Adjustment device for a movable element and arrangement with a movable element and an adjustment device associated with the movable element

Abstract

The invention relates to an adjustment device (14) for a movable element (12) with at least one adjustment element (16, 18) pivotally connected to the element (12) for adjusting it. The at least one adjustment element (16) has a spring element (24) and two guide elements (26, 28) that are telescopically extendable relative to each other. The invention further relates to an arrangement (10) with a movable element (12) and an adjustment device (14) associated with the movable element (12).

Description

The invention relates to an adjustment device for a movable element, comprising at least one adjustment element pivotally connected to the movable element for adjusting the element. The invention further relates to an arrangement comprising a movable element and an adjustment device associated with the movable element. Adjustment devices for movable elements, such as movable doors, hoods, or flaps of motor vehicles, which allow the movable element to be moved from an open to a closed position or vice versa, are generally known. Known adjustment devices in the form of gas springs, shock absorbers, or electric drives enable effortless and convenient adjustment of flaps or similar elements, thereby increasing the vehicle's user-friendliness. In electrically driven adjustment devices, a passive adjusting element, i.e., a gas spring or a gas spring in combination with a mechanical spring element, is often used to compensate for force. With such a passive / active system, it is important that both adjusting elements exert approximately the same force on the movable element under all operating conditions; otherwise, elements with low torsional stiffness may not function reliably. Therefore, the object of the invention is to provide an improved adjustment device for a movable flap. Furthermore, an improved arrangement comprising a movable element and an adjustment device associated with the movable element is to be provided. This problem is solved according to the invention by an adjusting device for a movable element with at least one adjusting element articulated for adjusting the element according to claim 1. According to the invention, the at least one adjusting element comprises a spring element and two guide elements that are telescopically adjustable relative to each other. Preferably, a single spring element is provided. However, within the scope of the invention, it is also conceivable to use several spring elements. This results in a cost-effective design of the adjusting element according to the invention with few components. The at least one adjusting element is preferably designed as a passive adjusting element, whose entire spring force is provided solely by the spring element(s). The guide elements also partially assume the task of transmitting longitudinal and transverse forces. This allows for particularly cost-effective force compensation with fewer components. The spring element is preferably designed as a mechanical spring element. The mechanical spring element can, for example, be designed as a helical compression spring. Other designs of the mechanical spring element, for example as a rubber buffer, are also possible within the scope of the invention. Depending on the design and arrangement of the spring element(s), a first guide element can be provided for the outer guidance of the spring element and a second guide element for the inner guidance of the spring element. Likewise, both guide elements can be designed for either inner or outer guidance. Preferably, in a retracted and / or extended position of the adjusting element, the two guide elements can be brought into a lockable contact. This allows for selective and simple locking in the retraction or extension direction by means of the guide elements. Preferably, the second guide element comprises an inner guide element and an outer tube that at least partially surrounds the inner guide element, wherein, in a retracted and / or extended position of the passive adjusting element, the outer tube can be brought into lockable contact with the first guide element. The outer tube allows for simple limiting of the position(s) of the two guide elements relative to each other. The outer tube can have an inner projection that can be positioned against an outer projection of the first guide element. These projections can be easily manufactured, for example, using an injection molding process, and can be integrally molded onto the respective components. Alternatively, they can be formed on a separate component. Preferably, a stop element is provided which forms the inner projection, wherein the stop element is designed to be positively locked to an end of the outer tube facing the first guide element. This separate design has the advantage that the guide elements can be simplified. Furthermore, assembly can be simplified. The stop element can, through appropriate design, fulfill additional functions such as end damping. A coating on the metal spring element may be omitted if the first and second guide elements are at least partially made of plastic. "Partially" in this context means that the components in contact with the spring element are made of plastic. A coating on the spring element is generally applied to prevent noise. One known coating method is flocking. This costly coating may be unnecessary due to the existing plastic-on-plastic or plastic-on-metal friction pairing. To further simplify the passive adjustment element, the guide elements can each have a base at their opposite end regions, with a connection element for attaching the passive adjustment element to the flap or to a higher-level component being arranged on each base. The connection elements can thus be attached directly to the components. Additional connecting elements are obsolete. It is particularly advantageous if the housing of the connecting element is formed as a single piece with the base. Especially when the guide elements are made of plastic, the housing can be easily molded in during manufacturing. A ball socket for receiving a ball head can be easily integrated into the housing. Costly work steps, such as welding on threaded bolts or screwing on ball sockets, can be eliminated. According to an advantageous embodiment of the invention, one or more absorption elements can be provided which are designed to absorb the kinetic energy of the adjusting element in the event of an overload, particularly an overload occurring at the end stop. In other words, the end stop of the preferably passive adjusting element can be equipped with an energy absorption function, thereby creating a damping effect. This is possible, for example, by deformation of the absorption element(s). In normal operation, i.e., under normal load conditions, the weight of the element to be moved and, if applicable, a speed control adapted to it, work against the extension force of the adjusting element. Unwanted, uncontrolled, and undamped acceleration of the adjusting element occurs, for example, in the event of misuse, if the articulated connection of the adjusting element is unintentionally or fraudulently removed or damaged.Failure. In this case, the potential energy stored in the mechanical spring element is abruptly converted into kinetic energy, and the adjusting element accelerates uncontrollably and without damping. This overload situation can also occur during vehicle assembly if the vehicle is tilted to facilitate assembly and the weight force opposing the adjusting element is significantly reduced. With the aid of the absorption element(s), it is possible to absorb at least a large portion of the energy in the aforementioned overload situation and thus significantly reduce the force generated at the end stop. The absorption element can be designed to be reversible or irreversible within the scope of the invention. Preferably, a tubular absorption element made of plastic can be arranged between the guide elements. This can be easily inserted during assembly. For example, the tubular absorption element is arranged axially between the inner and outer projections. According to a preferred embodiment, the absorption element has at least one deformation element which is designed to absorb kinetic energy of the adjusting element in the event of an overload occurring at the end stop. Particularly in the overload case already described several times, in which the potential energy stored in the spring element is suddenly converted into kinetic energy and the adjusting element accelerates uncontrollably and undamped, the deformation element absorbs the kinetic energy occurring at the end stop through deformation and / or friction. According to a preferred embodiment, the absorption element comprises at least one first deformation element and at least one second deformation element, as well as a predetermined breaking element. The predetermined breaking element is designed such that it separates the first and second deformation elements from each other in a rest state and breaks upon an overload occurring at the end stop, causing the first and second deformation elements to engage with each other. This provides a simple and effective safety mechanism that is activated only in the event of an overload and thus reliably prevents damage from uncontrolled extension, i.e., from an undamped impact at the end of the stroke (end stop) due to an axial overload, without impairing normal operation. It should be noted that a rest state can also be understood as a normal load case or a non-overload case, not exclusively an unactuated state of the adjusting element.the adjustment device. According to a further preferred embodiment of the invention, the first deformation element and the second deformation element are configured as a first group of axially aligned prong elements and a second group of prong elements configured in the opposite direction and axially offset to the first group. The predetermined breaking element is configured as a web that rigidly connects the two groups of prong elements in the rest state, so that they interlock when the web fails. This design enables particularly cost-effective manufacturing, for example by injection molding, and ensures a defined and reliable energy dissipation over the available process path (stroke). In other words, a type of friction brake is created. According to a further preferred embodiment of the invention, the tine elements of the first and second groups have an interference cross-section relative to each other, which, after failure of the web, generates energy-absorbing friction between the interlocking tine elements and / or between the tine elements and the first guide element. This defined interference cross-section allows the strength of the braking effect, and thus the rate of energy absorption, to be precisely and repeatably adjusted. Preferably, a maximum frictional force of 3 kN is specified. The non-reversible end damping can be adapted to the respective applications, in particular by the number of fan-like, interlocking tine elements (more tine elements = more energy dissipation per path), the interference between the tine elements, the wall thickness of the tine elements, and by the surface finish or material selection. The design of the web defines the static holding force before activation of the end damping. Furthermore, the inventive design of the tine elements makes it possible to design them above their buckling point, since they are guided both internally and externally. This not only allows for a particularly space-saving radial design, but also generates additional frictional work through controlled buckling or folding of the tine elements due to the internal and external forced guidance. Preferably, the absorption element can be formed as a single unit with a stop element of the second guide element. This integral design reduces the number of components and significantly simplifies assembly, resulting in significant cost savings. According to an alternative preferred embodiment of the invention, the absorption element is designed as a reversible damping element which, in the event of an overload occurring at the end stop, transitions from a first stable state to a second stable state, or snaps shut, in order to absorb the kinetic energy of the adjusting element. This design offers the advantage that the damping element is reusable after an overload event and no permanent damage to components occurs. Ring springs can be used as an example of a reversible element. The almost purely elastic deformation of the ring springs exhibits a high degree of utilization. Preferably, the adjusting element is passive and forms a first adjusting element. In this context, passive means that the entire spring force is provided solely by the mechanical spring element(s). The adjustment device may preferably have a further, second adjustment element. The second adjustment element may be active or passive. In this context, "active" means that the movable flap can be adjusted by means of the active adjustment element, either by motor and / or hydraulically. Preferably, the second adjusting element is designed as an electric drive, in particular as an electric spindle drive. The invention further relates to an arrangement with a movable element and an adjustment device associated with the movable element. Preferably, the arrangement is designed as an adjustment arrangement for a movable element, in particular for a vehicle flap. The invention will be explained in more detail below with reference to exemplary embodiments and the accompanying drawing. The drawing shows: Fig. 1 a schematic representation of a motor vehicle with a movable flap as a movable element, an adjusting device according to the invention, and an arrangement according to the invention; Fig. 2 a side view of a passive adjusting element of an adjusting device according to the invention; Fig. 3 a longitudinal section along AA of the passive adjusting element according to Fig. 2; Fig. 4 a side view of a passive adjusting element of a second exemplary embodiment of an adjusting device according to the invention; Fig. 5 a longitudinal section along AA of the passive adjusting element according to Fig. 4; Fig. 6 an enlarged detail of a further longitudinal section of the passive adjusting element according to Figs. 4 and 5; Fig. 7 an enlarged detail of a third longitudinal section of the passive adjusting element according to Figs. 4, 5, and 6.Fig. 6; Fig. 8 a side view of a stop element of the passive adjustment element according to Figs. 4, 5 and 6; Fig. 9 a front view of the stop element according to Fig. 8; Fig. 10 a perspective view of the stop element according to Figs. 8 and 9; Fig. 11 a perspective view of a stop element with an integrally formed absorption element of a further embodiment of the invention; Fig. 12 a perspective view of an absorption element of a further embodiment of the invention; Fig. 13 a perspective view of an absorption element of a further embodiment of the invention; and Fig. 14 a longitudinal section of the absorption element according to Fig. 13. Fig. 1 shows a schematic representation of a principle sketch of a motor vehicle with a flap arrangement 10 according to the invention, comprising a movable flap 12 as a movable element and an adjustment device 14 associated with the flap 12. It should be noted that, within the scope of the invention, the movable elements can be movable doors, flaps, loading hatches, hoods or similar, in particular of vehicles, buses, aircraft, etc. The adjusting device 14, with two adjusting elements 16 and 18, enables distortion-free adjustment of the flap 12 between an open and a closed position, with intermediate positions also being possible. It is designed to compensate for the weight of the flap 12, thereby assisting the user and enabling comfortable opening and closing of the flap 12. The adjustment movement of the flap 12 can be fully force-compensated, self-opening, or automatically opening. Depending on the requirements and design of the flap 12, different versions of the adjusting device 14 are possible. In the illustrated embodiment, the movable flap 12 is designed as a tailgate of a motor vehicle and is mounted in a virtual, horizontal pivot axis 20 extending transversely to the motor vehicle. A first adjusting element 16 is arranged on one side of the flap 12, and a second adjusting element 18 is arranged on the opposite side of the flap 12. Both adjusting elements 16 and 18 are pivotally attached to the flap 12 and to a body 22 of the motor vehicle as a higher-level assembly by means of connecting elements and attachment elements 36 and 54 (see Fig. 3). The adjustment device 14 is designed as a passive / active system. The first adjustment element 16 is designed as a passive adjustment element. The second adjustment element 18, on the other hand, is designed as an active adjustment element, for example as an electric drive, in particular as an electric spindle drive, and enables motorized adjustment of the flap 12. In this context, "active" means that the movable flap 12 can be adjusted by means of the active adjusting element 18, either motor-driven and / or hydraulically. An adjusting element that serves to compensate for and / or assist forces without a motor drive is referred to as "passive." The second adjusting element 18 can also be designed as a passive element. Figures 2 and 3 show a first embodiment of a first, passive adjusting element 16 for an adjusting device 14 according to the invention. As can be seen particularly in Figure 3, which shows a longitudinal section along line AA of Figure 2, the first adjusting element 16 has a spring element 24, here a helical compression spring, and two guide elements 26, 28 that are telescopic relative to each other. It can be seen that a first guide element 26 is designed for the outer guidance of the helical compression spring 24 and a second guide element 28 for the inner guidance of the helical compression spring 24. The embodiment provides that the adjusting device 14 has a single mechanical spring element 24. However, within the scope of the invention, it is conceivable to use one or more helical compression springs. Furthermore, other configurations of a mechanical spring element (for example, a rubber buffer) are possible. In the illustrated embodiment, the spring force of the passive adjusting element 16 is provided solely by the helical compression spring 24. The first guide element 26 is made of plastic and has a guide tube 32 to which a base 30 is attached or molded at one end. In the illustrated embodiment, the base 30 is integrally molded onto the guide tube 32 of the first guide element 26, in particular by means of an injection molding process. A first spring end 34 of the spring element 24 rests against the inside of the base 30. On the outside of the base 30, a first connecting element 36 is attached, which is provided for the articulated connection of the passive adjusting element 16 to the body 22 or to the flap 12. It is particularly advantageous if the housing of the first connecting element 36 is formed in one piece with the base 30. This means that the housing, which here exemplarily has a ball socket for receiving a ball head of the joint connection, is simply injection-molded directly onto the base 30, thus eliminating additional work steps such as welding on threaded bolts or screwing on ball sockets. The second guide element 28 comprises an inner guide element 38, by means of which the helical compression spring 24 is guided internally. As can be seen from Fig. 3, the inner guide element 38 is tubular. A base 40 of the second guide element 28 is integrally formed with the inner guide element 38 and is produced in particular by means of an injection molding process. Furthermore, the second guide element 28 comprises an outer tube 42, which partially surrounds the inner guide element 38 and the helical compression spring 24, and which is designed to be displaceable relative to the guide tube 32 of the first guide element 26. The guide tube 32 and the outer tube 42, which is displaceable on an outer surface of the guide tube 32, form a housing for the passive adjusting element 16. The outer tube 42 is attached to the base 40, for example by means of a clip connection. For this purpose, the outer tube 42 can have elastic tongues 44 with recesses 46 at its ends, which engage or snap into corresponding radially projecting projections 48 of the base 40 for attachment. The outer tube 42 is also advantageously made of plastic. A one-piece design of the guide element 28 is also conceivable within the scope of the invention. To define a maximum extended position of the passive adjusting element 16, the two guide elements 26, 28 can be brought into a lockable contact in a fully extended position. This means that the two guide elements 26, 28 cannot be moved further relative to each other in this maximally extended position, which is shown in Figs. 2 and 3. In the illustrated embodiment, the outer tube 42 and the guide tube 32 can be brought into lockable contact with each other. For this purpose, the outer tube 42 has an inner projection 50, which can be abutted against an outer projection 52 of the first guide element 26 or the guide tube 32. "Inner" here means that the projection 50 extends radially inwards. Thus, the outer projection 52 extends radially outwards. The projections 50 and 52 are easy to manufacture and are integrally formed on the outer tube 42 and the guide tube 32, respectively. As can be seen in Fig. 3, the projections 50 and 52 each form contact surfaces 70 and 72, which, in the extended position, abut each other and thus prevent further displacement of the two guide elements 26 and 28 from one another. The two tubes 32 and 42 can be easily mounted together, for example, by means of a bayonet fitting. Analogous to the first guide element 26, a housing of a second connection element 54 is also integrally formed on the base 40 of the second guide element 28 and serves as the articulated connection to the body 22 or to the flap 12. Figures 4, 5, 6, 7, 8, 9 to 10 show a passive adjusting element 16 of a further embodiment of an adjusting device 14. The basic structure does not differ from the first embodiment, so only the differences will be discussed below. Identical and similar components are designated with the same reference numerals. Fig. 4 shows a side view of the passive adjusting element 16 of the second embodiment of an adjusting device 14 according to the invention. From the longitudinal section along AA shown in Fig. 5, it can be seen that, in contrast to the embodiment described above, the inner guide element 38 of the second guide element 28 is not formed integrally with the base 40, but rather as a separate component made of plastic and bears against the inside of the base 40 with a radially outwardly projecting collar 56. A second spring end 58 of the helical compression spring 24 bears against the inside of the collar 56 of the inner guide element 38 and supports it against the base 40. In contrast, the outer tube 42 is provided as a single unit with the base 40, which eliminates the need for the clip connection described above. Furthermore, the guide tube 32 of the first guide element 26 has the outer projection 52 as already described. In a further difference from the first embodiment, the inner projection 50 of the first guide element 26 is designed as a separate stop element 60, which is shown in various views in Figures 8, 9 to 10. The holding force or energy absorption can be adjusted by changing the stop element 60 without changing the other components. This allows for a wide variety of force settings. The essentially tubular stop element 60 has, for example, eight radially outwardly projecting projections 62, which, during assembly of the stop element 60, can be engaged between the guide tube 32 and the outer tube 42 in recesses 64 of elastic tongues 66 of the outer tube 42. This ensures that the stop element 60 is positively locked to an end of the outer tube 42 facing the first guide element 26. As can be seen in particular from Figs. 6 and 7, which show enlarged sections of further longitudinal sections of the passive adjusting element 16 from Fig. 4, the stop element 60 in this embodiment forms the inner projection 50 with the contact surface 70. Furthermore, the stop element 60 has one or more, preferably two, guide ribs 68 which can be inserted between two elastic tongues 66 of the outer tube 42, thus facilitating assembly. Likewise, the stop element 60 has a chamfer 74 in the area of ​​the contact surface 70 to improve insertion between the guide tube 32 and the outer tube 42. As can be seen in Fig. 8 and Fig. 10, the guide webs 68 and the projections 62 also have chamfers 68 and 63, which greatly simplify assembly. Furthermore, one or more absorption elements are provided, which are designed to dissipate the kinetic energy of the passive adjustment element 16 in the event of an overload, particularly in the case of its unintentional extension. In other words, the end stop of the passive adjustment element 16 can be equipped with an energy absorption function. This is possible, for example, by deformation of the absorption element(s). For example, a tubular absorption element 76, made of plastic and shown in Fig. 6, can be provided as an absorption element, which is arranged between the guide elements 16, 18, i.e., specifically between the outer projection 52 and the stop element 60. It is also conceivable to provide a ribbed or honeycomb structure on the plastic components 32 and / or 42, which, if necessary, can absorb a large part of the spring energy when the passive adjusting element 16 is extended by means of deformation. Due to the described friction pairing of plastic on plastic or plastic on metal, it is advantageously possible to omit a spring coating and avoid disturbing noises. Figures 11, 12, 13 to 14 show absorption elements 78 of further embodiments of a passive adjusting element 16. The basic structure of the adjusting element 16 does not differ from the previous embodiments, so only the differences are discussed below. Identical and similar components are designated with the same reference numerals. Figure 11 shows a perspective view of the absorption element 78 of a further embodiment. This element serves as a safety element and, as already described, enables end-position damping in the event of an overload. The absorption element 78 comprises a first deformation element 84 arranged in a first axial region 80 and at least one second deformation element 86 arranged in a second axial region 82, as well as a predetermined breaking element 88, which separates the first and second deformation elements 84, 86 from each other in a rest state. The predetermined breaking element is designed such that, in the event of unintentional extension of the passive adjusting element 16, i.e., in the case of high impact forces exceeding the strength of the adjusting element 16 or its components, it breaks due to an axial overload, causing the first and second deformation elements 84, 86 to engage with each other. As can be clearly seen in Fig. 11, the first deformation element 84 and the second deformation element 86 are designed as a first group of axially aligned tine elements and a second group of tine elements arranged in the opposite direction and axially offset to the first group. The predetermined breaking element 88 is designed as a web that preferably rigidly connects the two groups of tine elements in the rest state (normal load case or non-overload case) and reliably prevents them from interlocking. In the case of overload, the web can fail in a controlled manner, allowing the tine elements, which are arranged offset from each other, to move into or engage with one another. The tine elements of the first and second groups have an excess in cross-section relative to each other, which, after failure of the web, creates energy-absorbing friction between the interlocking tine elements and / or between the tine elements and the first guide element 28 or the outer tube 42, as the tine elements bunch up. A friction brake is created, so that the end stop of the adjusting element 16 is designed in a simple and cost-effective manner with an energy dissipation function and thus end-position damping in the event of an overload. A simple and effective safety mechanism is provided that is only activated in the event of an overload and thus reliably prevents damage from uncontrolled extension without affecting normal operation. As can be seen from Fig. 11, the prong elements are each chamfered at their mutually facing ends, which are connected to the bridge in the rest state, to simplify and ensure interlocking. The width and flank angles of the tine elements can vary due to manufacturing advantages. This allows for a 180° offset lateral demolding, which is significantly more robust and cost-effective than radial demolding of each recess. As shown in the example in Fig. 11, the absorption element 78 is provided as a single unit with a stop element 60 already described above. This integral design reduces the number of components and significantly simplifies assembly. Slots 90 provided on one end face of the stop element 60 can also serve for position verification. Figure 12 shows a perspective view of the absorption element 78 of a further embodiment. Unlike the preceding embodiment, this element is not formed integrally with the stop element of the passive adjusting element 16, but is arranged between the guide elements 16, 18, i.e., specifically between the outer projection 52 and the stop element 60. The absorption element 78 is simple and cost-effective in design and can be easily adapted to various requirements. Figures 13 and 14 show a perspective view of the absorption element 78 of a further embodiment. In contrast to the preceding embodiment, the deformation elements are not designed as prong elements. The first deformation element 84 is a continuous wall, while the second deformation element 86 is designed as a double wall. In this embodiment as well, the deformation elements are rigidly connected in the rest state by means of a web as a predetermined breaking element. In the event of overload, the web can fail in a controlled manner, so that the continuous wall and the double wall can engage with each other. The continuous wall is then pressed into a radial gap in the double wall that is too narrow, in order to generate energy-absorbing friction between the engaging elements and / or between the elements and the first guide element 28 or the outer tube 42. The absorption elements 68, 78 described above can also be used in passive adjustment elements which have a gas spring as a spring element or a gas spring in combination with one or more mechanical spring elements (strut). The inner guide element can, for example, be formed by a cylinder of the gas spring.

Claims

Adjustment device (14) for a movable element (12) with at least one adjustment element (16, 18) pivotally connected for adjusting the element (12), characterized in that the at least one adjustment element (16) has a spring element (24) and two guide elements (26, 28) that are telescopically extendable relative to each other. Adjusting device (14) according to claim 1, characterized in that the spring element is designed as a mechanical spring element. Adjustment device (14) according to claim 1 or 2, characterized in that a first guide element (26) is provided for the outer guidance of the spring element (24) and a second guide element (28) is provided for the inner guidance of the spring element (24). Adjustment device (14) according to one of claims 1 to 3, characterized in that in a retracted and / or in a retracted position of the adjustment element (16) the two guide elements (26, 28) can be brought into a lockable contact. Adjustment device (14) according to claim 4, characterized in that the second guide element (28) has at least one inner guide element (38) and an outer tube (42) at least partially surrounding the inner guide element (38), wherein in a pushed-in and / or in a pushed-out position of the adjustment element (16) the outer tube (42) can be brought into a lockable contact with the first guide element (26). Adjustment device (14) according to claim 5, characterized in that the outer tube (42) has an inner projection (50) which can be applied to an outer projection (52) of the first guide element (26). Adjustment device (14) according to claim 6, characterized in that a stop element (60) is provided which forms the inner projection (50), wherein the stop element (60) is provided to be positively lockable on an end of the outer tube (42) facing the first guide element (26). Adjustment device (14) according to one of the preceding claims, characterized in that the guide elements (26, 28) are at least partially made of plastic. Adjustment device (14) according to claim 8, characterized in that the guide elements (26, 28) each have a base (30, 40) at mutually opposite end regions, wherein a connecting element (36, 54) for connecting the adjustment element (16) to the movable element (12) or to a superior assembly unit (22) is arranged on each of the bases (30, 40). Adjustment device (14) according to claim 9, characterized in that each housing of the connecting element (36, 54) is provided as a single unit with the base (30, 40). Adjustment device (14) according to one of the preceding claims, characterized in that one or more absorption elements (76, 78) are provided which are designed to absorb the kinetic energy of the adjustment element (16) in the event of an overload, in particular in the event of an overload occurring at the end stop. Adjustment device (14) according to claim 11, characterized in that a tubular absorption element (76) made of plastic is arranged between the guide elements (26, 28). Adjustment device (14) according to claim 11 or 12, characterized in that the absorption element (78) has at least one deformation element which is designed to absorb kinetic energy of the adjustment element in the event of an overload occurring at the end stop. Adjustment device (14) according to one of claims 10 to 13, characterized in that the absorption element (78) has at least one first deformation element and at least one second deformation element as well as a predetermined breaking element (88), wherein the predetermined breaking element is designed such that it separates the first and the second deformation element (84, 86) from each other in a rest state and breaks in the event of an overload occurring at the end stop, so that the first and the second deformation element (84, 86) engage with each other. Adjustment device (14) according to claim 14, characterized in that the first deformation element and the second deformation element are designed as a first group of axially aligned tine elements (84) and a second group of tine elements (86) designed in the opposite direction and axially offset to the first group, and that the predetermined breaking element is designed as a web (88) which rigidly connects the two groups of tine elements (84, 86) in the rest state, so that they interlock when the web (88) fails. Adjustment device (14) according to claim 15, characterized in that the tine elements (84, 86) of the first and second group have an interference in cross-section with respect to each other, which, after the failure of the web (80), generates an energy-absorbing deformation and / or friction between the interlocking tine elements (84, 86) and / or between the tine elements (84, 86) and one of the guide elements (26, 28). Adjustment device (14) according to claim 11, characterized in that the absorption element (78) is formed in one piece with a stop element (60) of the second guide element (28). Adjustment device (14) according to claim 11, characterized in that the absorption element is designed as a reversible damping element which, in the event of an overload occurring at the end stop, transitions from a first stable state to a second stable state in order to absorb kinetic energy of the adjustment element (16). Adjustment device (14) according to one of the preceding claims, characterized in that a further, second adjustment element is provided, wherein the second adjustment element (18) is designed to be active or passive. Arrangement (10) with a movable element (12) and an adjustment device (14) associated with the movable element (12) according to one of the preceding claims. Arrangement (10) according to claim 20, wherein the arrangement (10) is designed as an adjustment arrangement for a movable element, in particular for a vehicle flap.

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