element 50 forms a braking body 72 which, in braking engagement, slides along the braking contour 71 when the coupling arm 20 is adjusted between the position of non-use N and the position of use G, as a result of which the pivoting movement of the coupling arm 20 in the region of the braking contour 71 is braked.

The braking contour 71 extends to the front of the pivot stops 37N, 37G, with spacing or clearance sections 73N in front of the pivot stops 37N, 37G and 73G between the brake contour 71 and the pivot stops 37N, 37G. Between the clearance sections 73N and 73G, the braking contour 71 forms a contact track 71K or has a contact track 71K which is designed and provided for braking contact with the brake body 72 and is shorter than a movement track BB between the pivot stops 37N, 37G.

Consequently, the brake body 72 or stop body 57 is released from the brake contour 71 in the areas in front of the pivot stops 37N, 37G. Between the clearance sections 73N and 73G and the brake contour 71 there are engagement sections 74N and 74G, for example ramps, along which the brake body 72 runs during its movement between the brake contour 71 and the clearance sections 73N and 73G. The brake body 72 thus runs, for example, from the clearance section 73N along a ramp or an inclined contour, namely the slide-on section 74N, onto the brake contour 71.

The clearance portion 73G upstream of the pivot stop 37G is preferably longer than the clearance portion 73N upstream of the pivot stop 37N. Thus, starting from the non-use position N, the brake body 72 comes almost immediately into engagement with the braking contour 71, e.g. For example, in the non-use position N, the coupling arm 20 has an upper position that is displaced away from a road surface, so that the coupling arm 20 would experience high acceleration from the non-use position N due to its weight. Starting from the non-use position N, the braking device 70 is used with a high braking force in the sense of braking the coupling arm 20 .

On the other hand, clearance section 73G is longer than clearance section 73N.

Thus, when the clutch arm 20 is displaced toward the use position G, it comes before it hits the pivot stop 37G on the Clearance section 73G free of the braking device 70, so to speak, so that the coupling arm 20 can pivot without the braking effect of the braking device 70 or with at least a lower braking effect of the braking device 70 on its last path section up to the position of use G.

On the other hand, when the coupling arm 20 is adjusted from the non-use position N, the braking effect of the braking device 70 begins after the relatively short clearance section 73N has passed through, so that the coupling arm 20 is braked in an intermediate position Z between the non-use position N and the use position G, generally a lower intermediate position. at which the clutch arm 20 projects down in front of the bumper 94 arrived. This reduces the risk of an operator of the trailer hitch 10 being injured by the coupling arm 20 when the fixing device 80 is released.

This braking behavior of the braking device 70 is particularly advantageous in connection with the fixing using the fixing device 80 explained below.

The fixing device 80 comprises a fixing body 81, for example a bolt body, which engages in a fixing position F in a positive-locking receptacle 82 in order to fix the coupling arm bearing element 50 and thus the coupling arm 20 in the use position G and preferably also the non-use position N with respect to the pivot axis or pivot axis D .

In a release position L, the fixing body 81 is moved out of the positive-locking receptacle 82 so that the coupling arm bearing element 50 can rotate about the pivot axis or pivot axis D with respect to the holder bearing element 31 or is non-rotatable.

The end wall 63 of the sealing element 60 is advantageously supported by the section 16B of the holding element 15 so that the braking contour 71 protruding in front of the end wall 63 or arranged on the end wall 63 is also supported by the holding element 15 . The section 16B forms a support contour 16K for supporting the end wall 63 and thus the brake contour 71 or provides a support contour 16K ready. The end wall 63 is preferably supported flat on the support contour 16K. The end wall 63 and the support contour 16K extend radially with respect to the pivot axis D. A normal direction of the end wall 63 and the support contour 16K is preferably parallel to the pivot axis D.

When brake body 72 slides along brake contour 71, it rubs against brake contour 71 on the one hand and compresses the material of sealing element 60 in the area of end wall 63 on the other.

The end wall 63 is further supported against the action of a force by the brake body 72 by the seal receptacle 59 , which represents a positive-locking receptacle supporting the end wall 63 .

However, it is also readily conceivable and possible for a displacement cavity 75 to be arranged on the holding element 15, into which the end wall 63 or the braking contour 71 can be deformed in the sense of flexing. The braking body 72 thus performs flexing work with regard to the braking contour 71, which has the effect of braking. Furthermore, the brake contour 71 can also be deformed into a free space 76 next to the holding element 15 or outside of the holding element 15, for example in the direction of the peripheral wall 61, which also causes flexing and thus braking of the brake body 72 and thus the clutch arm 20.

The braking contour 71 extends transversely to the pivot axis D around the pivot axis D around. A braking surface 77 of the braking contour 71 thus has a normal or normal component NK parallel to the pivot axis D. The braking body 72 acts with a force component parallel to the pivot axis D on the braking contour 71 with its braking surface 78 .

However, a radial deceleration, so to speak, with respect to the pivot axis D is also readily possible. For example, a brake contour 71 R protrudes radially inwards with respect to the pivot axis D in front of the peripheral wall 61, in particular in the region of a lower or lowermost pivot position of the coupling arm 20 between the use position G and the non-use position N. on which the brake body 72 comes into braking contact with its radially outer end face.

Furthermore, the braking effect can be influenced, for example, in that the braking contour 71 has narrower or wider sections or protrudes further or less far from the braking body 72 . For example, a narrower section 79, in particular in the form of a waist, can be provided on the brake contour 71. At section 79, the braking surface 77 is less wide than at other sections of the braking contour 71, so that the contact area between the braking body 72 and the braking contour 71 is smaller in the area of the narrower section 79 and the braking effect is therefore also lower, e.g. when the braking contour 71 is worn the brake body 72 is deformed, for example flexed and/or compressed.

The positive-locking receptacle 82 is in two parts, so to speak, and has bearing element receiving sections 83G, 83N on the coupling arm bearing element 50 and a holder receiving section 84 which is stationary with respect to the holder 11, for example on the holder bearing element 31. The bearing member accommodating portions 83G and 83N are associated with the G position of use and the N position of non-use.

The bearing member accommodating portions 83G and 83N are laterally open radially outward with respect to the pivot axis D . The holder accommodating section 84 is open radially inward with respect to the pivot axis D. FIG. If the receiving sections 83G and 84 or 83N and 84 face each other in the use position G or the non-use position N, they form the form-fitting receptacle 82.

The holder receiving section 84 is open towards the swivel bearing seat 32, ie radially inwards towards the swivel axis D. The pivot mount 32 forms a pivot mount portion 32A on which the holder receiving portion 84 is disposed. The fixing element 81 is guided along an adjustment axis V in a guide 85 with respect to the holder 11 , specifically the holder bearing element 31 . The adjustment axis V runs parallel to the pivot axis or pivot axis D. In the present case, the guide 85 is designed as a linear guide. The guide 85 is located in a guide section 39 of the holder bearing element 31. The guide section 39 is arranged or provided, for example, on or next to the section of the holder bearing element 31 that has the bearing shaft receptacle 33. In any case, it should be mentioned that the positive-locking receptacle 82 does not form part of the guide 85 .

The guide 85 is designed, for example, as a guide channel 85K in the guide section 39 or has a guide channel 85K.

The fixing element 81 is loaded in the direction of the fixing position F by a spring 86, thus a spring arrangement. The spring 86 is supported on a support surface 86A on an end region of the guide 85 facing away from the fixing element 81 and on a support surface 86B of the fixing element 81 . The support surface 86B is provided, for example, on a bottom portion of a receiving recess on the fixing member 81 for the spring 86. The fixing element 81 can be moved from the fixing position F into the release position L against the force of the spring 86 .

A release body 87 is provided for moving the fixing element 81 from the fixing position F to the release position L. The release body 87 has a rod-like shape or a longitudinal body 87A and is connected to the fixing element 81 with an abutment head 87B. The abutment head 87B is supported on a receptacle 81Z of the fixing element 81, for example. The longitudinal body 87A has an actuating section 87C on its end region facing away from the fixing element 81 . The actuating section 87C or the release body 87 as a whole preferably form a pulling element for actuating the fixing element 81 in the direction of the release position L. For example, a release cable or another similar pulling element for a pulling operation of the release body 87 could be provided on the actuating section 87A.

An actuating contour 87D, for example a toothing, is preferably provided on the actuating section 87C, in which an output 87E, for example a toothed wheel, of a release drive 87F engages, for example meshing with the actuating contour 87D. The release drive 87F generates, for example, a release movement VL in order to actuate the fixing element 81 from the fixing position F in the direction of the release position L. In the opposite direction, i. H. in the direction of the fixing position F, the spring 86 acts.

The fixing element 81 has a cylindrical support surface 81A which, in the fixing position F, bears positively against a cylindrical abutment surface 83Z of the respective bearing element receiving section 83 and a likewise cylindrical abutment surface 84Z of the holder receiving section 84 . The abutment surfaces 83Z and 84Z extend parallel to the guide axis V, which in turn runs parallel to the pivot axis D. The support surface 81A and the abutment surfaces 83Z, 84Z cannot be disengaged by the action of a torque about the pivot axis D, so that the locking and form-fit fixing of the coupling arm 20 is ensured even under high loads when driving.

In order to clamp fixing element 81, clamping surfaces can be provided in an engagement area between fixing element 81 and positive-locking receptacle 82, for example a clamping bevel or insertion bevel 81S on the free, front end region of fixing element 81 and/or a clamping bevel 83S on the bearing element receiving section 83.

At this point it should be mentioned that the holder receiving section 84 only has the cylindrical bearing surface 84Z, but no surface assigned to the end face or front side of the fixing element 81 and/or serving as a stop surface. On the bearing element receiving section 83, on the other hand, an end surface or a frontal stop surface 83E with respect to the guide axis V is provided. The clamping bevel 83S extends between the cylindrical section or the cylindrical abutment surface 83Z and the abutment surface 83E. In the fixing position V, however, the fixing element 81 is not supported on the stop surface 83E, but instead engages with the clamping bevel 83S. If the clamping bevel 83S is not present, an end face 81F of the cylindrical fixing element 81 strikes the stop face 83E.

During the movement between the use position G and the non-use position N, the end face 81 F slides along a support surface extending between the bearing element receiving sections 83 , for example on the rear side 38 of the holder bearing element 31

The release drive 87F includes, for example, an electric drive 122 , for example an electric drive, which is arranged in a protective housing 121 of a drive module 120 . Drive module 120 has, for example, a gear 123 arranged between release drive 87F and its output drive 87E, in particular a gear of this type which also includes an anti-release device, so that only when the release drive 87F is actively actuated, for example by means of a gear arranged in an interior of motor vehicle 90 or electric switch 127 that can be arranged or a wireless remote control 124, the fixing device 80 can be released, but otherwise the release drive 87F is self-locking and/or internally locked. The guide section 39 of the holder bearing element 31 is connected to an interface 126 of the drive module 120 with a connecting element 125 and connected thereto. Interface 126 includes, for example, a receiving opening for connecting element 125 and/or a screw connection and/or a latching connection for connecting release drive 87F and drive module 120 to release body 87.

Claims

Expectations

1 . Trailer coupling for a motor vehicle (90) with a coupling arm (20), wherein the coupling arm (20) has a coupling element (27), in particular a coupling ball (27A), and on a motor vehicle (90) attached or attachable holder (11) using a swivel bearing (30) between a use position (G) and a non-use position (N), the coupling arm (20) being in the use position (G) for attaching a trailer (AK) or attaching a load carrier (LT) to the coupling element (27) of the coupling arm (20) protrudes further to the rear in front of a rear end (95) of the motor vehicle (90) than in the non-use position (N) intended for non-use of the coupling arm (20), the holder (11) having a pivot bearing section (32A ) for the pivot bearing (30), on which a coupling arm (20) carrying the coupling arm bearing element (50) about a pivot axis (D) is pivotally mounted, wherein the trailer hitch (10) has a Bremseinri Device (70) for braking a pivoting movement of the coupling arm bearing element (50) with respect to the holder (11) during the pivoting movement between the use position (G) and the non-use position (N), which has a brake body (72) and a brake contour (71) for cooperation with the brake body (72), the brake body (72) and the brake contour (71) sliding along one another during the pivoting movement of the coupling arm bearing element (50) between the use position (G) and the non-use position (N) and braking the pivoting movement, characterized characterized in that the braking contour (71) and the braking body (72) are designed in such a way that the braking contour (71) and the braking body (72) generate at least two different braking forces during the pivoting movement between the position of use (G) and the position of non-use (N) exert on the clutch arm bearing element (50).

2. Trailer coupling according to claim 1, characterized in that on the brake body (72) and / or the brake contour (71) at least one frictional contact surface is provided for providing a braking force by frictional engagement.

3. Trailer coupling according to Claim 1 or 2, characterized in that the brake body (72) and/or the brake contour (71) can be elastically deformed to provide the braking forces, in particular in the sense of flexing and/or compression of the brake body (72) or the brake contour (71) or both.

4. Trailer coupling according to one of the preceding claims, characterized in that the brake body (72) and the brake contour (71) along a ring-shaped around the pivot axis (D) extending contact track (71 K) are in braking engagement with each other.

5. Trailer coupling according to Claim 4, characterized in that the contact path (71K) is shorter than a path of movement (BB) of the brake body (72) which the brake body (72) moves when the coupling arm bearing element (50) is adjusted between the non-use position (N ) and the position of use (G).

6. Trailer coupling according to Claim 4 or 5, characterized in that the brake contour (71) has contact surfaces arranged one behind the other with respect to the contact track (71K) for contact with the brake body (72), which protrude to different extents in the direction of the brake body (72) and /or have different widths.

7. Trailer coupling according to one of claims 4 to 6, characterized in that the brake contour (71) with respect to the contact track (71K) has successively arranged contact surfaces for contact with the brake body (72), which have different friction properties from one another.

8. Trailer coupling according to one of the preceding claims, characterized in that the brake body (72) is formed by a stop body or is arranged on a stop body, the stop body limiting a pivoting movement of the coupling arm bearing element (50) relative to the holder (11).

9. Trailer coupling according to one of the preceding claims, characterized in that a clearance section (73G, 73N) is provided between the brake contour (71) and a pivot stop assigned to the non-use position (N) or the use position (G), in which the brake body (72 ) is not braked or braked less than in the area of the brake contour (71).

10. Trailer coupling according to claim 9, characterized in that a clearance section (73G) associated with the use position (G) is longer than a clearance section (73N) associated with the non-use position (N), or vice versa.

11 . Trailer coupling according to Claim 9 or 10, characterized in that a slide-on section (74G, 74N), in particular a ramp and/or an inclined surface, is arranged between the braking contour (71) and at least one clearance section (73G, 73N), on which the brake body (72) starting from the clearance section (73G, 73N) can slide onto the braking contour (71).

12. Trailer coupling according to one of the preceding claims, characterized in that it has a sealing element (60) for sealing the trailer coupling and/or for sealing the pivot bearing (30) and/or for sealing the braking device (70).

13. Trailer coupling according to claim 12 or the preamble of claim 1, characterized in that the brake contour (71) and / or the brake body (72) is arranged in an interior (60A) through the or a sealing element (60) for sealing the hitch of the swivel bearing (30) is sealed.

14. Trailer coupling according to one of claims 12 or 13 or the preamble of claim 1, characterized in that the braking contour (71) is arranged between sealing sections (61D, 64D) with which the or a sealing element (60) for sealing the trailer coupling or the pivot bearing (30) tightly, in particular during the entire pivoting movement between the use position (G) and the non-use position (N), on the holder (11) and tightly on the coupling arm bearing element (50).

15. Trailer coupling according to one of claims 12 to 14 or the preamble of claim 1, characterized in that sealing sections (61D, 64D) of the sealing element (60), between which the braking contour (71) is located, with a press fit and/or with a material bond and/or are held by means of an adhesive bond on at least one component of the coupling arm bearing element (50) or holder (11) and/or are positively engaged with at least one component of the coupling arm bearing element (50) or holder (11) and/or by means of interlocking sealing contours (59K, 64K) are sealed to the sealing member (60) and the retainer (11) and/or the sealing member (60) and the clutch arm bearing member (50).

16. Trailer coupling according to one of claims 12 to 15, characterized in that the sealing element (60) during the pivoting movement between the non-use position (N) and the use position (G) in which the brake body (72) along the brake contour (71). slides, is held in a tight fit on the holder (11) and on the coupling arm bearing element (50).

17. Trailer coupling according to one of claims 12 to 16, characterized in that the braking contour (71) or the brake body (72) is arranged on the sealing element (60) for sealing the trailer coupling.

18. Trailer coupling according to claim 17, characterized in that the brake contour (71) is arranged on a wall section of the sealing element (60) which can be compressed and/or walked and/or by the brake body (72). can be deformed into a displacement cavity (75) facing away from the brake body (72).

19. Trailer coupling according to one of Claims 17 or 18 or the preamble of Claim 1, characterized in that the braking contour (71) is arranged on a section of the sealing element (60) which, in particular, is caused by the braking body (72) when the Brake contour (71) opposite support contour (16K) of the holder (11) or the Kupplungsarmlagerelements (50) is supported.

20. Trailer coupling according to one of Claims 17 to 19 or the preamble of Claim 1, characterized in that the braking contour (71) is arranged on a section of the sealing element (60) which, in relation to a direction of force in which the braking body (72 ) acts on the brake contour (71), based on a positive connection between the sealing element (60) and the holder (11) or the Kupplungarmlagerelement (50) is supported.

21 . Trailer coupling according to one of the preceding claims, characterized in that the brake contour (71) extends transversely, in particular at right angles transversely, to the pivot axis (D) around the pivot axis (D), so that the brake body (72) has a force direction parallel to the pivot axis (D) acts on the braking contour (71) during its braking intervention on the braking contour (71).

22. Trailer coupling according to one of the preceding claims, characterized in that the brake body (72) rotatably held on the clutch arm bearing element (50) and the brake contour (71), in particular the sealing element (60), rotatably held on the holder (11). are.

23. Trailer coupling according to one of the preceding claims, characterized in that the trailer coupling has a fixing device (80) for fixing the coupling arm (20) at least in the position of use (G), the fixing device (80) having a fixing element (81) which by means of a guide with respect to the coupling arm bearing element (50) and/or the holder (11) between a fixing position (F), in which the fixing element (81) rotationally fixes the coupling arm bearing element (50) with respect to the pivot axis (D), and a release position (L) in which the coupling arm bearing element (50) is movably mounted with respect to the Pivot axis (D) is rotatable.