Trailer coupling

Abstract

The aim of the invention is to reduce, preferably to minimize, noise generation during the transition from the released position into the rotation-blocking position. This aim is achieved in that the rotation-blocking device is assigned at least one locking unit which delays a transition, which has been initiated via action upon the rotation-blocking device, of the latter into the rotation-blocking position at least when the operating position and / or the idle position is reached.

Description

[0001] TOW HOIST

[0002] The invention relates to a trailer coupling comprising a ball neck movable between a working position and a rest position with a pivot bearing body arranged at a first end and a coupling ball arranged at a second end, a pivot bearing unit arranged fixed to the vehicle, by means of which the pivot bearing body is pivotally received to execute a pivoting movement about a pivot axis between the working position and the rest position, and a rotation-blocking device acting between the pivot bearing unit and the pivot bearing body with, on the one hand, at least one rotation-blocking unit which has a rotation-blocking body which is movably guided in a guide direction by means of a guide receptacle of a guide body and which is movable in the guide direction by means of a pressure surface extending transversely to the guide direction and provided on an actuating body,and on the other hand, with at least one working position receptacle and / or at least one rest position receptacle, wherein by moving the actuating body in the actuating direction, the rotation-blocking body of the rotation-blocking unit can be moved and acted upon in the guide direction, and wherein the rotation-blocking body of the rotation-blocking unit can be moved into a rotation-blocking position in the working position and / or the rest position by moving it in the guide direction, and in this position the rotation-blocking body engages with a respective working position receptacle or rest position receptacle in order to block a pivoting movement of the pivot bearing body about the pivot axis relative to the guide body, and wherein the rotation-blocking body can be brought into a release position and in this position is disengaged from the working position receptacle and / or the rest position receptacle and releases the pivoting movement of the pivot bearing body.

[0003] Such trailer couplings are known from the prior art, and they suffer from the problem of noise generation when the rotation-locking unit transitions into the rotation-locking position. The invention is therefore based on the object of reducing, preferably minimizing, noise generation during the transition from the release position to the rotation-locking position.

[0004] This object is achieved according to the invention in a trailer coupling of the type described at the outset in that at least one locking unit is assigned to the rotation-blocking device, which at least when the working position and / or the rest position is reached, delays a transition of the rotation-blocking device into the rotation-blocking position caused by an action on the rotation-blocking device.

[0005] The advantage of this solution is that it reduces noise during the transition to the rotation-locking position.

[0006] The invention thus relates to trailer couplings in which the rotation-locking device is intended to be effective only in the working position, as well as to trailer couplings in which the rotation-locking device is intended to be effective in the working position and the rest position, as well as to trailer couplings in which the rotation-locking device is intended to be effective only in the rest position.

[0007] In principle, the delay unit could be designed in such a way that it delays the effect on the rotation-blocking device when it transitions into the rotation-blocking position.

[0008] However, it is particularly advantageous if at least one delay unit acts on the rotation blocking device itself.

[0009] It is particularly advantageous if the at least one delay unit delays the transition of the rotation-locking unit into the rotation-locking position, as this results in a significant reduction in noise generation. The at least one delay unit can be designed to act on one or more elements of the rotation-locking device.

[0010] A particularly advantageous solution provides that the at least one delay unit acts directly on one of the elements of the rotation-locking device, i.e. delays a movement of this element by directly acting on this element.

[0011] An advantageous embodiment of the at least one delay unit provides for it to delay the movement of the rotation-locking body into the rotation-locking position. This delay can be achieved by direct, in particular immediate, action on the rotation-locking body and / or by indirect, in particular indirect, action.

[0012] Another possibility is for the at least one delay unit to delay the movement of the actuating body into the rotation-locking position. This is particularly an indirect deceleration effect.

[0013] This can be achieved in an advantageous embodiment of at least one delay unit in that the delay unit is effective between the guide body and the actuating body.

[0014] For this purpose, for example, at least one delay unit can be arranged on the actuating body.

[0015] Alternatively or additionally, it is also possible for the at least one delay unit to be arranged on the guide body.

[0016] A particularly simple design of a deceleration unit provides for at least one deceleration unit to have a spring-elastic element. For example, it is conceivable for the spring-elastic element to form at least one friction surface or act upon a friction body.

[0017] A simple solution provides that the at least one delay unit comprises a movement delay body which is effective between a surface of the actuating body and a surface of the guide body facing this.

[0018] In the simplest case, the movement delay body is designed as a rotation delay ring, which acts between an annular surface of the actuating body and an annular surface of the guide body facing this.

[0019] It is particularly advantageous if the movement deceleration body has a different friction effect depending on the direction of movement.

[0020] This allows, for example, the interaction between the actuating body and the guide body to be designed in such a way that a strong deceleration effect occurs in one direction of movement, in particular a direction of movement in the direction of the rotation-blocking position, and a smaller deceleration occurs when moving out of the rotation-blocking position.

[0021] A further advantageous solution which can be used in addition to or as an alternative to one of the above-mentioned delay units provides that the at least one delay unit is arranged in a defined position on the guide body or the actuating body and, starting from this, has a delaying effect on the actuating body or the guide body moving relative to it.

[0022] In this case, it is also preferable for the deceleration unit to be provided with a friction body acted upon by a spring-elastic body, which acts on the actuating body or the guide body. Such a solution can be advantageously implemented by having the deceleration unit arranged on the guide body or the actuating body act with the friction body on a friction surface arranged on the actuating body or the guide body, since a friction surface allows reproducible conditions to be created.

[0023] This solution provides a simple way to interact with the delay unit arranged on one of the bodies with the other of the bodies under defined conditions, so that a delay in the movement of the actuating body is enabled in a direction of rotation in which the actuating body moves the respective rotation-blocking body from the release position to the locking point.

[0024] Preferably, the friction surface is designed such that it extends over an angular range around the axis of rotation of the actuating body, so that the relative movement between the guide body and the actuating body allows the delay unit to interact with the friction surface during a definable period of time.

[0025] Preferably, the friction surface extends over an angular range around the axis of rotation of the actuating body which corresponds to the angular range of the rotational movement of the actuating body which is required in order to move it from the release position into the rotation-blocking position.

[0026] In particular, the friction surface is designed such that it extends from a deceleration start region, which is assigned to the release position, to a deceleration end region, which is assigned to the rotation blocking position.

[0027] It is particularly advantageous if the area of ​​the friction surface acted upon by the friction body runs at a varying distance from a guide receptacle of the deceleration unit during a rotational movement of the actuating body relative to the guide body, i.e. the distance between the guide receptacle and the area of ​​the friction surface acted upon by the friction body does not have to be constant.

[0028] A particularly advantageous solution provides that when the friction body acts on the deceleration end region, the spring-elastic body acts on the friction body with a greater force than when the friction body acts on the deceleration start region.

[0029] This solution has the great advantage that by increasing the force acting on the friction body, there is also an increased deceleration effect of the interaction between the friction body and the friction surface, and thus the rotational movement of the actuating body is increasingly slowed down during the rotational movement from the release position to the rotation-blocking position, the more the rotational movement of the actuating body approaches the rotation-blocking position of the actuating body.

[0030] One possible implementation provides that the area of ​​the friction surface acted upon by the friction body moves increasingly in the direction of the guide receptacle with increasing movement of the friction body from the deceleration start area to the deceleration end area in order to increasingly tension the spring-elastic body.

[0031] In this case, the area of ​​the deceleration end region acted upon by the friction body could still be inclined relative to the guide mount and thus still generate a torque acting in the direction of the release position when acted upon by the friction body.

[0032] A particularly advantageous solution provides that the deceleration end region acted upon by the friction body extends over its entire area acted upon by the friction body along a circular arc around the axis of rotation of the actuating body or at approximately the same distance from the guide receptacle in order to thereby not generate a torque acting in the direction of the release position, which would counteract the torque acting in the direction of the rotation-blocking position of the actuating body and thus reduce the force acting on the rotation-blocking bodies in the direction of the rotation-blocking position.

[0033] The friction body could act on the actuating body in a variety of ways.

[0034] An advantageous solution provides that the friction body acts circumferentially on the actuating body, in particular on a circumferentially arranged friction surface thereof, in order to delay its movement in the direction of the rotation-blocking position.

[0035] Preferably, the at least one deceleration unit is arranged such that the friction body acts on a pressure surface acting on a rotation-blocking body in order to act on the rotation-blocking body.

[0036] Alternatively or additionally, it is particularly advantageous if the friction body acts on a circumferential area of ​​the actuating body adjacent to a pressure surface for acting on the rotation-blocking body.

[0037] In this case, the peripheral area is preferably provided with a friction-promoting surface in such a way that greater friction occurs between it and the friction body than can be achieved when interacting with the pressure surface, since this should have an optimal effect on the rotation-blocking body.

[0038] Alternatively, a further variant of the solution according to the invention provides that the friction body acts on the front side of the actuating body, in particular on a friction surface arranged on the front side of the actuating body. In this case, the deceleration unit is arranged in the guide body and acts with the friction body on the front side of the actuating body, i.e., in particular on a friction surface arranged on the front side of the actuating body.

[0039] A further alternative solution provides that the friction body, with the deceleration unit arranged in the actuating body, acts on wall surfaces of a receptacle provided in the guide body for the actuating body, in particular on a friction surface arranged on the receptacle.

[0040] Such a friction surface can, for example, be arranged on a cylindrical surface of the guide body forming the receptacle if the deceleration unit is arranged in the actuating body.

[0041] Alternatively, if the deceleration unit is arranged in the actuating body, such a friction surface can also be arranged on an inner side of a flange of the guide body which delimits the receptacle and faces the actuating body.

[0042] A further advantageous embodiment of at least one delay unit which can be used in addition to or as an alternative to one or more of the above solutions provides that the at least one delay unit acts on a rotation-blocking body when the working position and / or the rest position is reached, in particular acts directly on this, and delays its movement in the working position receptacle or rest position receptacle.

[0043] No further details have been provided so far regarding the arrangement of such a delay unit.

[0044] One advantageous solution provides that the delay unit is assigned to at least the working position receptacle and / or the rest position receptacle. Such a delay unit operates particularly advantageously if it counteracts the impact of the rotation-locking body on a base of the working position receptacle and / or the rest position receptacle by delaying it.

[0045] Such a delay unit can be designed particularly advantageously if it comprises a spring-elastic element which counteracts the movement of the rotation-blocking body in the direction of the respective receiving base in a delaying manner.

[0046] Furthermore, it is preferably provided that this at least one deceleration unit is held and supported on a component of the pivot bearing unit carrying the receptacle.

[0047] One such component of the pivot bearing unit is the pivot bearing body.

[0048] Furthermore, it is preferably provided that the spring-elastic element has a decelerating effect on the rotation-blocking body entering the receptacle via a deceleration body, so that the rotation-blocking body does not act directly on the spring-elastic element, but the spring-elastic element is given additional protection by the deceleration body.

[0049] Furthermore, such a delay unit can be designed particularly advantageously if it has a guide body which accommodates the spring-elastic element and, if appropriate, the delay body.

[0050] In this case, it is particularly advantageous if the guide body is held in an adjustably positionable manner on the component carrying the receptacle, for example the pivot bearing body. In the case of a delay unit which acts on a rotation-locking body in the working position and / or the rest position and delays its entry into the working position receptacle or rest position receptacle, it is preferably provided that if there are several working position receptacles and / or several rest position receptacles, the delay unit is only assigned to one working position receptacle or one rest position receptacle, since in this case the delay unit can act on the rotation-locking body impinging on it in such a way that the rotation-locking body in turn acts back on the actuating body and, in turn, the reaction on the actuating body also leads to the other rotation-locking bodies being moved into the provided working position receptacles or rest position receptacles with a delay.Resting position recordings occur.

[0051] In general, the solution according to the invention further advantageously provides that the rotation-blocking device has at least two rotation-blocking units, and thus at least two working position receptacles are assigned to the working position and / or at least two rest position receptacles are assigned to the rest position.

[0052] In this case too, the present invention described below relates to trailer couplings with only at least two working position receptacles as well as trailer couplings with at least two working position receptacles and at least two rest position receptacles as well as trailer couplings with only two rest position receptacles.

[0053] In order to achieve the simplest possible fixation of the rotation-locking device in the release position in such a case, it is advantageously provided that blocking surfaces run between the working position receptacles and / or the rest position receptacles, against which the rotation-locking bodies can be placed and from which the working position receptacles and / or the rest position receptacles extend, that the rotation-locking units and the working position receptacles and / or the rest position receptacles are arranged at angular distances from one another around the pivot axis in such a way that in all intended pivot positions of the pivot bearing body, except for the working position and / or the rest position, the rotation-locking body of at least one of the rotation-locking units is opposite one of the blocking surfaces and thus this blocking surface, in particular when a force is applied to the actuating body,a movement of the actuating body in the actuating direction and consequently also a force-loaded engagement of the rotation-locking bodies of each of the rotation-locking units in one of the working position receptacles or rest position receptacles is blocked.

[0054] The advantage of the solution according to the invention is therefore that the fixing of the actuating body in the release position can be realized in a simple and reliable manner by means of the rotation-blocking bodies that are already present and that, in addition, a significant reduction in noise occurs during the transition of this trailer coupling from the release position to the rotation-blocking position of the rotation-blocking bodies, since the rotation-blocking bodies can slide easily from the blocking surfaces into the receptacles.

[0055] This solution further provides, in a trailer coupling according to the invention, alternatively or in addition to the solution described above, that the rotation-blocking units are arranged at angular intervals around the pivot axis to form a rotation-blocking configuration, that the working position receptacles and / or the rest position receptacles are arranged at the same angular intervals around the pivot axis as the rotation-blocking units to form a receptacle configuration for the working position and / or the rest position, respectively, that the rotation-blocking configuration and the receptacle configuration of the working position receptacles in the working position or the rest position receptacles in the rest position are congruent with one another, so that the rotation-blocking bodies can engage in the working position receptacles or the rest position receptacles,and that the angular distances between the rotation-locking units of the rotation-locking configuration and the angular distances between the working position receptacles or rest position receptacles of the receptacle configurations are selected such that the rotation-locking configuration and the receptacle configurations are only congruent with each other in the working position and / or the rest position and thus only allow a transition of the actuating body from the release position to the rotation-locking position in one of these or in both, while a transition of the actuating body from the release position to the rotation-locking position is not possible in the other pivot positions of the pivot bearing body.

[0056] Alternatively or additionally, a further advantageous solution provides that the angular distances of at least one of the rotation-blocking units are unequal from the rotation-blocking units arranged adjacently in a direction of rotation around the pivot axis and from the rotation-blocking units arranged opposite to this direction of rotation, and that in the working position the working position receptacles are arranged such that the rotation-blocking bodies of each of the rotation-blocking units can be brought into engagement with one of the working position receptacles, and / or that in the rest position the rest position receptacles are arranged such that the rotation-blocking body of each of the rotation-blocking units can be brought into engagement with one of the rest position receptacles, and that in all pivot positions of the pivot bearing body provided for operation that lie outside the working position and / or the rest position,the rotation-locking body of at least one of the rotation-locking units is located opposite a blocking surface located between the working position receptacles and / or the rest position receptacles, and the blocking surface blocks movement of the actuating body from the release position to the rotation-locking position, in particular when force is applied to the actuating body.

[0057] The inequality of the angular distances, starting from equal angular distances, amounts to, for example, at least a deviation from equal angular distances of the order of half the angular range over which each of the receptacles extends, preferably up to the angular range over which each of the receptacles extends. The advantage of all the aforementioned inventive solutions is that they provide a structurally simple solution for holding the actuating body in the release position and allowing it to transition into the rotation-blocking position only in the working position and / or the rest position, wherein the rotation-blocking bodies already present for the rotation-blocking device can be used particularly advantageously.

[0058] Within the scope of the solution according to the invention, it has proven particularly advantageous if the number of rotation blocking units corresponds to the number of working position receptacles and / or the number of rest position receptacles.

[0059] Furthermore, in order to obtain a spatially compact solution, particularly in the direction of the pivot axis, it is advantageous if the rotation-locking bodies of all rotation-locking units are designed and arranged symmetrically to a geometric plane running perpendicular to the pivot axis and intersecting it.

[0060] A particularly advantageous solution provides that the blocking surfaces face the rotation-blocking bodies of the rotation-blocking units, in particular transversely, preferably perpendicular to the guide direction, so that the rotation-blocking bodies can be moved over the blocking surfaces with little or almost no resistance to movement when they rest against them.

[0061] It is particularly advantageous if the blocking surfaces extend within a defined radius around the pivot axis, so that during the pivoting movement, the rotation-locking bodies resting against these blocking surfaces do not perform any additional radial movement relative to the pivot axis. Furthermore, it is advantageous for the blocking surfaces to extend to the opening edges of the working position receptacles and / or the rest position receptacles and merge into them.

[0062] In particular, it is preferably provided that the opening edges of the working position receptacles and / or the rest position receptacles are at the same radial distance from the pivot axis as the blocking surfaces, so that a movement of the rotation blocking bodies resting on the blocking surfaces over the opening edges into the receptacles can take place without additional movement resistance, as would occur, for example, with different distances of the opening edges from the pivot axis in relation to the distance of the blocking surfaces from the pivot axis.

[0063] In particular, this solution also has the advantage that it allows a simple and movement-resistance-free transition of the pivot bearing body from the working position to a pivot position, since in this case too the rotation blocking bodies can leave the working position receptacles and / or the rest position receptacles over the opening edges essentially without movement resistance and can move in the direction of the blocking surfaces.

[0064] It is particularly advantageous if at least one of the rotation-locking bodies of the rotation-locking units rests against one of the blocking surfaces during a pivoting movement of the pivot bearing body in the direction of the working position, in particular during the pivoting movement from the rest position to the working position, in particular is in contact with one of the blocking surfaces in a force-loaded manner by the action of the actuating body, wherein the force is applied, for example, by retraction receptacles in the actuating body provided for the release position of the rotation-locking bodies, which act on the rotation-locking bodies with surfaces running transversely to the guide direction.In particular, it is advantageous if the rotation-locking bodies rest against the blocking surfaces under the influence of force before reaching the working position and then enter the receptacles under the influence of force on the opening edges of the receptacles, so that the noise level when the rotation-locking bodies transition from the release position to the rotation-locking position can be kept as low as possible, in contrast to a case in which the rotation-locking bodies initially rest against the blocking surfaces with play, are then applied to the blocking surfaces under the influence of force and then enter from the blocking surfaces into the working position receptacles or the case in which the rotation-locking bodies move into the working position with play in relation to the blocking surfaces and are subjected to the influence of force in the working position in order to enter the working position receptacles.

[0065] With regard to the design of the working position receptacles, it is particularly advantageous if the working position receptacles extend from the blocking surfaces in the guide direction, in particular with at least one component in the radial direction to the pivot axis, so that the rotation blocking bodies do not experience any additional deflection when moving in the guide direction when entering the working position receptacles.

[0066] It is particularly advantageous if at least one of the rotation-locking bodies of the rotation-locking units rests against one of the blocking surfaces during a pivoting movement of the pivot bearing body in the direction of the rest position, in particular during the pivoting movement from the working position to the rest position, in particular in a force-loaded manner by the action of the actuating body, wherein the force is applied, for example, by retraction receptacles in the actuating body provided for the release position of the rotation-locking bodies, which act on the rotation-locking bodies with surfaces running transversely to the guide direction.In particular, it is advantageous if the rotation-locking bodies rest against the blocking surfaces under the influence of force before reaching the rest position and then enter the rest position receptacles under the influence of force on the opening edges of the rest position receptacles, so that the noise level when the rotation-locking bodies transition from the release position to the rotation-locking position can be kept as low as possible, in contrast to a case in which the rotation-locking bodies initially rest against the blocking surfaces with play, are then placed against the blocking surfaces under the influence of force and then enter the rest position receptacles from the blocking surfaces or the case in which the rotation-locking bodies move into the working position with play in relation to the blocking surfaces and are subjected to the influence of force in the working position in order to enter the rest position receptacles.

[0067] With regard to the design of the rest position receptacles, it is particularly advantageous if the rest position receptacles extend from the blocking surfaces in the guide direction, in particular with at least one component in the radial direction to the pivot axis, so that the rotation blocking bodies do not experience any additional deflection when entering the rest position receptacles during movement in the guide direction.

[0068] Furthermore, no further details were given regarding the alignment of the working position mounts and the rest position mounts and the blocking surfaces relative to the guide sleeve.

[0069] Thus, an advantageous solution provides that the working position receptacles and the rest position receptacles and the blocking surfaces of the guide sleeve are arranged facing each other, so that a deflection-free movement of the rotation blocking bodies can take place in the direction of the blocking surfaces or in the direction of the working position receptacles and the rest position receptacles.

[0070] In principle, the guide body could pivot around the pivot axis together with the pivot bearing body. However, a particularly advantageous design solution involves the guide body being part of the pivot bearing unit, which is fixed to the vehicle.

[0071] Furthermore, with regard to the design of the guide body, it is provided that all guide receptacles for the rotation-blocking bodies of the rotation-blocking units are arranged in the guide body.

[0072] Furthermore, it is expedient if the guide direction runs with at least one component in the radial direction to the pivot axis, so that the rotation-blocking bodies are moved with at least one component in the radial direction to the pivot axis between the rotation-blocking position and the release position and thus no exclusive movement of the rotation-blocking bodies takes place in the direction of the pivot axis in order to move them between the rotation-blocking position and the release position.

[0073] A particularly advantageous solution in terms of design provides that the guide body has a guide sleeve with guide receptacles for the rotation-locking bodies of the rotation-locking units and that, in particular, the rotation-locking bodies are guided by the guide body which adjoins the pivot bearing body in the radial direction.

[0074] In connection with the explanation of the above embodiments, no further details were given as to how the pivot bearing body should be pivotally mounted on the pivot bearing unit.

[0075] For this purpose, for example, a dedicated bearing could be provided on the pivot bearing unit, which is independent of the guide body.

[0076] However, it is particularly simple in terms of construction if the guide body has a pivot bearing for the pivot bearing body, i.e. it either carries a pivot bearing for the pivot bearing body or itself forms a pivot bearing for the pivot bearing body with an outer surface.

[0077] No further details were given regarding the movement of the actuating bodies in relation to the guide body.

[0078] An advantageous solution provides that the actuating body is guided so as to be movable relative to the guide body.

[0079] The actuating body could be movable relative to the guide body in the direction of the pivot axis between the rotation-blocking position and the release position in order to move the rotation-blocking bodies into the corresponding positions.

[0080] A solution which is particularly optimised with regard to space requirements provides that the actuating body is arranged so as to be rotatable about the pivot axis and in particular has wedge surfaces which extend over an angular range about the pivot axis and vary in a direction parallel to the guide direction, preferably combined with retraction receptacles.

[0081] Furthermore, no further details were given regarding the arrangement of the receptacles and the blocking surfaces.

[0082] An advantageous solution provides that the receptacles and the blocking surfaces are arranged on the pivot bearing body.

[0083] Furthermore, a constructive solution with regard to the absorption of the acting forces is particularly favorable if the actuating body is enclosed by the guide body and if, in particular, the pivot bearing body encompasses the guide body.

[0084] No further details were provided regarding the arrangement of the anti-rotation elements relative to the actuating element. In principle, the anti-rotation elements could be arranged so that they are encompassed by the actuating element.

[0085] For the spatial construction of the trailer coupling according to the invention, it has also proven advantageous if the rotation-blocking bodies are arranged around the actuating body.

[0086] It has proven to be particularly advantageous in terms of construction if the pivot bearing body forms an outer body which surrounds the pivot bearing unit on the outside and is arranged so as to be non-displaceable relative to the pivot bearing unit in the direction of the pivot axis, and if in particular the pivot bearing body forms an outer body which surrounds at least a partial area of ​​the rotation-blocking unit on the outside and is arranged so as to be non-displaceable relative to the guide body in the direction of the pivot axis, so that the pivot bearing body does not carry out any movement in the direction of the pivot axis when the rotation-blocking body moves from the rotation-blocking position to the release position and vice versa, but can be arranged so as to be non-displaceable in the direction of the pivot axis.

[0087] Such an arrangement of the pivot bearing body has, on the one hand, the advantage of a favorable spatial structure of the pivot bearing unit itself and the advantage of a relatively simple sealing of the pivot bearing unit, since the pivot bearing body does not perform any movements in the axial direction of the pivot axis.

[0088] Preferably, a seal is provided between a housing of the pivot bearing unit and at least one end side of the outer body, which seals off the pivot axis and prevents the ingress of dirt and moisture.

[0089] In such a solution, the pivot bearing body simultaneously represents the outer body that protects and encloses the pivot bearing unit, and because the outer body is arranged immovably relative to the pivot bearing unit in the direction of the pivot axis, it is achieved in particular that a simple seal can be realized between the outer body and the pivot bearing unit.

[0090] A particularly advantageous design solution is one in which the pivot bearing body forms at least one outer body which externally encloses a partial area of ​​the rotation-blocking device and which is arranged immovably relative to the guide body in the direction of the pivot axis.

[0091] In particular, it is provided that the rotation-blocking bodies can be moved by the actuating body from the release position into the rotation-blocking position.

[0092] Preferably, the actuating body is designed such that it allows the rotation-blocking bodies to be released in the release position.

[0093] In particular, a further embodiment of the rotation-blocking body provides that, in the rotation-blocking position, it holds the rotation-blocking bodies in their rotation-blocking position.

[0094] In order to ensure that the rotation-blocking bodies always move into their rotation-blocking position, in particular when there is no active actuation of the actuating body, it is preferably provided that the actuating body is acted upon by an elastic force accumulator in the direction of its rotation-blocking position.

[0095] In order to be able to move the actuating body from the rotation-blocking position into the release position, it is preferably provided that the actuating body can be moved from the rotation-blocking position into the release position by an actuating device.

[0096] In particular, such a movement of the actuating body by the actuating device occurs counter to the action of the energy accumulator, i.e. the actuating device counteracts the action of the energy accumulator and thus has to overcome the forces applied by the energy accumulator.

[0097] In particular in the case of a rotatable actuating body, it is preferably provided that the actuating device rotates the actuating body in the opposite direction to the direction of rotation caused by the elastic force accumulator.

[0098] Such an elastic energy storage device can in principle be arranged in several locations.

[0099] From a design perspective, it is particularly advantageous if the elastic force accumulator is arranged within the pivot bearing unit.

[0100] Another constructively advantageous solution provides for the elastic force accumulator to be arranged on one side of the actuating body.

[0101] In this case, the elastic force accumulator can be advantageously coupled to the actuating element.

[0102] With regard to the effect on the actuating body, a wide variety of solutions are conceivable.

[0103] An advantageous solution provides that the actuating device has an output element which is coupled to the actuating body.

[0104] In principle, it would be possible to rigidly couple the output element and the actuating body.

[0105] However, it is particularly advantageous if the output element and the actuating body are coupled to one another via a driving coupling device which allows a relative movement by a limited angle of rotation depending on the position of the output element and the position of the actuating body, in particular the rotational position thereof.

[0106] The driving coupling device could be an elastic connecting link.

[0107] However, it is particularly simple if the coupling device has a non-carrying free state and a carrying state, i.e. that either the free state or the carrying state is present.

[0108] In connection with the previous solutions, only the drive of the rotation-locking device was explained in general terms, which allows a transition of the rotation-locking device from at least one rotation-locking position to a release position and vice versa.

[0109] Furthermore, it is preferably provided that the actuating device for the rotation blocking device comprises a motor drive unit.

[0110] A motor drive unit could be provided that is exclusively assigned to the actuating device for the rotation locking device.

[0111] Furthermore, it is preferably provided that the reduction gear is arranged on a side of the actuating element of the rotation-blocking device facing the motor drive.

[0112] For a compact design, it is particularly beneficial if, viewed in the direction of the pivot axis, the reduction gear is driven by the motor drive unit on one side and has an output for the actuating element on the opposite side. Thus, the reduction gear is preferably arranged between the motor drive unit and the actuating element, viewed in the direction of the pivot axis.

[0113] Furthermore, the reduction gear, the elastic force accumulator and the actuating element are preferably arranged successively in the direction of the pivot axis, in particular within the pivot bearing unit.

[0114] In order to further ensure that the actuating body does not leave its rotation-blocking position despite being acted upon by the elastic energy accumulator, it is preferably provided that the actuating body can be blocked in its rotational position by a safety device.

[0115] In particular, it is provided that the actuating body can be blocked by the safety device against reaching its release position in order to ensure that the actuating body never independently allows the release position of the rotation-blocking bodies, for example in the event of a breakage of the elastic force accumulator acting on it in the direction of its active position.

[0116] Such a safety device is designed in such a way that it requires an action to release the blocking of the actuating body.

[0117] For this reason, it is expediently provided that the actuating device for the rotation-locking device is coupled to the safety device, so that the blocking of the actuating body by the safety device can also be released via the actuating device.

[0118] Preferably, the securing device is coupled to the actuating device in such a way that the securing device blocks any movement of the actuating body that is not triggered by an actuation. In particular, the securing device is designed such that it blocks any movement of the actuating body into its release position when the actuating device is not actuated.

[0119] A suitable solution provides that the drive element of the actuating device, for example the output element of the reduction gear, is coupled to the safety device.

[0120] The output element, for example the output element of the reduction gear, can expediently be designed in such a way that the effect on the actuating body and the effect on the safety device are coordinated with one another via the output element, so that actuation of the actuating device leads, on the one hand, to the blocking of the actuating body being lifted and, on the other hand, to the actuating body being moved from the active position to the inactive position.

[0121] For example, it is provided that the output element, in the course of its movement from the starting position to an intermediate position, transfers the safety device from the safety position to the release position.

[0122] With regard to the coupling between the output element and the safety device, a wide variety of options are conceivable.

[0123] For example, any type of coupling, including via an electrical control, would be conceivable.

[0124] A particularly practical solution, due to its simplicity, involves connecting the output element and the safety device via a mechanical coupling device. The mechanical coupling device is advantageously designed to control the action on the safety device via a guide track.

[0125] With regard to the design of the safety device, a wide variety of solutions are conceivable.

[0126] The safety device works particularly reliably if it has an elastic force accumulator which always acts on the safety device in the direction of its position securing or blocking the actuating body in the rotation-blocking position.

[0127] Furthermore, it is preferably provided that the safety device can be moved from its safety position into an unlocked position.

[0128] Preferably, the safety device is also moved into the unlocked position by the output unit for the actuating unit.

[0129] Within the scope of the solution according to the invention, it is provided that by energizing a drive, the drive acts on the actuating body from an initial position in the opposite direction to a force applied to the actuating body, in particular by a spring element, so that the actuating body is moved from the rotation-blocking position into the release position.

[0130] As soon as the release position of the rotation-locking device is reached, the pivot bearing body leaves the position, i.e. the working position or the rest position in which it was rotationally locked, and moves, in particular due to the effect of gravity, into an intermediate position, whereby the movement of the actuating body into the rotation-locking position is already blocked by the blocking surfaces after leaving the working position or the rest position. After leaving the working position or rest position, the drive is therefore energized in such a way that it moves back to its starting position. The actuating body thus has the option, when the pivot bearing body reaches the working position or rest position, in particular due to manual action, to move from the release position to the rotation-locking position due to the application of force and to lock the pivot bearing body again.

[0131] The above description of solutions according to the invention thus includes in particular the various combinations of features defined by the following numbered embodiments:

[0132] 1. Trailer coupling, comprising a ball neck (10) movable between a working position (A) and a rest position (R), with a pivot bearing body (14) arranged at a first end and a coupling ball (18) arranged at a second end, a pivot bearing unit (20) fixed to the vehicle, by means of which the pivot bearing body (14) is pivotally received to execute a pivoting movement about a pivot axis (22) between the working position (A) and the rest position (R), and a rotation-blocking device (50) acting between the pivot bearing unit (20) and the pivot bearing body (14), with, on the one hand, at least one rotation-blocking unit (80) which has a rotation-blocking body (54) which is movably guided in a guide direction (58) by means of a guide receptacle (56) of a guide body (40) and which is guided in the guide direction (58) by ais movable on an actuating body (52), and on the other hand with at least one working position receptacle (60A) and / or at least one rest position receptacle (60R), wherein by moving the actuating body (52) in an actuating direction (72), the rotation-blocking body (54) of the rotation-blocking units (80) is movable and loadable in the guide direction (58), and wherein the rotation-blocking body (54) of the rotation-blocking units (80) in the working position (A) and / or the rest position (R) can be brought into a rotation-blocking position by moving it in the guide direction (58), and in this position the rotation-blocking body (54) engages with a respective working position receptacle (60A) or rest position receptacle (60R) in order to block a pivoting movement of the pivot bearing body (14) about the pivot axis (22) relative to the guide body (40),and wherein the rotation-blocking body (54) can be brought into a release position and in this position is disengaged from the working position receptacle (60) and / or the rest position receptacle (60R) and releases the pivoting movement of the pivot bearing body (14), wherein the rotation-blocking device (50) is assigned at least one delay unit (300, 400, 500) which, at least upon reaching the working position (A) and / or the rest position (R), delays a transition of the rotation-blocking device (50) into the rotation-blocking position caused by an action on the rotation-blocking device (50).

[0133] 2. Trailer coupling according to embodiment 1, wherein the at least one deceleration unit (300, 400, 500) acts on the rotation blocking device (50).

[0134] 3. Trailer coupling according to embodiment 1 or 2, wherein the at least one delay unit (300, 400, 500) delays the transition of the rotation-blocking unit (80) into the rotation-blocking position.

[0135] 4. Trailer coupling according to one of the preceding embodiments, wherein the at least one deceleration unit (300, 400, 500) acts on one or more elements of the rotation blocking device (50).

[0136] 5. The trailer coupling according to one of embodiments 2 to 4, wherein the at least one delay unit (300, 400, 500) acts directly on one of the elements of the rotation-locking device (50). 6. The trailer coupling according to one of the preceding embodiments, wherein the at least one delay unit (300, 400, 500) delays the movement of the rotation-locking body (54) into the rotation-locking position.

[0137] 7. Trailer coupling according to one of the preceding embodiments, wherein the at least one delay unit (300, 400, 500) delays the movement of the actuating body (52) into the rotation-blocking position.

[0138] 8. Trailer coupling according to embodiment 7, wherein the at least one delay unit (300, 400) is effective between the guide body (44) and the actuating body (52).

[0139] 9. Trailer coupling according to embodiment 7 or 8, wherein the at least one deceleration unit (300, 400', 400"') is arranged on the actuating body (52).

[0140] 10. Trailer coupling according to one of embodiments 7 to 9, wherein the at least one deceleration unit (300, 400, 400") is arranged on the guide body (44).

[0141] 11. Trailer coupling according to one of the preceding embodiments, wherein the at least one deceleration unit (300, 400, 500) has a spring-elastic element (312, 314, 322, 336, 406, 504).

[0142] 12. Trailer coupling according to one of embodiments 7 to 11, wherein the resilient element (312, 314, 322, 336, 406) forms at least one friction surface (316, 318, 342) or acts upon a friction body (326, 328, 338, 402). 13. Trailer coupling according to one of embodiments 7 to 12, wherein the at least one deceleration unit (300) comprises a movement deceleration body (310) acting between a surface (302) of the actuating body (52) and a surface of the guide body (40) facing said surface.

[0143] 14. Trailer coupling according to embodiment 13, wherein the movement deceleration body (310) has a different friction effect depending on the direction of movement.

[0144] 15. Trailer coupling according to one of embodiments 7 to 12, wherein the at least one deceleration unit (400) is arranged in a defined position on the guide body (40) or the actuating body (52) and, starting therefrom, acts in a decelerating manner on the actuating body (52) or the guide body (40).

[0145] 16. Trailer coupling according to embodiment 15, wherein the deceleration unit (400) is provided with a friction body (402) acted upon by a spring-elastic body (406), which acts on the actuating body (52) or the guide body (40).

[0146] 17. Trailer coupling according to embodiment 15 or 16, wherein the deceleration unit (400, 400', 400", 400"') arranged on the guide body (40) or the actuating body (52) acts with the friction body (402, 402', 402", 402'") on a friction surface (403, 403', 403", 403'") which is arranged on the actuating body (52) or the guide body (40).

[0147] 18. Trailer coupling according to embodiment 17, wherein the friction surface (403, 403', 403", 403'") extends over an angular range around the rotational axis (22) of the actuating body (52). 19. Trailer coupling according to embodiment 17 or 18, wherein the friction surface (403, 403', 403", 403'") extends from a deceleration start region (405, 405', 405", 405'") to a deceleration end region (407, 407', 407", 407'").

[0148] 20. Trailer coupling according to one of embodiments 17 to 19, wherein the friction surface (403, 403', 403", 403'") extends at a varying distance relative to a guide receptacle (404, 404', 404", 404'") of the deceleration unit (400, 400', 400", 400'") during a rotational movement of the actuating body (52) relative to the guide body (40).

[0149] 21. Trailer coupling according to one of embodiments 17 to 20, wherein when the friction body (402, 402', 402", 402'") acts on the deceleration end region (407, 407', 407", 407'"), the spring-elastic body (406) acts on the friction body (402, 402', 402", 402'") with a greater force than when the friction body (402, 402', 402", 402'") acts on the deceleration start region (405, 405', 405", 405'").

[0150] 22. Trailer coupling according to embodiment 16, wherein the friction body (402, 402', 402", 402'") acts circumferentially on the actuating body (52), in particular on a circumferentially arranged friction surface (403, 403', 403", 403'").

[0151] 23. Trailer coupling according to embodiment 22, wherein the friction body (402) acts on a pressure surface (66) acting on a rotation-blocking body (54) for acting on the rotation-blocking body (54).

[0152] 24. Trailer coupling according to embodiment 22 or 23, wherein the friction body (402) acts on a circumferential region (71) of the actuating body (52) adjacent to a pressure surface (66) for acting on a rotation-locking body (54). 25. Trailer coupling according to one of embodiments 15 to 21, wherein the friction body (402) acts on the front side of the actuating body (52), in particular on a friction surface (403') arranged on the front side thereof.

[0153] 26. Trailer coupling according to one of embodiments 15 to 21, wherein the friction body (402) acts on a wall surface of a receptacle (102) provided in the guide body (40) for the actuating body (52), in particular on a friction surface (403", 403"') arranged on the receptacle (102).

[0154] 27. Trailer coupling according to one of the preceding embodiments, wherein the at least one delay unit (500) acts on a rotation-blocking body (54) upon reaching the working position (A) and / or the rest position (R) and delays its movement in the working position receptacle (60A) or rest position receptacle (60R).

[0155] 28. Trailer coupling according to embodiment 20, wherein the delay unit (500) is assigned to at least the working position receptacles (60A) and / or the rest position receptacle (60R).

[0156] 29. Trailer coupling according to embodiment 28, wherein the delay unit (500) counteracts an impact of the rotation-blocking body (54) on a receiving base (61A, 61R) of the working position receptacle (60A) and / or the rest position receptacle (60R) in a delaying manner.

[0157] 30. Trailer coupling according to embodiment 29, wherein the delay unit (500) comprises a spring-elastic element (504) which counteracts the movement of the rotation-blocking body (54) in the direction of the respective receiving base (61) in a delaying manner.

[0158] 31. A trailer coupling according to embodiment 29, wherein the deceleration unit (500') comprises a fluid braking element (505) made of a shear-thickening fluid. 32. A trailer coupling according to embodiment 30 or 31, wherein the deceleration unit (500) is held and supported on a component (14) of the pivot bearing unit (20) carrying the receptacle (60A, 60R).

[0159] 33. Trailer coupling according to one of embodiments 27 to 32, wherein the spring-elastic element (504) acts via a delay body (502) on the rotation-blocking body (54) entering the receptacle (60A, 60R) in a delaying manner.

[0160] 34. Trailer coupling according to one of embodiments 27 to 33, wherein the delay unit (500) is adjustably positionable relative to the receptacle (60A, 60R).

[0161] 35. Trailer coupling according to embodiment 34, wherein the deceleration unit (500) has a guide body (506) which receives the spring-elastic element (504) and optionally the deceleration body (502).

[0162] 36. Trailer coupling according to embodiment 35, wherein the guide body (506) is held in an adjustably positionable manner on the component (14) carrying the receptacle (60A, 60R).

[0163] 37. Trailer coupling according to one of the preceding embodiments, wherein blocking surfaces (90) extend between the working position receptacles (60A) and / or the rest position receptacles (60R), against which the rotation-blocking bodies (54) can be placed and from which the working position receptacles (60A) and / or the rest position receptacles (60R) extend, such that the rotation-blocking units (80) and the working position receptacles (60A) and / or the rest position receptacles (60R) are arranged at angular distances (W) from one another around the pivot axis (22) in such a way that in all intended pivot positions of the pivot bearing body (14), except for the working position (A) and / or the rest position (R), at least one of the rotation-blocking units (80) is opposite one of the blocking surfaces (90) and thus these blocking surfaces (90), in particular when a force is applied to the actuating body (52) in the direction of the actuation direction (72),a movement of the actuating body (52) in the actuating direction (72) and consequently also a force-loaded engagement of the rotation-blocking bodies (54) of each of the rotation-blocking units (80) in one of the working position receptacles (60A) or the rest position receptacles (60R) is blocked.,

[0164] 38. Trailer coupling according to one of the preceding embodiments, wherein the rotation-blocking units (80) are arranged at angular intervals (W) around the pivot axis (22) to form a rotation-blocking configuration, the working position receptacles (60A) and / or the rest position receptacles (60R) are arranged at the same angular intervals (W) around the pivot axis (22) as the rotation-blocking units (80) to form a respective receptacle configuration for the working position (A) and / or the rest position (R), the rotation-blocking configuration and the receptacle configuration of the working position receptacles (60A) in the working position (A) and the rest position receptacles (60R) in the rest position (R) are congruent with one another, so that the rotation-blocking bodies (54) can engage in the working position receptacles (60A) and the rest position receptacles (60R), respectively.and that the angular distances (W) between the rotation-blocking units (80) of the rotation-blocking configuration and the angular distances between the working position receptacles (60) and the rest position receptacles (60R) of the receptacle configurations are selected such that the rotation-blocking configuration and one of the receptacle configurations are only congruent with each other in the working position (A) and / or the rest position (R).

[0165] 39. Trailer coupling according to one of the preceding embodiments, wherein the angular distances (W) of at least one of the rotation-locking units (80) are unequal from the rotation-locking units (80) arranged adjacently in a direction of rotation around the pivot axis (22) and from the rotation-locking units (80) arranged opposite to this direction of rotation, such that in the working position (A), the working position receptacles (60A) are arranged such that the rotation-locking body (54) of each of the rotation-locking units (80) can be brought into engagement with one of the working position receptacles (60A), and / or such that in the rest position (R), the rest position receptacles (60R) are arranged such that the rotation-locking body (54) of each of the rotation-locking units (80) can be brought into engagement with one of the rest position receptacles (60R), and such that in all pivot positions of the pivoting body (14) provided for operation, which lie outside the working position (A) or the rest position (R),the rotation-blocking body (54) of at least one of the rotation-blocking units (80) is located opposite a blocking surface (90) extending between the working position receptacles (60A) and / or the rest position receptacles (60R), and the blocking surface (90), in particular when a force is applied to the actuating body (52), blocks a movement of the actuating body (52) from the release position into the rotation-blocking position.

[0166] 40. Trailer coupling according to one of embodiments 37 to 39, wherein the blocking surfaces (90) face the rotation blocking bodies (54) of the rotation blocking units (80).

[0167] 41. Trailer coupling according to one of embodiments 37 to 40, wherein the blocking surfaces (90) extend in a defined radius around the pivot axis (22).

[0168] 42. Trailer coupling according to one of the embodiments 37 to 41, wherein the blocking surfaces (90) extend to the opening edges (92) of the working position receptacles (60A) and / or the rest position receptacle (60R) and merge into these.

[0169] 43. Trailer coupling according to embodiment 42, wherein the opening edges (92) of the working position receptacles (60A) and / or the rest position receptacle (60R) are at the same radial distance from the pivot axis (22) as the blocking surfaces (90).

[0170] 44. Trailer coupling according to one of the embodiments 37 to 43, wherein at least one of the rotation blocking bodies (54) of the rotation blocking units (80) bears against one of the blocking surfaces (90) during a pivoting movement of the pivot bearing body (14) in the direction of the working position (A), in particular by the action of the actuating body (52), in a force-loaded manner.

[0171] 45. Trailer coupling according to one of the embodiments 37 to 44, wherein the rotation blocking bodies (54) bear against the blocking surfaces (90) in a force-loaded manner before reaching the working position (A) and then enter the working position receptacles (60A) in a force-loaded manner against opening edges (92) of the working position receptacles (60A).

[0172] 46. ​​Trailer coupling according to one of the embodiments 37 to 45, wherein the working position receptacles (60A) extend from the blocking surfaces (90) in the guide direction (58), in particular with at least one component in the radial direction to the pivot axis (22).

[0173] 47. Trailer coupling according to one of the embodiments 37 to 46, wherein at least one of the rotation-blocking bodies (54) of the rotation-blocking units (80) bears against one of the blocking surfaces (90) during a pivoting movement of the pivot bearing body (14) in the direction of the rest position (R), in particular by the action of the actuating body (52), in a force-loaded manner.

[0174] 48. Trailer coupling according to one of the embodiments 37 to 47, wherein the rotation blocking bodies (54) bear against the blocking surfaces (90) in a force-loaded manner before reaching the rest position (R) and then enter the rest position receptacles (60R) in a force-loaded manner against opening edges (92) of the rest position receptacles (60R).

[0175] 49. Trailer coupling according to one of embodiments 37 to 48, wherein the rest position receptacles (60R) extend from the blocking surfaces (90) in the guide direction (58), in particular with at least one component in the radial direction to the pivot axis (22). 50. Trailer coupling according to one of embodiments 37 to 49, wherein the working position receptacles (60A), the rest position receptacles (60R), and the blocking surfaces (90) are arranged facing the guide sleeve (40).

[0176] 51. Trailer coupling according to one of the preceding embodiments, wherein the guide body (40) is part of the pivot bearing unit (20) arranged fixed to the vehicle.

[0177] 52. Trailer coupling according to one of the preceding embodiments, wherein all guide receptacles (56) for the rotation-blocking bodies (54) of the rotation-blocking units (80) are arranged in the guide body (40).

[0178] 53. Trailer coupling according to one of the preceding embodiments, wherein the guide direction (58) extends with at least one component in the radial direction to the pivot axis (22).

[0179] 54. Trailer coupling according to one of the preceding embodiments, wherein the guide body (40) has a guide sleeve (44) with guide receptacles (56) for the rotation-blocking bodies (54) of the rotation-blocking units (80) and that in particular the rotation-blocking bodies (54) are guided by the guide body (40) adjoining the pivot bearing body (14) in the radial direction.

[0180] 55. Trailer coupling according to one of the preceding embodiments, wherein the guide body (40) has a pivot bearing for the pivot bearing body (14).

[0181] 56. Trailer coupling according to one of the preceding embodiments, wherein the actuating body (52) is guided so as to be movable relative to the guide body (40). 57. Trailer coupling according to one of the preceding embodiments, wherein the actuating body (52) is arranged rotatably about the pivot axis (22) and in particular has wedge surfaces (66) extending over an angular range about the pivot axis (22) and varying in a direction parallel to the guide direction (58), preferably combined with retraction receptacles (62).

[0182] 58. Trailer coupling according to one of the preceding embodiments, wherein the receptacles (60) and the blocking surfaces (90) are arranged on the pivot bearing body (14).

[0183] 59. Trailer coupling according to one of the preceding embodiments, wherein the actuating body (52) is enclosed by the guide body (40) and in particular the pivot bearing body (14) engages around the guide body (40).

[0184] 60. Trailer coupling according to one of the preceding embodiments, wherein the rotation-blocking bodies (54) are arranged around the actuating body (52).

[0185] 61. Trailer coupling according to one of the preceding embodiments, wherein the pivot bearing body (14) forms an outer body which surrounds the pivot bearing unit (20) on the outside and is arranged so as to be non-displaceable relative to the pivot bearing unit (20) in the direction of the pivot axis (22), and in particular that the pivot bearing body (14) forms an outer body which surrounds at least a partial area of ​​the rotation-blocking unit (50) on the outside and is arranged so as to be non-displaceable relative to the guide body (40) in the direction of the pivot axis (22).

[0186] 62. Trailer coupling according to one of the preceding embodiments, wherein the actuating body (52) is biased toward its rotation-locking position by an elastic force accumulator (114). 63. Trailer coupling according to one of the preceding embodiments, wherein the actuating body (52) is movable from the rotation-locking position to the release position by an actuating device (180).

[0187] 64. Trailer coupling according to embodiment 62 or 63, wherein the actuating body (52) is movable by the actuating device (180) against the action of the energy accumulator (114).

[0188] 65. Trailer coupling according to one of the embodiments 62 to 64, wherein the actuating body (52) can be rotated by the actuating device (180) opposite to the actuating direction (72) effected by the elastic force accumulator (114).

[0189] 66. Trailer coupling according to one of the preceding embodiments, wherein the actuating device (180) has an output element (142) which is coupled to the actuating body (52).

[0190] 67. Trailer coupling according to embodiment 66, wherein the output element (142) and the actuating body (52) are coupled to one another via a driving coupling device (156, 158).

[0191] 68. Trailer coupling according to embodiment 67, wherein the driving coupling device (156, 158) has a driving-free free state and a driving state.

[0192] 69. Trailer coupling according to one of the preceding embodiments, wherein the actuating device (180) for the rotation-locking device (50) comprises a motor drive unit.

[0193] Further features and advantages of the inventive solution are the subject of the following description and the drawing of an exemplary embodiment. The drawing shows:

[0194] Fig. 1 is a rear view of a motor vehicle with a trailer coupling according to the invention;

[0195] Fig. 2 is a plan view of a trailer coupling according to the invention, looking in the direction of travel at the trailer coupling mounted on a rear of a vehicle, the trailer coupling being in its working position;

[0196] Fig. 3 is a plan view of the trailer coupling in Fig. 2 in the direction of the pivot axis;

[0197] Fig. 4 is a view corresponding to Fig. 2 of the trailer coupling in the rest position;

[0198] Fig. 5 is a plan view of the trailer coupling according to Fig. 4 in the rest position in the direction of the pivot axis;

[0199] Fig. 6 is a view of a section taken along line 6-6 in Fig. 3;

[0200] Fig. 7 is a section along line 7-7 in Fig. 6 in the working position with rotation blocking by rotation blocking bodies in a rotation blocking position;

[0201] Fig. 8 is a representation of a section similar to Fig. 7 in the release position with the actuating body rotated into a release position and the rotation blocking bodies in the release position;

[0202] Fig. 9 is a view similar to Fig. 8 with the pivot bearing body pivoted slightly out of the working position, with the actuating body blocked under the action of the torsion spring; Fig. 10 is a view similar to Fig. 8 with the pivot bearing body rotated further toward the rest position, but in the release position;

[0203] Fig. 11 is a view similar to Fig. 10 with the pivot bearing body further rotated towards the rest position;

[0204] Fig. 12 is a view similar to Fig. 11 with the pivot bearing body further rotated towards the rest position;

[0205] Fig. 13 is a view similar to Fig. 7 in the rest position;

[0206] Fig. 14 is a view similar to Fig. 8 in the rest position;

[0207] Fig. 15 a section along line 15-15 in Fig. 6 without support plate and retaining ring;

[0208] Fig. 16 is a perspective view of a ring gear and a drive sleeve interacting with it;

[0209] Fig. 17 is an exploded perspective view of the pivot bearing body with the cover;

[0210] Fig. 18 is an enlarged section according to Fig. 6 in the working position;

[0211] Fig. 19 is an enlarged section similar to Fig. 18 in the rest position;

[0212] Fig. 20 is a schematic representation similar to Fig. 6 of a first exemplary embodiment of a trailer coupling according to the invention with a first exemplary embodiment of a deceleration unit; Fig. 21 is an enlarged partial representation in the region of the deceleration unit of the first exemplary embodiment of the trailer coupling according to the invention;

[0213] Fig. 22 is an enlarged view of a cross section through a delay ring of the first embodiment of the delay unit according to the invention;

[0214] Fig. 23 is an enlarged view of a first variant of the delay unit according to the first embodiment;

[0215] Fig. 24 is a perspective view of a second variant of the delay unit according to the first embodiment;

[0216] Fig. 25 is a representation of the actuating body in cooperation with a rotation delay ring of the second variant of the delay unit according to the first embodiment;

[0217] Fig. 26 is a perspective view of the rotation delay ring according to Fig. 24 and Fig. 25;

[0218] Fig. 27 is a view similar to Fig. 8 of a second embodiment of a trailer coupling according to the invention with a second embodiment of a deceleration unit according to the invention when the rotation blocking bodies begin to move in the direction of the working position receptacles;

[0219] Fig. 28 is a representation of the second embodiment of the trailer coupling according to the invention when the rotation-locking bodies are acted upon by an initial region of pressure surfaces of the actuating body; Fig. 29 is a representation of the second embodiment of the trailer coupling according to Fig. 28 with the rotation-locking bodies fully immersed in the working position receptacles;

[0220] Fig. 30 is a representation of a first variant of the second embodiment similar to Fig. 7,'

[0221] Fig. 31 is a representation of the first variant of the second embodiment similar to Fig. 28;

[0222] Fig. 32 is a representation of the first variant of the second embodiment similar to Fig. 29;

[0223] Fig. 33 is a representation of a second variant of the second embodiment;

[0224] Fig. 34 is an enlarged view of the delay unit of the second variant;

[0225] Fig. 35 is a view similar to Fig. 34 of a modification of the second variant;

[0226] Fig. 36 is a plan view of the actuating body with the friction surface and indicated friction body in the deceleration starting position in the second variant of the second embodiment;

[0227] Fig. 37 is a section along line 37-37 in Fig. 36;

[0228] Fig. 38 is a plan view of the actuating body with the friction surface and indicated friction body in the deceleration end position in the second variant of the second embodiment;

[0229] Fig. 39 is a section along line 39-39 in Fig. 38; Fig. 40 is a representation of a third variant of the second embodiment;

[0230] Fig. 41 is a view similar to Fig. 39 of the third variant of the second embodiment in the deceleration end position;

[0231] Fig. 42 is a view similar to Fig. 8 of a third embodiment of a trailer coupling according to the invention with a third embodiment of a delay unit according to the invention when the rotation blocking bodies begin to move in the direction of the working position receptacles;

[0232] Fig. 43 is a representation of the third embodiment of the trailer coupling according to the invention with the third embodiment of the deceleration unit with the rotation blocking bodies completely immersed in the working position receptacles,

[0233] Fig. 44 is a view similar to Fig. 42 of a first variant of the third embodiment and

[0234] Fig. 45 is a view similar to Fig. 43 of the first variant of the third embodiment.

[0235] A trailer coupling AK for a motor vehicle, shown in Fig. 1, 2 and 3 in a working position A and in Fig. 4 and 5 in a rest position R, comprises a ball neck, designated as a whole by 10, which is held by a first end 12 on a pivot bearing body 14 and carries at a second end 16 a coupling ball, designated as a whole by 18, to which a coupling ball receptacle of a trailer can be fixed.The pivot bearing body 14 is pivotally mounted about a pivot axis 22 relative to a vehicle-fixed support 24 by a pivot bearing unit designated as a whole by 20, wherein the support 24 preferably has a support plate 26 holding the pivot bearing unit 20, which preferably extends in a plane perpendicular to the pivot axis 22, and has a vehicle-fixed cross member 28 which can be fastened in a known manner to a rear region H of a vehicle body F, in such a way that the pivot bearing unit 20 and the support 24 lie on the side of a lower edge 30 of a bumper unit 36 ​​facing away from a road surface FO, and are covered by the bumper unit 36 ​​(Fig. 3).

[0236] 1 and 2, the ball neck 10 engages under the lower edge 30 of the bumper unit 36 ​​with a section 32 adjoining the first end 12, so that the second end 16 and the coupling ball 18 together with a socket receptacle 34 are located on a side of the rear bumper unit 36 ​​facing away from the vehicle body F, while in the rest position both the pivot bearing unit 20 and the entire ball neck 10 together with the coupling ball 18 are covered by the rear bumper unit 36 ​​against view from behind.

[0237] The pivot bearing unit 20 comprises, as shown in Figs. 6 to 9, a guide body 40 which is fixedly connected to the support plate 26 by a flange 42 and a guide sleeve 44 extending from the flange 42 away from the support plate 26, on which the pivot bearing body 14 is rotatably mounted.

[0238] For this purpose, the guide sleeve 44 comprises a cylindrical outer surface 46, against which the pivot bearing body 14 rests with a cylindrical inner surface 48 and thereby undergoes a rotational guidance about the pivot axis 22, so that the pivot bearing body 14 is rotatable relative to the guide body 40 such that the ball neck 10 can be pivoted from the working position A into the rest position R and vice versa. The guide body 40 also comprises an extension 41 extending through an opening 27 in the support plate 26, which has a receptacle following the extension 41 on a side opposite the flange 42.

[0239] 43 for a retaining ring 45 which can be fixed thereto, so that the guide body 40 is seated in a rotationally fixed manner in the support plate 26 by means of the extension 41 due to its non-rotationally symmetrical but radially varying outer contour 47 (Fig. 15) in the correspondingly shaped opening 27 by means of a positive fit and is fixed to the support plate 26 by means of the flange 45 and the retaining ring 43 which bear against opposite sides of the support plate 26.

[0240] The guide body 40 thus forms the vehicle-fixed pivot bearing for the pivot bearing body 14 through its fixed connection to the support plate 26 and the carrier 24.

[0241] To fix the pivot bearing body 14 in the working position A, the pivot bearing unit 20 is provided with a rotation blocking device designated as a whole by 50 (Fig. 7 to 14), which comprises an actuating body 52, a plurality of rotation blocking bodies 54 which can be acted upon by the actuating body 52, each of which is arranged in a guide receptacle 56 of the guide sleeve

[0242] 44 are movably guided in a guide direction 58 extending substantially radially to the pivot axis 22.

[0243] Preferably, at least the rotation-blocking bodies 54 and the guide receptacles 56 are arranged symmetrically to a geometric plane running perpendicular to the pivot axis 22 and intersecting the rotation-blocking bodies 54, which corresponds to the plane of the drawing in Figs. 7 to 14.

[0244] Furthermore, the rotation-blocking device 50 comprises working position receptacles 60A extending from the inner surface 48 of the pivot bearing body 14, in particular in the radial direction to the pivot axis 22, into the latter, with which the rotation-blocking bodies 54 can be brought into engagement in the working position A, wherein the working position receptacles 60A have wall surfaces which are increasingly spaced apart from one another in the radial direction to the pivot axis 22.

[0245] Furthermore, the rotation blocking device 50 comprises, in addition to or alternatively to the working position receptacles 60A, rest position receptacles 60R, which in the simplest case are designed in the same way as the working position receptacles 60A.

[0246] For example, if the rotation-blocking device 50, as shown in connection with Fig. 7 to Fig. 14 in the first embodiment, comprises a set of three rotation-blocking bodies 54a, 54b and 54c, the guide sleeve 44 has a corresponding set of three guide receptacles 56a, 56b and 56c, in which the rotation-blocking bodies 54a, 54b and 54c are guided displaceably in the guide direction 58 extending substantially radially to the pivot axis 22, and the pivot bearing body 14 is provided with a set of working position receptacles 60Aa, 60Ab and 60Ac, with which the rotation-blocking bodies 54a, 54b and 54c can be brought into engagement in the working position A (Fig. 7), and / or with a set of rest position receptacles 60Ra, 60Rb, 60Rc, with which the rotation-blocking bodies 52 can be engaged in the rest position R (Fig. 13).

[0247] For the appropriate movement and positioning of the rotation-blocking bodies 54 in the guide direction 58, the actuating body 52 is provided with a set of, for example, a total of three retraction receptacles 62a, 62b and 62c corresponding to the number of rotation-blocking bodies 54, and pressure surfaces 66a, 66b and 66c adjoining the respective retraction receptacles 62a, 62b, 62c in a circumferential direction 64, which are designed as wedge surfaces acting radially to the pivot axis 22, wherein the rotation-blocking bodies 54 can immerse themselves in the retraction receptacles 62a, 62b, 62c in their release position (Fig.8) that they no longer protrude beyond the outer surface 46 of the guide sleeve 44, and wherein the pressure surfaces 66a, 66b, 66c each extend from a radially inner initial region 68a, 68b and 68c directly adjoining the respective retraction receptacles 62, with increasing extent in the direction of rotation 64, increasingly radially outwards towards the pivot axis 22, up to a radially outer end region 70a, 70b and 70c and thus act as wedge surfaces on the rotation-blocking bodies 54 during a rotational movement of the actuating body 52 in order to move them into their rotation-blocking position.

[0248] Preferably, the pressure surfaces 66 extend as spiral or involute segments relative to the pivot axis 22.

[0249] In order to hold the rotation-blocking bodies 54 either in their rotation-blocking position by applying pressure to them with the pressure surfaces 66 between the initial region 68 and the end region 70 or to allow them to dip into the retraction receptacles 62 in the release position, the actuating body 52 is also rotatable about the pivot axis 22, in particular coaxially thereto, in such a way that either the set of retraction receptacles 62a, 62b and 62c faces the rotation-blocking bodies 54 and, as shown in Fig.8, in its inactive position or release position, it is possible, upon transition to the release position, to plunge into the retraction receptacles 62 in the radial direction towards the pivot axis 22 in order to give the respective rotation-blocking bodies 54 the opportunity to leave the working position receptacles 60A or the rest position receptacles 60R and to release the pivot bearing body 14 with regard to rotation about the pivot axis 22 relative to the guide body 40, so that the pivot bearing body 14 with the ball neck 10 is unhindered and freely rotatable relative to the guide sleeve 44, as shown in Fig. 8 and Fig. 14, wherein in this case the rotation-blocking bodies 54 do not extend beyond the outer circumferential surface 46 of the guide sleeve 44.

[0250] A rotation of the actuating body 52 with the rotation-blocking bodies 54 seated in the retraction receptacles 62 in a direction of rotation 72 opposite to the direction of rotation 64 causes the rotation-blocking bodies 54 to be moved out of the retraction receptacles 62 and initially to sit on the initial regions 68 of the pressure surfaces 66 in the active position or rotation-blocking position of the actuating body 52, but in the process, for example, already dip into the receptacles 60 and thus prevent the free rotation of the pivot bearing body 14 relative to the guide body 40 in their rotation-blocking position.

[0251] If the actuating body 52 is rotated further in the direction of rotation 72 opposite to the direction of rotation 64, areas of the pressure surfaces 66 lying radially outward relative to the pivot axis 22 act increasingly on the rotation-blocking bodies 54 and thus increasingly press the rotation-blocking bodies 54 in the working position A or the rest position R of the ball neck 10 into the working position receptacles 60Aa, 60Ab and 60Ac, Fig. 7, or into the rest position receptacles 60Ra, 60Rb and 60Rc, Fig. 13, in order to achieve a substantially play-free fixing of the pivot bearing body 14 relative to the guide body 40, in this case to the guide sleeve 44.

[0252] In the rotation-blocking position of the rotation-blocking bodies 54, the actuating body 52 is in its active position such that the rotation-blocking bodies 54, as shown in Fig. 7 and Fig. 13, sit approximately on central regions 76, which lie between the starting regions 68 and the end regions 70, of the pressure surfaces 66 and are acted upon by them.

[0253] In order to enable the actuating body 52 to optimally act upon each of the three rotation-locking bodies 54, it is provided that, in the active position, the actuating body 52 is centered according to the position of the rotation-locking bodies 54. In particular, the actuating body 52 is mounted in the guide sleeve 44 such that, due to the radial play, the actuating body 52 can center itself relatively according to the position of the rotation-locking bodies 54 within the guide body 40, which is determined by manufacturing tolerances. The self-centering of the actuating body 52 may deviate slightly from a coaxial arrangement with the geometric pivot axis 22.Due to the self-centering, the rotation blocking bodies 54a, 54b and 54c act in the respective guide direction 58a, 58b and 58c with approximately equal forces on the working position receptacles 60Aa, 60Ab and 60Ac or the rest position receptacles 60Ra, 60Rb and 60Rc, so that the reaction forces acting on the actuating body 52 are also approximately equal.

[0254] Preferably, the rotation-blocking bodies 54 are designed as balls, which thus bear on the one hand against the actuating body 52 and on the other hand also against the receptacles 60.

[0255] Thus, only a play-affected rotatable mounting of the actuating body 52 relative to the pivot axis 22 takes place, which is primarily relevant when the actuating body 52 holds the rotation-blocking bodies 54 in a release position in which the rotation-blocking bodies 54 are inserted into the retraction receptacles 62 of the actuating body 52.

[0256] In order to cause the actuating body 52 to always move in the direction of rotation 72 without external influence, whereby the rotation-blocking bodies 54 move in the direction of the rotation-blocking position, the actuating body 52 is acted upon by a torsion spring 114 (Fig. 6), which on the one hand acts on the actuating body 52 and on the other hand is supported radially outwardly on the guide body 40.

[0257] The torsion spring 114 also causes the actuating body 52 to press the rotation-blocking bodies 54 into the working position receptacles 60A or the rest position receptacles 60R under force, and thus the pivot bearing body 14 is fixed without play, wherein the freedom from play is maintained by further rotation of the actuating body 52 in the direction of rotation 72 even when the geometry of the working position receptacles 60A or the rest position receptacles 60R changes due to the loads during operation.The three guide receptacles 56, for example, and the rotation-blocking bodies 54 arranged therein, as well as the retraction receptacles 62 respectively assigned to these rotation-blocking bodies 54 with the pressure surfaces 66 adjoining them in the actuating body 52, each form three rotation-blocking units 80, and these are arranged around the pivot axis 22 at unequal angular distances Wab, Wbc, Wca (relative to the respective central axes Ma, Mb, Mc) relative to one another, whereby, with respect to the pivot axis 22 as the axis of rotation, a rotation-blocking configuration of the rotation-blocking units 80 only leads to a congruent arrangement of the rotation-blocking units 80 when the rotation-blocking configuration is rotated by 360°.

[0258] For example, the angular distance Wab = 120°, the angular distance Wbc = 137° and the angular distance Wca = 103°, which means that the deviation from equal angular distances is 17°.

[0259] However, in the case of, for example, three rotation-locking units, deviations from equal angular distances of up to 30° or more are also possible, so that, for example, angular distances of Wab = 120°, Wbc = 150° and Wca = 90° are possible.

[0260] Likewise, the working position receptacles 60A and / or the rest position receptacles 60R are each arranged relative to one another with respect to the pivot axis 22 in a receptacle configuration with the same angular spacing as the rotation-blocking units 80 relative to one another, which, with respect to the pivot axis 22, also only lead to a congruent arrangement of the respective receptacle configuration when rotated by 360°, so that in the working position A or the rest position R, this is congruent with the rotation-blocking configuration, so that in the working position A or the rest position R, a rotation-blocking body 54 of one of the rotation-blocking units 80 is opposite one of the working position receptacles 60A or one of the rest position receptacles 60R and can engage with it in the rotation-blocking position, as shown in Fig. 7 and Fig.13, whereby the pivot bearing body 14 is fixed in a rotationally fixed manner relative to the pivot bearing unit 20 (Fig. 7, Fig. 13).

[0261] However, if the actuating body 52 is moved into the release position in the working position A or the rest position R against the force of the torsion spring 114, as described below, each of the rotation-blocking bodies 54 of the respective rotation-blocking unit 80 has the possibility of immersing itself in the retraction receptacle 62 assigned to it and of leaving the respective working position receptacle 60A or rest position receptacle R, so that the pivot bearing body 14 can be pivoted out about the pivot axis 22 to the working position A or the rest position R (Fig. 8, Fig. 14).

[0262] As soon as the pivot bearing body 14 has left the working position A and / or the rest position R (Fig. 9), the entirety of the rotation blocking units 80 arranged in the rotation-blocking configuration relative to the pivot axis 22 no longer has the possibility of engaging with the entirety of the working position receptacles 60A and / or the rest position receptacles 60R arranged in the respective receptacle configuration in all pivot positions between the working position A and / or the rest position R, so that when the actuating body 54 is acted upon in the direction of rotation 72, the entirety of the rotation-blocking bodies 54 seated in the retraction receptacles 62 can no longer engage with the entirety of the working position receptacles 60A and / or the rest position receptacles 60R, since the rotation-blocking bodies 54 are indeed acted upon by the actuating body 52 acted upon by the torsion spring 114 in the direction of rotation 72,in particular by the curved base surfaces of the retraction receptacles 62 running obliquely to the guide direction 58, in the direction of the pivot bearing body 14, however, in each of the rotational positions of the pivot bearing body 14 outside the working position A, the entirety of the rotation-blocking bodies 54 is never opposed by a receptacle from the entirety of the working position receptacles 60A and / or the rest position receptacles 60R and thus at least one of the rotation-blocking bodies 54 is always blocked by one of the blocking surfaces 90 running between the working position receptacles 60A and / or rest position receptacles 60R, formed in the simplest case by the cylindrical inner surface 48 of the pivot bearing body 14, and thereby prevents a rotation of the actuating body 52 in the direction of rotation 72 caused by the torsion spring 114,so that the actuating body 52 is held in the release position in all pivot positions of the pivot bearing body 14 outside the working position A and / or the rest position R even when the torsion spring 114 acts in the direction of rotation 72 and consequently can only return to the rotation-blocking position when the working position A is reached.

[0263] Preferably, the deviation of the rotation-blocking configuration of the rotation-blocking unit 80 and the receiving configuration of the receptacles 60 from a symmetrical design is so great that when one of the rotation-blocking units 80 is opposite one of the working position receptacles 60A or the rest position receptacles 60R, so that the rotation-blocking body 54 could engage with this working position receptacle 60A and / or the rest position receptacle 60R, at least one, even better at least two, rotation-blocking units 80 are offset in the direction of rotation relative to the nearest receptacle of the working position receptacle 60A and / or the rest position receptacle 60R to such an extent that a contact point of the rotation-blocking body 54 assigned to this rotation-blocking unit 80 already lies on one of the blocking surfaces 90 and cannot come to rest in the area of ​​one of the receptacles 60, so that a reliable blocking of the actuating body 52, in particular whenwhen the actuating body 52 is acted upon by the torsion spring 114 in the direction of rotation 72, is ensured by the blocking surfaces 90 acting in the release position.

[0264] If the actuating body 52 is acted upon with a direction of rotation 64 opposite to the action of the torsion spring 114 and is rotated to its maximum, the rotation blocking bodies 54 are located in all pivot positions of the pivot bearing body 14 with play between the respective blocking surface 90 and the retraction receptacles 62. However, if the action of the torsion spring 114 dominates in the direction of rotation 72, conditions such as those shown in Figs. 9 to 12 also exist when pivoting between the working position A and / or the rest position R in the respective pivot positions of the pivot bearing body 14.

[0265] Fig. 9 to 12 show that the actuating body 52 is held in the release position in each of the pivoting positions of the pivot bearing body 14 by at least one, preferably two, rotation-blocking bodies 54, which bear against one of the blocking surfaces 90, and prevent one of the rotation-blocking bodies 54, for example the rotation-blocking body 54b in Fig. 10 or the rotation-blocking body 54a in Fig. 11, from engaging in the receptacle 60 which is aligned with it.

[0266] In any case, the conditions according to Fig. 7 to 14 are present when pivoting between the rest position R and / or the working position A, wherein due to the contact of the rotation-blocking bodies 54 on the blocking surfaces 90 according to Fig. 9 to 12 when pivoting between the rest position R and the working position A, the rotation-blocking bodies 54 slide along the blocking surfaces 90 with little noise development and slide from the blocking surfaces 90 directly and in particular continuously over the opening edges 92 of the working position receptacles 60A and / or the rest position receptacles 60R adjoining these into the working position receptacles 60A and / or the rest position receptacles 60R and move into the rotation-blocking position according to Fig. 7 or Fig. 13.

[0267] The guide sleeve 44 preferably extends with a section forming a receptacle 102 for the actuating body 52 between the flange 42 and a flange 104 which closes the guide sleeve 44 and extends radially towards the pivot axis 22, which flange 104 is preferably formed integrally with the guide sleeve 44 and delimits the receptacle 102 for the actuating body 52, so that the actuating body 52 is guided radially to the pivot axis 22 through the receptacle 102 of the guide sleeve 44 and is guided axially in the direction of the pivot axis 22 by bearing against an inner side 108 of the flange 104.

[0268] The flange 104 further comprises a receptacle 106 coaxial with the pivot axis 22, into which an insert 110 is inserted, in particular screwed, through which a shaft 100 passes, which insert is seated in the receptacle 106 and guides the shaft 100 rotatably relative to the guide sleeve 44.

[0269] On a side of the receptacle 102 for the actuating body 52 opposite the flange 104, the guide sleeve 44 forms, for example with a section passing through the flange 42, a torsion spring receptacle 112 in which the torsion spring 114 is arranged adjacent to the actuating body 52, which torsion spring 114 is fixed at one end in the torsion spring receptacle 112 and is connected at one end to a drive sleeve 122 which is coupled in a rotationally fixed manner to the actuating body 52.

[0270] For this purpose, the drive sleeve 122, as shown in Figs. 6, 7 and 16, is provided, for example, with extensions 124 which engage in corresponding recesses 126 in the actuating body 52 to produce a positive connection.

[0271] Because the torsion spring 114 acts on the drive sleeve 122, which is coupled in a rotationally fixed manner to the actuating body 52, the action of the torsion spring 114 on the drive sleeve 122 drives the actuating body 52 in the direction of rotation 72, so that the actuating body 52, with unhindered action of the torsion spring 114 on the drive sleeve 122, always acts on the actuating body 52 in the direction of rotation 72, so that the actuating body 52 has the tendency to move the rotation-blocking bodies 54 radially outwards away from the pivot axis 22 in the guide direction 58, with the blocking surfaces 90 in all intended pivot positions of the pivot bearing body 14, with the exception of the working position A and the rest position R.is prevented and consequently only in the working position A and the rest position R the rotation blocking bodies 54 are pressed into the working position receptacles A and the rest position receptacles R and thus the pivot bearing body 14 is fixed relative to the guide sleeve 44 in a rotationally fixed and in particular play-free manner.

[0272] In order to be able to move the rotation blocking body 54 into the release position, an action on the actuating body 52 opposite to the direction of rotation 72 and thus also opposite to the action of the torsion spring 114 is required.

[0273] For this purpose, the drive sleeve 122 can be driven by means of a planetary gear 130 designated as a whole by 130 (Fig. 6), which is arranged in a gear receptacle 132 of the guide sleeve 44, in particular coaxially to the pivot axis 22, which is arranged, for example, partially within the opening 27 of the carrier plate 26 and preferably extends away from the opening 27 of the carrier plate 26 on a side opposite the flange 42.

[0274] The planetary gear 130 (Fig. 15) in turn comprises a ring gear 142, which is guided in the gear receptacle 132 and is provided with an internal toothing 144, with which planet gears 146 engage with their external toothing 148.

[0275] The planetary gears 146 are rotatably held on a planetary gear carrier 152, which in turn is connected in a rotationally fixed manner to the stationary shaft 100.

[0276] Furthermore, as shown in Fig. 16, the ring gear 142 comprises a flange body 154 located between the planetary gear carrier 152 and the torsion spring 114, which also extends in the direction of the shaft 100, encloses it, but is rotatable relative to it and forms an output of the planetary gear 130 for actuating the rotation-blocking device 50. As shown in Fig.16, the flange body 154 has circular arc-shaped drive slots 156a, 156b arranged circumferentially around the pivot axis 22, which interact with drive fingers 158a, 158b of the drive sleeve 122 engaging therein, and which are designed such that the difference between the angular range around the pivot axis 22 over which the drive slots 156 extend and the angular range around the pivot axis 22 over which the drive fingers 158 extend allows free movement of the drive sleeve 122 relative to the ring gear 142, which will be explained in more detail below.

[0277] The planet gears 146 are furthermore in engagement with their external toothing 148 with an external toothing 164 of a sun gear 162 of the planetary gear 130, which is seated on a drive shaft designated as a whole by 166, which is arranged coaxially to the pivot axis 22 and is freely rotatable relative to the pivot drive shaft 100, for example by means of an end-side shaft stub 168 which engages in a front-side bore 172 of the standing shaft 100, but is mounted coaxially thereto.

[0278] The drive shaft 166 carries, at a distance from the planetary gear 130, a drive gear 174, for example a bevel gear, which is driven by an output gear of a motor drive unit 182, which comprises, for example, on the one hand a drive motor, preferably an electric motor, and on the other hand a reduction gear for driving the drive gear.

[0279] The drive unit 182 is held, for example, on a cover body 184 which, starting from the carrier plate 126, engages over the drive shaft 166 with the drive gear 174 and the driven gear meshing with it and also supports the drive shaft 166 on a side facing away from the shaft stub 168.

[0280] Thus, the planetary gear 130 and the drive unit 182 form, for example, an actuating device 180 for the rotation-locking device 50. The standing shaft 100, which is non-rotatably coupled to the planet gear carrier 152, is non-rotatably connected to the flange 104 of the guide body 40.

[0281] An end flange 198 of the pivot bearing body 14 engages over the flange 104 of the guide body 40 in the outer region 200 and extends up to a guide projection 202 of the flange 104, wherein the end flange 198, for example with a radially inner cylindrical surface 204, engages around an outer cylindrical surface 206 of the guide projection 202 and, for example, rests against this and is thus also additionally guided on the guide projection 202 coaxially to the pivot axis 22.

[0282] In addition, a thread 212 extends into the receptacle 106 of the guide projection 202, in which the insert 110 is fixed, in particular screwed, which thread partially overlaps the end flange 198 in a radially inner region with an outer flange 214, so that the end flange 198 of the pivot bearing body 14 is guided axially immovably between the flange 104 and the outer flange 214 of the insert 110 and thus axially immovably relative to the guide body 40.

[0283] Furthermore, a cover 222 is mounted on the end flange 198 in a rotationally fixed manner, so that the cover 222 forms a unit with the pivot bearing body 14 which is rotatable about the pivot axis 22 (Fig. 17).

[0284] The cover 222 sits on the end flange 198 and is fixed thereto in a rotationally fixed manner.

[0285] In the solution described above, a set of working position receptacles 60A is provided for the rotationally fixed fixing of the pivot bearing body 14 in the working position A, as well as a set of rest position receptacles 60R for the rotationally fixed fixing of the pivot bearing body 14 in the rest position R. In order to reduce the noise development during the transition of the rotation blocking body 54 from the release position to the rotation blocking position while moving in the guide direction 58 in a trailer coupling with a rotation blocking device 50, as described above, a first embodiment of a trailer coupling according to the invention, as shown in Fig.20, a first embodiment of a trailer coupling according to the invention provides a delay unit 300 which is designed such that it delays a movement of the actuating body 52 in the direction of rotation 72, in particular when the initial regions 68 of the pressure surfaces 66 already begin to act on the rotation-blocking bodies 54, in order to reduce the speed with which the rotation-blocking bodies 54 are moved in the direction of the working position receptacles 60A or the rest position receptacles 60R.

[0286] 20 and 21, in the first exemplary embodiment, the actuating body 52 is provided with an annular extension 302 extending in the direction of the flange 104, which engages in an annular groove 304 provided in the flange 104 of the guide body 40, wherein the annular extension 302 and the annular groove 304 have annular surfaces 306 and 308 facing one another and arranged coaxially with the pivot axis 22, between which a rotation delay ring 310 is arranged, which serves to delay the rotational movement of the actuating body 52 in order to reduce the speed with which the rotation-blocking bodies 54 move in the guide direction 58 into the working position receptacles 60A or the rest position receptacles 60R.

[0287] In this case, for example, as shown in Fig. 22, the rotation delay ring 310 is designed such that it has two pressure legs 312 and 314 which run approximately parallel to one another and which face the annular surfaces 306 and 308 with their outer sides 316 and 318, respectively, and are connected to one another via a middle leg 322, the pressure legs 312, 314 and the middle leg 322 being formed from an elastic material which ensures that the pressure legs 312 and 314 are spring-elastically biased with their outer sides 316 and 318 in the direction of the annular surface 306 and 308, respectively, in order to, in the simplest case, create sufficiently great friction between the outer side 316 and the annular surface 306 and 308, respectively.the outer side 318 and the annular surface 308, which counteracts the torque exerted by the torsion spring 114 on the rotation blocking body 152 and acting in the direction of rotation 72 and thus delays the rotational speed of the rotational movement of the actuating body 52 in the direction of rotation 72.

[0288] In a variant of this solution, however, it is also possible to arrange one of the outer sides 316 or 318 firmly on the respective annular surface 306 or 308 and to allow only the other outer side 318 or 316 to act in a frictional manner on the respective annular surface 308 or 306.

[0289] Preferably, the outer sides 316 and 318 can be provided with coatings 326 and 328 forming friction surfaces 332, 334, by the selection of which the deceleration of the rotational movement in the direction of rotation 72 can be predetermined.

[0290] It is particularly advantageous if the friction surfaces 332, 334 of the coatings 326 and 328 are designed such that they develop an increased friction effect during a rotational movement in the direction of rotation 72 and a reduced friction effect in a direction of rotation opposite to the direction of rotation 72 in order to facilitate the transition of the actuating body 52 from the rotation-blocking position to the release position.

[0291] In a first variant of the first embodiment of a delay unit according to the invention, shown in Fig. 23, the delay unit 300' is provided with a rotation delay ring 310', which has a support body 336 which bears against the ring surface 306, for example in a rotationally fixed manner, and a friction body 338 which bears against the ring surface 308, wherein, for example, the support body 336 is designed to be radially elastic and presses the friction body 338 against the ring surface 308 and also preferably bears against the ring surface 306 with a high friction force, while the friction body 338 bears against the ring surface 308 and is movable relative to the ring surface 308 with a predeterminable friction coefficient.

[0292] In a second variant of the first exemplary embodiment of the deceleration unit 300" according to the invention, shown in Figs. 24 to 26, the rotation deceleration ring 310", which acts between the annular surface 306 and the annular surface 308, is formed from a base body 342 made of elastic material with a desired coefficient of friction and has support bodies 344 arranged in the base body 342 at a distance from one another in the circumferential direction, which are oriented obliquely relative to radial directions 346 to the pivot axis in order to ensure that the base body 342, during a rotational movement in the direction of rotation 72, bears with its outer sides 316" and 318" against the annular surfaces 306 and 308 with greater force and thus generates a greater frictional force than during a rotational movement opposite to the direction of rotation 72.

[0293] As a result, the friction effect during a rotational movement of the actuating body 52 in the direction of rotation 72, ie when moving the rotation-blocking bodies 54 into the working position or rest position receptacles 60, is greater than during a rotational movement opposite to the direction of rotation 72, ie when releasing the rotation block and transitioning into the release position.

[0294] Alternatively or additionally, a second exemplary embodiment of a trailer coupling according to the invention provides a second exemplary embodiment of a deceleration unit 400, which is arranged in the section of the guide sleeve 44 of the guide body 40 that surrounds the actuating body 52 and interacts with a peripheral side of the actuating body 52, in particular with a pressure surface 66 and / or with a peripheral region 71 adjoining one of the pressure surfaces 66, wherein the deceleration unit 400 comprises a friction body 402, which is arranged in a guide sleeve 404, for example forming a guide receptacle, and can be acted upon in the direction of the actuating body 52 by a spring-elastic body 406, which is also seated in the guide sleeve 404 and is formed, for example, by a spiral spring or a plate spring assembly, wherein the friction body 402 is arranged such that, as shown in Fig.28, becomes effective when the initial area 68 of the respective pressure surface 66 begins to act on the respective rotation-blocking body 54 (Fig. 27 to Fig. 29) and to move it into the rotation-blocking position.

[0295] This can be achieved, for example, in that the friction body 402 protrudes from the guide sleeve 44 only so far in the direction of the actuating body 52 that it only becomes effective when the end region 70 of the pressure surface 66 is opposite it, or even only becomes effective when the circumferential region 71 following the pressure surface 66 is opposite it, which in particular forms a circular-cylindrical circumferential region of the actuating body 52.

[0296] The end region 70 thus forms a deceleration start region 405 of a friction surface 403 and the circular cylindrical peripheral region 71 forms a deceleration end region 407 of the friction surface 403, along which the deceleration unit 400 moves during the rotational movement in the direction of rotation 72 of the actuating body 52 when the rotation-blocking bodies 54 are to be moved from the release position into the rotation-blocking position.

[0297] In particular, when the friction body 402 interacts with the peripheral region 71, the peripheral region 71 can be provided with a friction-promoting surface structure or surface coating, which cannot be realized in the region of the pressure surface 66.

[0298] In this case, only one deceleration unit 400 can be assigned to one of the rotation-blocking bodies 54; due to the mounting of the actuating body 52 with play relative to the pivot axis 22, it is also possible to provide a deceleration unit 400 acting for each circumferential region 71 following a pressure surface 66. These deceleration units 400 or deceleration units 400 allow the rotational movement of the actuating body 52 in the direction of rotation 72 and thus the movement of the respective rotation-blocking body 54 in the guide direction 58 to engage, for example, the working position receptacles 60A or the rest position receptacles 60R immediately before impact on a receptacle base 61A or 61R, and thus to reduce the impact noise of the respective actuating body 54 on the respective receptacle base 61A or 61R.

[0299] In a first variant of the second embodiment - shown in Figs. 30 to 32 - a delay unit 400' is arranged in the actuating body 52, the friction body 402' of which projects beyond a retraction receptacle 62 in the circumferential region 71 between the respective pressure surface 66 and the retraction receptacle 62 following thereon in the opposite direction to the rotation-blocking body 54 moving into the rotation-blocking position, and cooperates with a friction surface 403' provided in the guide sleeve 44 of the guide body 40.

[0300] Preferably, the friction surface 403' extends in such a way that its radial distance from the pivot axis 22 forming a rotational axis of the actuating body 52 in the direction of the rotational axis 72, starting from a deceleration start region 405' to a deceleration end region 407', becomes smaller, so that the distance of the region of the friction surface 403' acted upon by the friction body 402' from the deceleration unit 400', in particular from its guide sleeve 404' forming, for example, the guide receptacle, becomes smaller when the actuating body 52 rotates in the direction of rotation 72 and thereby, through increased compression of the spring-elastic body 406' arranged in the guide sleeve 404', the friction force between the friction body 402' and the friction surface 403' when the actuating body 52 rotates in the direction of rotation 72 and the movement of the deceleration unit 400' along the friction surface 403' increases from the delay start area 405' to a delay end area 407',and consequently, the braking effect of the deceleration unit 400' on the actuating body 52 also increases, and in particular when the respective pressure surface 66 begins to act on the respective rotation-blocking body 54 and is at its maximum shortly before the rotation-blocking body 54 fully engages the respective rotation-blocking receptacle 62.

[0301] In particular, the deceleration end region 407' runs along a circular arc line around the rotational axis 22 of the actuating body 52 in order to prevent the deceleration unit 400' from generating a permanent torque opposite to the direction of rotation 72 in the rotation-blocking position.

[0302] In a second variant of the second embodiment, shown in Figs. 33 to 37, the delay unit 400" is arranged in the flange 104 encompassed by the guide body 40, which flange delimits the receptacle 102 for the actuating body 52 and is in particular formed integrally with the guide sleeve 44 of the guide body 40.

[0303] The guide sleeve 404" forming the guide receptacle is arranged in the flange 104 such that the friction body 402" projects out of the guide sleeve 404" in the direction of the actuating body 52 and interacts with a friction surface 403" which is arranged on a side of the actuating body 52 facing the flange 104 and is rotatable with the actuating body 52.

[0304] Furthermore, the friction body 402" is acted upon by the spring-elastic body 406" seated in the guide sleeve 404", which is supported, for example, by the flange 104, as shown in Figs. 33 and 34, or can also be supported on the end flange 198 of the pivot bearing body 14 adjacent to the flange 104, as shown in Fig. 35 in a modification of the second variant of the second embodiment.

[0305] The friction surface 403" formed on the actuating body 52 extends in an arc around the axis 22 from the deceleration start region 405" to the deceleration end region 407", as shown in Fig. 36 and 37 and runs from the deceleration start region 405" to the deceleration end region 407" with increasingly smaller distances from the guide sleeve 404", which forms, for example, the guide receptacle, so that upon movement of the friction body 402" from the deceleration start region 405" shown in Fig. 36 and Fig. 37 into the deceleration end region 407" shown in Fig. 38 and Fig.39, the spring-elastic body 406" is increasingly compressed and thus acts on the friction body 402" with a greater force in the deceleration end region 407" than in the deceleration start region 405", so that when the rotation-blocking body 52 moves in the direction of rotation 72, the friction force and thus also the braking force acting opposite to the direction of rotation 72 increases and thus brakes the movement in the direction of rotation 72.

[0306] Preferably, the entire deceleration region 407" acted upon by the friction body 402" no longer extends at an incline, but rather at a constant distance from the guide receptacle 404", so that in this position of the actuating body 52, the friction body 402" in cooperation with the deceleration end region 407" does not generate a torque opposite to the direction of rotation 72, which would counteract the locking force acting on the rotation-blocking bodies 54 by the actuating body 52.

[0307] In a third variant of the second embodiment, shown in Figs. 40 and 41, the delay unit 400"' is arranged in the actuating body 52 and the friction surface 403"' is arranged on the inner side 108 of the flange 104 of the guide body 40 facing the actuating body 52.

[0308] In the actuating body 52, the guide receptacle forming the guide sleeve 404'" with the friction body 402'" guided therein and the spring-elastic body 406" acting on the friction body 402" are thus arranged.

[0309] When the actuating body 52 moves in the direction of rotation 72 in order to transfer the rotation-blocking bodies 54 from the release position to the rotation-blocking position, the friction body 402''' moves from the deceleration start region 405''' to the deceleration end region 407''' and causes an increasing deceleration of the rotational movement in the direction of rotation 72 in order to reduce the noise development when the rotation-blocking bodies 54 finally insert into the respective receptacles 60. In this variant, too, the friction surface 403''' has an increasingly smaller distance from the guide receptacle 404''' as it extends from the deceleration start region 405''' to the deceleration end region 407''', thus increasing the frictional force between the friction body 402''' and the friction surface 403''' in the area acted upon by the friction body 402'''.

[0310] Furthermore, in this variant, the deceleration end region 407'" also runs parallel to the guide receptacle 404'" in order to avoid receiving a torque acting opposite to the direction of rotation 72 in the locking position of the actuating body 52.

[0311] Also in the first to third variants of the second embodiment, the respective deceleration unit 400', 400" and 400'" with the corresponding friction surface 403', 403" and 403'" can be assigned not only to one of the rotation-blocking bodies 54, but due to the mounting of the actuating body 52 with play relative to the pivot axis 22, it is also possible to assign several of the deceleration units 400', 400" 400'", in particular to each of the rotation-blocking bodies 54 or its pressure surfaces 66 a deceleration unit 400', 400", 400'" with the friction surface 403', 403", 403'" cooperating therewith.

[0312] Alternatively or in addition to the previously described embodiments of a deceleration unit according to the invention, a third embodiment of a trailer coupling according to the invention provides a third embodiment of a deceleration unit 500 (Fig. 42 and Fig. 43), which is provided in the pivot bearing body 14 and is assigned, for example, to one of the working position receptacles 60A, for example, the working position receptacle 60Aa. The deceleration unit 500 comprises a deceleration body 502 assigned to the working position receptacle base 61Aa, which, in its inactive position, projects beyond the working position receptacle base 61Aa and is acted upon by a spring-elastic element 504.

[0313] In this case, both the delay body 502 and the spring-elastic element 504 are arranged in a guide body 506, which is arranged in a bore 508 in the pivot bearing body 14 which is assigned to the working position receptacle 60Aa and which is provided, for example, with an internal thread, and thus opens up the possibility of receiving the guide body 506 which is provided, for example, with an external thread, whereby the guide body 506 together with the delay body 502 arranged therein and the associated spring-elastic element 504 can be moved in the direction of the working position receptacle base 61Aa and can thus be adjusted such that the delay body 502, in its still ineffective initial position in which there is still no action by the associated rotation-blocking body 54, projects more or less far beyond the working position receptacle base 61Aa into the working position receptacle 60Aa.

[0314] Depending on how far the deceleration body 502 projects beyond the working position receiving base 61Aa into the working position receiving base 60Aa, the deceleration effect exerted by the deceleration body 502 on the rotation blocking body 54 when moving in the guide direction 58 in the direction of the working position receiving base 61Aa is adjustable and thus the deceleration effect of the deceleration unit 500 is also adjustable from an outer side of the pivot bearing body 14, in particular if the guide body 506 has a guide body head 512 which projects beyond an outer circumference of the pivot bearing body 14 and has, for example, a receptacle 514 for an adjustment tool, for example a screwdriver.

[0315] With a deceleration unit 500 adjusted in this way, the rotation-blocking body 54a reaches the deceleration body 502 before striking the working position receiving base 61Aa, which decelerates the movement of the rotation-blocking body 54a by deformation of the spring-elastic element 504 and allows it to strike the working position receiving base 61Aa at a reduced speed.

[0316] Although the delay unit 500 is only assigned to one working position receptacle 60A, for example the working position receptacle 60Aa, it also simultaneously has a delaying effect on the remaining rotation-blocking bodies 54 entering the respective working position receptacles 60Ab and 60Ac, since the rotation-blocking body 54a, which is delayed by the delay unit 500 before hitting the working position receptacle base 61Aa, simultaneously exerts a reaction on the actuating body 52, so that the latter is also delayed in its rotational movement in the direction of rotation 72 and thus also moves the remaining rotation-blocking bodies 54b and 54c with a delay in the direction of the respective working position receptacle base 61Ab and 61Ac, thus leading overall to a reduction in noise.

[0317] In the same way, one of the rest position receptacles 60R can also be additionally or alternatively assigned such a delay unit 500 according to the invention in order to achieve the desired noise damping even when the rotation blocking bodies 54 enter the respective rest position receptacles 60R.

[0318] In a first variant of the third embodiment, shown in Fig. 44, the deceleration body 502 is not supported by a spring-elastic element 504, but by a fluid braking element 505 made of a shear-thickening fluid in an elastic sheath 507, which has a shear rate-dependent dilatancy, thus having a high resistance to relative flow in the event of a sudden action of the rotation-blocking body 54 on the deceleration body 502 and thus decelerates the movement of the rotation-blocking body in the direction of movement 48 and then, in the decelerated state, due to the then occurring lower resistance to relative flow with expansion of the elastic sheath 507, allows the transition into the rotation-blocking position, as shown in Fig. 45.

[0319] A further detailed description of the trailer coupling according to the invention, in particular the individual movement sequences, is given in the

[0320] DE 10 2020 11 468, so that in this regard, reference is made in full to the disclosure in this application.

Claims

PATENT CLAIMS Trailer coupling, comprising a ball neck (10) movable between a working position (A) and a rest position (R), with a pivot bearing body (14) arranged at a first end and a coupling ball (18) arranged at a second end, a pivot bearing unit (20) arranged fixedly to the vehicle, by means of which the pivot bearing body (14) is pivotally received for performing a pivoting movement about a pivot axis (22) between the working position (A) and the rest position (R), and a rotation blocking device (50) acting between the pivot bearing unit (20) and the pivot bearing body (14), with on the one hand at least one rotation blocking unit (80) which has a rotation blocking body (54) which is movably guided in a guide direction (58) by means of a guide receptacle (56) of a guide body (40) and which is guided in the guide direction (58) by aon an actuating body (52) is movable, and on the other hand with at least one working position receptacle (60A) and / or at least one rest position receptacle (60R), wherein by moving the actuating body (52) in an actuating direction (72) the rotation-blocking body (54) of the rotation-blocking units (80) is movable and loadable in the guide direction (58), and wherein the rotation-blocking body (54) of the rotation-blocking units (80) in the working position (A) and / or the rest position (R) is brought into a rotation-blocking position by moving it in the guide direction (58), and in this position the rotation-blocking body (54) engages with a respective working position receptacle (60A) or rest position receptacle (60R) in order to block a pivoting movement of the pivot bearing body (14) about the pivot axis (22) relative to the guide body (40), and wherein the rotation-blocking body (54) can be brought into a release position and in, this is disengaged from the working position receptacle (60) and / or the rest position receptacle (60R) and releases the pivoting movement of the pivot bearing body (14), characterized in that the rotation-blocking device (50) is assigned at least one delay unit (300, 400, 500), which, at least when the working position (A) and / or the rest position (R) is reached, delays a transition of the rotation-blocking device (50) into the rotation-blocking position caused by an action on the rotation-blocking device (50). Trailer coupling according to claim 1, characterized in that the at least one delay unit (300, 400, 500) acts on the rotation-blocking device (50). Trailer coupling according to claim 1 or 2, characterized in that the at least one delay unit (300, 400, 500) delays the transition of the rotation-blocking unit (80) into the rotation-blocking position.Trailer coupling according to one of the preceding claims, characterized in that the at least one delay unit (300, 400, 500) acts on one or more elements of the rotation-locking device (50). Trailer coupling according to claims 2 to 4, characterized in that the at least one delay unit (300, 400, 500) acts directly on one of the elements of the rotation-locking device (50). Trailer coupling according to one of the preceding claims, characterized in that the at least one delay unit (300, 400, 500) delays the movement of the rotation-locking body (54) into the rotation-locking position. Trailer coupling according to one of the preceding claims, characterized in that the at least one delay unit (300, 400, 500) delays the movement of the actuating body (52) into the rotation-locking position. Trailer coupling according to claim 7, characterized in that the at least one delay unit (300, 400) acts between the guide body (44) and the actuating body (52). Trailer coupling according to claim 7 or 8, characterized in that the at least one delay unit (300, 400', 400"') is arranged on the actuating body (52). Trailer coupling according to one of claims 7 to 9, characterized in that the at least one delay unit (300, 400, 400") is arranged on the guide body (44). Trailer coupling according to one of the preceding claims, characterized in that the at least one deceleration unit (300, 400, 500) has a spring-elastic element (312, 314, 322, 336, 406, 504).Trailer coupling according to one of claims 7 to 11, characterized in that the spring-elastic element (312, 314, 322, 336, 406) forms at least one friction surface (316, 318, 342) or acts on a friction body (326, 328, 338, 402, 402', 402", 402'"). Trailer coupling according to one of claims 7 to 12, characterized in that the at least one deceleration unit (300) comprises a movement deceleration body (310) which is effective between a surface (302) of the actuating body (52) and a surface of the guide body (40) facing this surface. Trailer coupling according to claim 13, characterized in that the movement-decelerating body (310) has a different friction effect depending on the direction of movement. Trailer coupling according to one of claims 7 to 12, characterized in that the at least one deceleration unit (400) is arranged in a defined position on the guide body (40) or the actuating body (52) and, proceeding therefrom, acts in a decelerating manner on the actuating body (52) or the guide body (40). Trailer coupling according to claim 15, characterized in that the deceleration unit (400) is provided with a friction body (402) acted upon by a spring-elastic body (406), which acts on the actuating body (52) or the guide body (40).Trailer coupling according to claim 15 or 16, characterized in that the deceleration unit (400, 400', 400", 400'") arranged on the guide body (40) or the actuating body (52) acts with the friction body (402, 402', 402", 402'") on a friction surface (403, 403', 403", 403'") which is arranged on the actuating body (52) or the guide body (40). Trailer coupling according to claim 17, characterized in that the friction surface (403, 403', 403", 403'") extends over an angular range around the axis of rotation (22) of the actuating body (52). Trailer coupling according to claim 17 or 18, characterized in that the friction surface (403, 403', 403", 403'") extends from a deceleration start region (405, 405', 405", 405'") to a deceleration end region (407, 407', 407", 407'"). Trailer coupling according to one of claims 17 to 19, characterized in that the friction surface (403, 403', 403", 403"') extends at a varying distance relative to a guide receptacle (404, 404', 404", 404'") of the deceleration unit (400, 400', 400", 400'") during a rotational movement of the actuating body (52) relative to the guide body (40). Trailer coupling according to one of claims 17 to 20, characterized in that when the friction body (402, 402', 402", 402'") acts on the deceleration end region (407, 407', 407", 407'"), the spring-elastic body (406, 406', 406", 406'") acts on the friction body (402, 402', 402", 402'") with a greater force than when the friction body (402, 402', 402", 402'") acts on the deceleration start region (405, 405', 405", 405'").Trailer coupling according to claim 16, characterized in that the friction body (402) acts circumferentially on the actuating body (52), in particular on a circumferentially arranged friction surface (403, 403', 403", 403'"). Trailer coupling according to claim 22, characterized in that the friction body (402) acts on a pressure surface (66) acting on a rotation-blocking body (54) for acting on the rotation-blocking body (54). Trailer coupling according to claim 22 or 23, characterized in that the friction body (402) acts on a circumferential region (71) of the actuating body (52) adjoining a pressure surface (66) for acting on a rotation-blocking body (54). Trailer coupling according to one of claims 15 to 21, characterized in that the friction body (402) acts on the front side of the actuating body (52), in particular on a friction surface (403') arranged on the front side thereof. Trailer coupling according to one of claims 15 to 21, characterized in that the friction body (402) acts on a wall surface of a receptacle (102) provided in the guide body (40) for the actuating body (52), in particular on a friction surface (403", 403"') arranged on the receptacle (102). Trailer coupling according to one of the preceding claims, characterized in that the at least one delay unit (500) acts on a rotation-blocking body (54) upon reaching the working position (A) and / or the rest position (R) and delays its movement in the working position receptacle (60A) or rest position receptacle (60R).Trailer coupling according to claim 20, characterized in that the delay unit (500) is assigned to at least one of the working position receptacles (60A) and the rest position receptacles (60R). Trailer coupling according to claim 28, characterized in that the delay unit (500) counteracts, in a delaying manner, an impact of the rotation-blocking body (54) on a receptacle base (61A, 61R) of the working position receptacle (60A) and / or the rest position receptacle (60R). Trailer coupling according to claim 29, characterized in that the delay unit (500) comprises a spring-elastic element (504) which counteracts, in a delaying manner, the movement of the rotation-blocking body (54) in the direction of the respective receptacle base (61). Trailer coupling according to claim 29, characterized in that the deceleration unit (500') comprises a fluid braking element (505) made of a shear-thickening fluid. Trailer coupling according to claim 30 or 31, characterized in that the deceleration unit (500) is held and supported on a component (14) of the pivot bearing unit (20) that carries the receptacle (60A, 60R). Trailer coupling according to one of claims 27 to 32, characterized in that the spring-elastic element (504) acts via a deceleration body (502) on the rotation-blocking body (54) entering the receptacle (60A, 60R). Trailer coupling according to one of claims 27 to 33, characterized in that the deceleration unit (500) is adjustably positionable relative to the receptacle (60A, 60R).Trailer coupling according to claim 34, characterized in that the deceleration unit (500) has a guide body (506) which accommodates the resilient element (504) and, if applicable, the deceleration body (502). Trailer coupling according to claim 35, characterized in that the guide body (506) is held in an adjustably positionable manner on the component (14) carrying the receptacle (60A, 60R). Trailer coupling according to one of the preceding claims, characterized in that blocking surfaces (90) extend between the working position receptacles (60A) and / or the rest position receptacles (60R), against which blocking surfaces the rotation-blocking bodies (54) can be placed and from which the working position receptacles (60A) extend. and / or the rest position receptacles (60R) extend such that the rotation-blocking units (80) and the working position receptacles (60A) and / or the rest position receptacles (60R) are arranged at angular intervals (W) from one another around the pivot axis (22) such that in all intended pivot positions of the pivot bearing body (14), except for the working position (A) and / or the rest position (R), at least one of the rotation-blocking units (80) is opposite one of the blocking surfaces (90) and thus these blocking surfaces (90), in particular when a force is applied to the actuating body (52) in the direction of the actuation direction (72), blocks a movement of the actuating body (52) in the actuation direction (72) and consequently also a force-loaded engagement of the rotation-blocking bodies (54) of each of the rotation-blocking units (80) in one of the working position receptacles (60A) or the rest position receptacles (60R). Trailer coupling according to one of the preceding claims,characterized in that the rotation-blocking units (80) are arranged at angular intervals (W) around the pivot axis (22) to form a rotation-blocking configuration, that the working position receptacles (60A) and / or the rest position receptacles (60R) are arranged at the same angular intervals (W) around the pivot axis (22) as the rotation-blocking units (80) to form a respective receptacle configuration for the working position (A) and / or the rest position (R), that the rotation-blocking configuration and the receptacle configuration of the working position receptacles (60A) in the working position (A) or of the rest position receptacles (60R) in the rest position (R) are congruent with one another, so that the rotation-blocking bodies (54) can engage in the working position receptacles (60A) or rest position receptacles (60R), and that the angular intervals (W) between the rotation-blocking units (80) of the rotation-blocking configuration and the angular intervals between, the working position receptacles (60) or the rest position receptacles (60R) of the receptacle configurations are selected such that the rotation-locking configuration and one of the receptacle configurations are congruent with each other only in the working position (A) and / or the rest position (R). Trailer coupling according to one of the preceding claims, characterized in that the angular distances (W) of at least one of the rotation-locking units (80) to the rotation-locking units (80) arranged adjacent in a direction of rotation around the pivot axis (22) and to the rotation-locking units (80) opposite to this direction of rotation are unequal, that in the working position (A) the working position receptacles (60A) are arranged such that the rotation-locking body (54) of each of the rotation-locking units (80) can be brought into engagement with one of the working position receptacles (60A), and / or that in the rest position (R) the rest position receptacles (60R) are arranged such thatthat the rotation-blocking body (54) of each of the rotation-blocking units (80) can be brought into engagement with one of the rest position receptacles (60R), and that in all pivot positions of the pivot bearing body (14) intended for operation, which lie outside the working position (A) or the rest position (R), the rotation-blocking body (54) of at least one of the rotation-blocking units (80) is opposite a blocking surface (90) extending between the working position receptacles (60A) and / or the rest position receptacles (60R), and the blocking surface (90), in particular when a force is applied to the actuating body (52), blocks movement of the actuating body (52) from the release position to the rotation-blocking position. Trailer coupling according to one of claims 37 to 39, characterized in that the blocking surfaces (90) face the rotation-blocking bodies (54) of the rotation-blocking units (80). Trailer coupling according to one of claims 37 to 40, characterized in that the blocking surfaces (90) extend within a defined radius around the pivot axis (22). Trailer coupling according to one of claims 37 to 41, characterized in that the blocking surfaces (90) extend to and merge into opening edges (92) of the working position receptacles (60A) and / or the rest position receptacle (60R). Trailer coupling according to claim 42, characterized in that the opening edges (92) of the working position receptacles (60A) and / or the rest position receptacle (60R) are at the same radial distance from the pivot axis (22) as the blocking surfaces (90).Trailer coupling according to one of claims 37 to 43, characterized in that at least one of the rotation-locking bodies (54) of the rotation-locking units (80) bears against one of the blocking surfaces (90) during a pivoting movement of the pivot bearing body (14) in the direction of the working position (A), in particular due to the action of the actuating body (52), with a force applied thereto. Trailer coupling according to one of claims 37 to 44, characterized in that the rotation-locking bodies (54) bear against the blocking surfaces (90) with a force applied thereto before reaching the working position (A) and subsequently enter the working position receptacles (60A) with a force applied thereto against opening edges (92) of the working position receptacles (60A).Trailer coupling according to one of claims 37 to 45, characterized in that the working position receptacles (60A) extend from the blocking surfaces (90) in the guide direction (58), in particular with at least one component in the radial direction to the pivot axis (22). Trailer coupling according to one of claims 37 to 46, characterized in that at least one of the rotation-blocking bodies (54) of the rotation-blocking units (80) bears against one of the blocking surfaces (90) during a pivoting movement of the pivot bearing body (14) in the direction of the rest position (R), in particular due to the action of the actuating body (52), with a force applied thereto. Trailer coupling according to one of claims 37 to 47, characterized in that the rotation-blocking bodies (54) bear against the blocking surfaces (90) with a force applied thereto before reaching the rest position (R) and subsequently enter the rest position receptacles (60R) with a force applied thereto against opening edges (92) of the rest position receptacles (60R).Trailer coupling according to one of claims 37 to 48, characterized in that the rest position receptacles (60R) extend from the blocking surfaces (90) in the guide direction (58), in particular with at least one component in the radial direction to the pivot axis (22). Trailer coupling according to one of claims 37 to 49, characterized in that the working position receptacles (60A), the rest position receptacles (60R), and the blocking surfaces (90) are arranged facing the guide sleeve (40). Trailer coupling according to one of the preceding claims, characterized in that the guide body (40) is a part of the pivot bearing unit (20) arranged fixedly to the vehicle. Trailer coupling according to one of the preceding claims, characterized in that all guide receptacles (56) for the rotation-blocking bodies (54) of the rotation-blocking units (80) are arranged in the guide body (40). Trailer coupling according to one of the preceding claims, characterized in that the guide direction (58) runs with at least one component in the radial direction to the pivot axis (22). Trailer coupling according to one of the preceding claims, characterized in that the guide body (40) has a guide sleeve (44) with guide receptacles (56) for the rotation-blocking bodies (54) of the rotation-blocking units (80), and in particular that the rotation-blocking bodies (54) are guided by the guide body (40) adjoining the pivot bearing body (14) in the radial direction. Trailer coupling according to one of the preceding claims, characterized in that the guide body (40) has a pivot bearing for the pivot bearing body (14). Trailer coupling according to one of the preceding claims, characterized in that the actuating body (52) is guided so as to be movable relative to the guide body (40).Trailer coupling according to one of the preceding claims, characterized in that the actuating body (52) is arranged to rotate about the pivot axis (22) and, in particular, has wedge surfaces (66) extending over an angular range about the pivot axis (22) and varying in a direction parallel to the guide direction (58), preferably combined with retraction receptacles (62). Trailer coupling according to one of the preceding claims, characterized in that the receptacles (60) and the blocking surfaces (90) are arranged on the pivot bearing body (14). Trailer coupling according to one of the preceding claims, characterized in that the actuating body (52) is enclosed by the guide body (40), and in particular that the pivot bearing body (14) engages around the guide body (40). Trailer coupling according to one of the preceding claims, characterized in that the rotation-blocking bodies (54) are arranged around the actuating body (52). Trailer coupling according to one of the preceding claims, characterized in that the pivot bearing body (14) forms an outer body which externally surrounds the pivot bearing unit (20) and is arranged immovably relative to the pivot bearing unit (20) in the direction of the pivot axis (22), and in particular that the pivot bearing body (14) forms an outer body which externally surrounds at least a partial region of the rotation-blocking unit (50), and which is arranged immovably relative to the guide body (40) in the direction of the pivot axis (22).Trailer coupling according to one of the preceding claims, characterized in that the actuating body (52) is biased toward its rotation-locking position by an elastic energy accumulator (114). Trailer coupling according to one of the preceding claims, characterized in that the actuating body (52) can be moved from the rotation-locking position to the release position by an actuating device (180). Trailer coupling according to claim 62 or 63, characterized in that the actuating body (52) can be moved by the actuating device (180) against the bias of the energy accumulator (114). Trailer coupling according to one of claims 62 to 64, characterized in that the actuating body (52) can be rotated by the actuating device (180) opposite to the actuating direction (72) brought about by the elastic force accumulator (114). Trailer coupling according to one of the preceding claims, characterized in that the actuating device (180) has an output element (142) which is coupled to the actuating body (52). Trailer coupling according to claim 66, characterized in that the output element (142) and the actuating body (52) are coupled to one another via a driving coupling device (156, 158). Trailer coupling according to claim 67, characterized in that the driving coupling device (156, 158) has a driving-free free state and a driving state.Trailer coupling according to one of the preceding claims, characterized in that the actuating device (180) for the rotation-locking device (50) comprises a motor drive unit.

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