JOINT DEVICE FOR A FLAP UNIT OF A MOTOR VEHICLE AND FLAP UNIT FOR A MOTOR VEHICLE

Description

Technical field

[0001] The present invention relates to a joint device for a flap unit of a motor vehicle and to a flap unit for a motor vehicle, wherein the flap unit has a joint device. State of the art

[0002] In vehicle manufacturing, particularly series production, there is a current need to equip the interior, especially the passenger compartment, of a motor vehicle, such as a passenger car and / or truck, with a variety of flap elements. These elements are designed, for example, to serve as a cover for a storage compartment and / or to provide different adjustment options for the vehicle's user. Such a flap element could, for instance, be an adjustable armrest, particularly for a center console, in the vehicle's interior. Furthermore, it is known in the automotive sector that such an adjustable armrest can be integrated with a cover element for the storage compartment. To ensure that a user of the flap element...If the user, in particular the driver, of a motor vehicle equipped with the corresponding flap element can move the flap element particularly easily - for example between an open position and a closed position - devices for the flap element are known by means of which the movement, in particular the opening, of the flap element is supported.

[0003] WO 2004 / 013439A2 and US 2007 / 0039135A1 each disclose a hinge mechanism for handheld devices such as flip phones, PDAs, etc. The hinge mechanism comprises a helical spring that functions as both a torsion spring and a compression spring. The hinge mechanism is designed to assist the rotation of a folding part relative to a main part of a device incorporating the hinge mechanism, such that, upon exceeding a limit position, the folding part is automatically pivoted into a fully extended or fully closed position by means of a relaxation of the helical spring in the torsional direction.

[0004] However, it is essential to prevent the aforementioned flap element from moving unintentionally, for example, unintentionally. This necessitates a device for the flap element that allows its movement to be braked. Consequently, a conflict of objectives exists for the conventional flap element and its movement, a conflict that neither WO 2004 / 013439A2 nor US 2007 / 0039135A1 resolves. Description of the invention

[0005] The object of the invention is to make the adjustment or movement of a flap element, in particular of a motor vehicle, particularly advantageous.

[0006] This problem is solved by the independent claims. Features, advantages, and advantageous embodiments of the joint device according to the invention are to be regarded as features, advantages, and advantageous embodiments of the flap unit according to the invention, and vice versa. Further possible embodiments of the invention are disclosed in the dependent claims, the description, and the figures.

[0007] According to the invention, a hinged device for a flap unit of a motor vehicle is proposed. The flap unit is, for example, a lid unit of a storage compartment of the motor vehicle, wherein this storage compartment is located, in particular, in an interior space, specifically in a passenger compartment or passenger area of ​​the motor vehicle. The motor vehicle is preferably a car, especially a passenger car and / or truck. Furthermore, the flap unit can be designed as an armrest element of a console, for example, a center console, of the motor vehicle, preferably as a center armrest, by which two adjacent seats of a seating arrangement of the motor vehicle or passenger car are spaced apart from each other. For example, such a center armrest can be arranged between a driver's seat and a front passenger seat of a first row of seats in the passenger car.The lid element or armrest is adjustable between at least two positions, in particular manually by the user.

[0008] The joint device, in particular the flap unit, has a shaft which can be connected to a shaft receptacle of the motor vehicle in a rotationally fixed manner. This means that the motor vehicle equipped with the joint device or the flap unit includes the shaft receptacle that corresponds to the shaft. It is conceivable that the shaft is designed as an elongated, polygonal beam. However, it is particularly preferred that the shaft be elongated and straight, circularly cylindrical. The shaft further has a longitudinal center axis through which a pivot axis of the joint device is formed or defined. In other words, the longitudinal center axis of the shaft and the pivot axis of the joint device coincide. For the function of the flap unit (and consequently for the present description), it is understood that the shaft is arranged in a rotationally fixed manner with respect to all other elements of the flap unit.For example, if it is described that an element "rotates around the shaft", this rotation or pivoting occurs in relation to the longitudinal center axis of the shaft, that is, in relation to the pivot axis of the joint device.

[0009] Furthermore, the joint assembly comprises a support unit fixedly mounted on the shaft. The support unit has a support element, which is in particular designed as a support pin extending transversely from the shaft. This means that a longitudinal center axis of the support pin and the longitudinal center axis of the shaft or the pivot axis of the joint assembly are arranged transversely to each other, in particular perpendicularly to each other. Here, the support pin projects radially beyond an outer circumferential surface of the shaft. Alternatively or additionally, the support unit has a (further) support element, which is in particular designed as a hole penetrating transversely through the shaft, whereby this hole can be a blind hole or a through hole. A longitudinal center axis of this hole is arranged transversely, in particular perpendicularly, to the longitudinal center axis of the shaft or to the pivot axis of the joint assembly.Furthermore, the support unit may be designed to have a plurality of support elements. In particular, it is provided that each support element is fixed to the shaft in a rotationally and translationally fixed manner with respect to the longitudinal center axis of the shaft or with respect to the pivot axis of the joint device.

[0010] The joint device further comprises a pivoting unit that is pivotable around the shaft between a first end position and a second end position. This means that the pivoting unit is pivotably arranged on the shaft, so that it rotates or pivots around the shaft or its longitudinal center axis – i.e., around the pivot axis of the joint device – when pivoting or adjusting between the end positions. In particular, the pivoting unit comprises a hub component arranged on the shaft and a lever component directly connected to the hub component, the lever component being arranged transversely, and in particular perpendicularly, to the shaft. The hub component and the lever component may be connected to each other by force-fit, form-fit, and / or material-fit, for example, by being formed integrally with each other.As will be explained in more detail below, it is conceivable that the swivel unit is either fixed or movable in relation to the shaft.

[0011] Furthermore, the articulated joint has a brake unit comprising a first brake structure fixed to the pivot unit, specifically to the hub portion of the pivot unit. This means that, since the pivot unit is pivotable about the shaft or pivot axis of the articulated joint, the first brake structure, fixed to the hub portion, can pivot along with the pivot unit or hub portion. The brake structure thus rotates along the outer circumferential direction of the shaft when the pivot unit pivots or rotates about the shaft or pivot axis. The brake unit also has a second brake structure fixed to the shaft. As will be explained in more detail below, the second brake structure is either fixed or displaceable on the shaft. The brake structures face each other directly along the shaft or along a longitudinal direction of the shaft.

[0012] The joint device further comprises a helical spring assembly, which is arranged directly on the support unit and the pivot unit along a torsional tension direction inherent in the helical spring assembly and is clamped in the first end position of the pivot unit. This tensions the pivot unit, particularly its lever component, along the outer circumferential direction of the shaft in the torsional tension direction, i.e., opposite to the torsional relaxation direction, by means of the helical spring assembly. For example, a first end of the helical spring assembly, such as a first end leg of the helical spring assembly, and the support unit are brought into interaction such that the helical spring is supported at / in the support unit via its first end. For example, the first end leg of the helical spring assembly engages in the support element of the support unit, which is designed as a through hole or blind hole.Alternatively or additionally, the first end of the coil spring assembly, or its first end leg, is supported on the support element of the support unit, which is designed as the support pin. This prevents the end leg, or the first end of the coil spring assembly, from rotating around the shaft or the pivot axis of the joint. At a second end of the coil spring assembly opposite the first end, for example, at a second end leg, the assembly is arranged on the pivot unit, particularly on the lever arm of the pivot unit, in such a way that the second end of the coil spring assembly, or its second end leg, rotates with the lever arm when the latter rotates around the pivot axis of the joint or the shaft.In the first end position of the swivel unit, the helical spring unit is tensioned in the torsional direction because the second end leg of the helical spring unit is held accordingly by the swivel unit or by the lever component. In other words, the helical spring unit is tensioned in the torsional direction between the support unit and the swivel unit when the swivel unit is in the first end position.

[0013] The coil spring unit of the joint assembly is further characterized by being arranged and clamped between the support unit and the brake unit along a translational tension direction inherent in the coil spring unit. The brake structures are tensioned towards each other by the coil spring unit along a longitudinal direction of the shaft opposite to the translational tension direction, i.e., in the translational relaxation direction. The coil spring unit is supported at its first end by the support unit and at its second end – directly or indirectly – by the first brake structure or the second brake structure – namely, the one of the brake structures that is translationally displaceable with respect to the longitudinal direction of the shaft or the pivot axis of the joint assembly.

[0014] Due to the arrangement of the described elements of the joint device, the helical spring unit is adjustable along the torsional tension direction by pivoting the pivoting unit between a first tension position and at least one second tension position. This means that the helical spring unit can be adjusted from the first tension position towards a second tension position and / or into the second tension position by adjusting the pivoting unit from the first end position towards the second end position and / or into the second tension position.

[0015] The coil spring unit therefore has a dual functionality, namely - firstly - a torsional spring effect is provided by the coil spring unit, and - secondly - a compression spring effect is provided by means of the coil spring unit.

[0016] The compression spring effect of the helical spring unit is used as follows: In the fully assembled state of the joint, the brake structures are in direct contact with each other. This causes the brake structures to rub against each other, for example, via their respective friction surfaces, when the swivel unit is pivoted around the shaft or pivot axis of the joint. This friction between the brake structures generates a braking torque, the magnitude of which is directed against the pivoting motion of the swivel unit. The braking torque is primarily dependent on a translational spring force, i.e., the compression spring effect, and the respective coefficient of friction of the brake structures or friction surfaces. Accordingly: The greater the tension of the helical spring unit in the translational direction, the greater the translational spring force generated by the helical spring unit.The greater the pressure effect, the greater the amount of braking torque.

[0017] According to the invention, the translational spring force of the helical spring unit is selected or designed such that the brake structures or friction surfaces are pressed so firmly against each other by means of the helical spring unit that the braking torque and a mass-related torque of the pivoting unit (optionally including a flap element) cancel each other out around the shaft. This allows the pivoting unit and / or the flap element to be held between the end positions, thus preventing unintentional pivoting of the pivoting unit (for example, the flap element arranged on the pivoting unit accidentally closing).

[0018] The torsional spring effect of the coil spring unit is used as follows: In the fully assembled state of the joint, a torsional spring moment from the coil spring unit acts against the direction of torsional tension, i.e., in the direction of torsional relaxation, on the pivot unit, particularly on its lever arm. This tensions the pivot unit via its lever arm in the first end position towards the second end position, whereby the mass-related torque of the pivot unit is at least partially counteracted by the correspondingly opposing torsional spring moment. In other words, the coil spring unit assists in moving the pivot unit from the first end position towards the second end position, by means of the torsional spring effect or the torsional spring moment of the coil spring unit, which rotates the pivot unit around the shaft.The pivoting mechanism can be driven around its pivot axis. It is important to note that the torsional spring torque must not exceed the braking torque, so that the final pivoting of the pivoting unit is achieved by an external actuating force, for example, by a user. In other words, the pivoting mechanism is designed, for example, to prevent automatic, unwanted, or unintentional movement or pivoting of the pivoting unit around its pivot axis by means of the helical spring unit—especially by means of its compression spring action—while still supporting the pivoting of the pivoting unit from its first end position toward its second end position by means of the helical spring unit—especially by means of its torsional spring action. This provides a particularly advantageous and safe way to adjust or move a flap element equipped with the pivoting mechanism.

[0019] In particular, the end positions between which the pivoting unit is adjustable are separated by an angle of more than 90 degrees along the outer circumference of the shaft. Specifically, the two end positions are separated by 135 degrees along the outer circumference of the shaft. This advantageously results in a particularly large adjustment range for the pivoting unit and, if applicable, for the flap element attached to or arranged on it. Particularly with respect to an XY plane of the motor vehicle equipped with the joint device or flap unit, the pivoting unit, and especially its lever component, is arranged parallel to this XY plane in the first end position, i.e., it is adjusted or pivoted by 0 degrees about the pivot axis or about the shaft. In simplified terms, in the first end position, the pivoting unit or its lever component is arranged horizontally with respect to the motor vehicle.In contrast, the swivel unit, and in particular its lever component, is adjusted by more than 90 degrees, especially by 135 degrees, relative to the swivel axis or shaft in the second end position. This second end position is particularly advantageous when the swivel unit (possibly including the flap element) is located between two individual seats of the vehicle, for example, as part of a center console. This is because, if the user of the joint or the flap unit equipped with the joint is able to swivel the unit by more than 90 degrees, the user will not inadvertently collide with the swivel unit, and especially not with the flap element attached to it, with their arm facing the joint. Accordingly, the joint enables particularly ergonomic and advantageous operation of the flap unit or the flap element.

[0020] According to a further advantageous embodiment of the joint device, a first intermediate pivot position is arranged between the first end position and the second end position. This intermediate position is located less than 45 degrees away from the first end position along the outer circumferential direction of the shaft. In particular, the intermediate position angle is less than 30 degrees, preferably 20 to 25 degrees. The pivot unit is held in the first intermediate pivot position by means of the helical spring unit along the torsional tension direction of the helical spring unit.Since – as explained above – in the first end position the coil spring unit is tensioned along the torsional tension direction between the pivot unit, in particular its lever arm, and the support element, this means that the first intermediate pivot position is reached when the torsional spring moment of the coil spring unit and a counter-torque cancel each other out. The counter-torque is the sum of the mass-related torque of the pivot unit (possibly including the flap element) that opposes the torsional spring moment and the braking torque generated by the brake unit.

[0021] Thus, the mass and the pivot unit, in particular the lever component (possibly including the flap element attached to it), the shape of the brake structures, and both a torsional spring constant and a translational spring constant of the helical spring unit correspond to each other in such a way that, in the intermediate pivot position, the torsional spring moment, the torque of the pivot unit, and the braking torque cancel each other out. In other words, when the helical spring unit is at least partially relaxed relative to the first end position, the pivot unit is held in the intermediate pivot position because the resulting torque acting on the pivot unit is zero.

[0022] In this context, it is particularly preferred if, due to a relaxation of the helical spring unit against the direction of torsional tension, i.e. in the direction of torsional relaxation, the pivoting unit can be pivoted into the first intermediate pivoting position.

[0023] In particular, the translational spring constant is selected or designed such that the braking torque can be overcome by relaxing the helical spring unit, whereby the swivel unit can be swivelled automatically in the direction of the second end position - for example in the direction of the first intermediate swivel position and / or into the first intermediate swivel position - without an external actuating force applied to the joint device, such as by a user of the joint device.

[0024] In a further advantageous embodiment, the articulated device has a locking element by means of which the pivoting unit can be reversibly and non-destructively locked against pivoting from the first end position. For example, the locking element is arranged directly or indirectly on the pivoting unit. Furthermore, the locking element corresponds to another locking element arranged in / on the motor vehicle, wherein the locking elements are designed, in particular, to provide a reversibly and non-destructively releasable connection device. This connection device is formed, for example, when the pivoting unit is arranged in the first end position, and the connection device can be opened, for example, by an actuation action of the user.It is specifically intended that - due to the user's action - the swivel unit will spring up from the first end position, in particular into the first intermediate swivel position, without any further action by the user, i.e., automatically.

[0025] During operation of the articulated device, the swivel unit is pivoted out of its first end position by releasing or unlocking the connecting device. This is because the swivel unit is driven by the relaxing helical spring unit along the outer circumference of the shaft, or in the direction of torsional relaxation, until the torsional spring torque of the helical spring unit balances the opposing torque (torque of the swivel unit + braking torque).

[0026] Furthermore, the connecting device is designed to be unlocked via an actuating element by applying an actuating force of at least 5 N (Newtons) and at most 25 N over an actuating path of 5 mm (millimeters). This actuating path is parallel to a longitudinal axis (x) of the vehicle, particularly in relation to the vehicle's coordinate system. The actuating element may be attached to the flap element or to / in the vehicle, but in any case, it is within reach of the user of the articulated device or the vehicle.

[0027] This ensures particularly efficient adjustment of the swivel unit of the joint device, requiring the user only to open the connecting device, at which point the swivel unit springs open from the first position. Specifically, the swivel unit – and in particular the attached flap element – ​​springs open far enough that the user can easily grasp the flap element with one hand (especially while wearing gloves) and pivot it further towards the second end position.

[0028] According to a further embodiment of the joint device, a second intermediate pivot position is arranged between the first end position and the second end position. This second intermediate position is located along the outer circumference of the shaft by a second intermediate position angle of more than 45 degrees from the first end position. With respect to the outer circumference of the shaft, i.e., with respect to the first end position, the second intermediate pivot position is located between the first intermediate pivot position and the second end position. It is particularly preferred if the second intermediate position angle is 90 degrees.

[0029] The shaft and the helical spring assembly are arranged coaxially. This means that the longitudinal center axis of the shaft and a longitudinal center axis of the helical spring assembly coincide. The shaft is encompassed by the helical spring assembly, specifically by a helical portion of the spring assembly, along its outer circumference. In the assembled state of the joint, the shaft extends through the spring's interior space. This interior space is defined radially outwardly by the coils of the helical spring assembly. The spring's interior space—considering only the helical spring assembly or its helical portion—is free of any material. This arrangement offers a space-saving advantage, as the helical spring assembly and the shaft are positioned in a particularly space-efficient manner.

[0030] According to a further embodiment of the joint device, the brake unit is arranged along the shaft, or along the longitudinal direction of the shaft, directly between the coil spring unit and the pivot unit. In this case, the joint device, and in particular the brake unit, has a second brake structure that is movably arranged along the shaft, or along the pivot axis, subject to translational tensioning or relaxation of the coil spring unit. In contrast, the first brake structure, which is opposite to the second brake structure along the pivot axis, or along the shaft of the first brake structure, is fixed translationally with respect to the shaft. This means that the coil spring unit is fixed opposite to the translational tensioning direction.In the translational relaxation direction, the first brake structure rests directly against it, thereby tensioning it along the pivot axis towards the first brake structure, which is arranged to be fixed against displacement. In particular, this allows the pivot unit and the flap element to be attached to one another, especially as a single piece. Furthermore, it can be provided that the pivot unit is at least partially formed by the flap element. This advantageously results in a particularly simple and uncomplicated design of the joint device, especially the flap unit.

[0031] In an alternative embodiment of the joint device, the pivoting unit is arranged along the shaft, or along its longitudinal center axis, directly between the coil spring unit and the brake unit. Here, the first brake structure is designed to be translationally displaceable along the longitudinal center axis of the shaft, even when the coil spring unit is tensioned or relaxed. In contrast, in this second embodiment, the second brake structure is translationally fixed relative to the pivot axis, or relative to the longitudinal center axis of the shaft. For example, the second brake structure and the shaft are formed integrally.

[0032] It has proven advantageous for the joint device if one of the brake structures comprises a brake structure body, while the other brake structure comprises a corresponding brake structure body receptacle. This means that the brake structure body and the brake structure body receptacle correspond to each other in such a way that the brake structure body can be arranged, at least partially, within the brake structure body receptacle. Accordingly, when the joint device is fully assembled, the brake structure body engages with the brake structure body receptacle along the shaft, so that the brake structure body is encompassed by the brake structure body receptacle along the outer circumferential direction of the shaft. It is particularly intended that the brake structure body and the brake structure receptacle directly adjoin each other on the inside of the brake structure body receptacle.The brake structure body has an outer circumferential surface, while the brake structure body receptacle has an inner circumferential surface. These surfaces are parallel to each other when the joint device is mounted. This is because the brake structure body and the brake structure body receptacle are designed to slide against each other internally when the pivoting unit is rotated or adjusted. This means that the outer circumferential surface of the brake structure body and the inner circumferential surface of the brake structure body receptacle can have, or be formed from, the friction surfaces of the respective brake structure.

[0033] For example, the brake structure body and the brake structure body mount each have the shape of a right circular cylinder. Alternatively, it is conceivable that the brake structure body and the brake structure body mount each have the shape of a right truncated circular cone. Depending on the geometry or shape of the brake structure body mount and the brake structure body, a braking torque can be generated between the brake structures, opposing any pivoting of the pivoting unit. This braking torque then depends on a translational spring force or pressure effect of the helical spring unit, the respective coefficient of friction of the brake structures or friction surfaces, and the contact angle of the brake unit. In this context, a contact angle is understood to be an angle relative to the translational tension direction of the helical spring unit at which the brake structure and the brake structure body mount abut or are in contact with each other.In this way, the joint device, in particular the brake unit of the joint device, can be adapted to a predetermined or predeterminable application of the joint device in a particularly simple and cost-effective manner, for example by means of a corresponding selection of the shape of the brake structure body mount and the brake structure body.

[0034] Furthermore, it is advantageous for the articulated device if the brake unit comprises a pair of positive locking elements, consisting of a first and a second positive locking element. The first positive locking element is formed on the first brake structure and is therefore rotatable around the shaft or pivot axis, as the pivot unit is rotatable around the pivot axis. The second positive locking element is formed on the second brake structure and is therefore rotationally fixed to the shaft. The two positive locking elements correspond to each other to establish a reversibly non-destructively releaseable positive lock between the pivot unit and the shaft. Furthermore, the positive locking elements can be brought into engagement with each other—due to pivoting the pivot unit into a locking position—while simultaneously releasing the helical spring unit against the translational tension direction (i.e., into a third tension position).Furthermore, the positive locking elements can be separated from one another by pivoting the pivoting unit out of the positive locking position while simultaneously tensioning the helical spring unit in the translational tensioning direction (i.e., into a fourth tensioning position). It follows that the helical spring unit is adjustable between the first and second tensioning positions and simultaneously between the third and fourth tensioning positions when the pivoting unit is pivoted. The positive locking elements thus engage with one another, or rather, form a reversibly non-destructive positive lock, when the pivoting unit is pivoted into the positive locking position.In this way, a possibility is created to positively lock the swivel unit, in particular between the first end position and the second end position, so that the swivel unit in the positive locking position can be secured even more securely against unintentional or unwanted movement, in particular against falling shut.

[0035] In particular, the positive locking elements are arranged opposite each other along the pivot axis or along the translational clamping direction, so that the positive locking elements are directly clamped against each other in the positive locking position by means of the helical spring unit. This means that the positive locking elements are positively secured against each other in the positive locking position of the pivot unit by means of the helical spring unit, which presses the positive locking elements against each other or into each other along the translational release direction. In this way, the positive locking formed or that can be formed by the positive locking elements is reliably secured against unintentional loosening, making the pivot unit even more reliably reversible and lockable in the positive locking position.

[0036] Furthermore, according to another advantageous embodiment of the articulated device, the brake structures are spaced apart from one another along the shaft via one or more of the positive locking elements when the pivoting unit is arranged outside the positive locking position. In this case, the helical spring unit is under greater tension along the translational tension direction than in the positive locking position. Therefore, if the pivoting unit is arranged outside the positive locking position and / or is pivoted or rotated about the pivot axis outside the positive locking position, the brake structures, in particular the friction surfaces, no longer slide directly against each other, but rather indirectly via one or more of the positive locking elements. In other words, a positive locking element formed on the first brake structure slides over a friction surface of the brake unit formed on the second brake structure.Alternatively or additionally, a positive locking element formed on the second brake structure slides over a friction surface formed on the first brake structure. In this case, the friction surfaces of the brake structures are spaced apart from each other by the corresponding positive locking elements, with the helical spring unit tensioned in the translational tension direction. This results in a particularly low braking torque between the brake structures when the pivoting unit is positioned outside the positive locking position or is pivoted. Consequently, the pivoting unit can be pivoted about the pivot axis particularly easily, for example by the user, thereby preventing the pivoting unit from being unintentionally or unintentionally pivoted beyond the positive locking position.

[0037] In a particularly advantageous embodiment of the joint device, the pair of positive locking elements is designed such that the swivel unit can be reversibly and non-destructively locked in the first intermediate swivel position by means of the pair of positive locking elements. Alternatively or additionally, the pair of positive locking elements is designed such that the swivel unit can be reversibly and non-destructively locked in the second intermediate swivel position by means of the pair of positive locking elements. Accordingly, the joint device can have more than one pair of positive locking elements, for example, a first pair of positive locking elements assigned to the first intermediate swivel position and a second pair of positive locking elements assigned to the second intermediate swivel position. The user of the joint device, orThis allows the user of the flap unit equipped with the joint device to be provided with particularly efficient haptic feedback indicating the position at which the swivel unit is currently locking in or has locked in place.

[0038] Furthermore, it has proven advantageous for the joint device if a further, for example, third pair of positive locking elements is designed such that the swivel unit can be reversibly and non-destructively locked in the second end position, i.e., at 135 degrees, by means of the (third) pair of positive locking elements. Since the second end position is more than 90 degrees, in particular 135 degrees, away from the first end position along the outer circumferential direction of the shaft, the swivel unit can thus be effectively secured against further swiveling, i.e., beyond the second end position, by the pair of positive locking elements forming a positive connection with each other when the swivel unit has been swiveled into the second end position, i.e., by more than 90 degrees or 135 degrees, from the first end position.Alternatively or additionally, a further (fourth) pair of positive locking elements can be provided, by means of which the swivel unit can be reversibly and non-destructively locked in the first end position. In particular, it is conceivable that the locking device is formed by the (fourth) pair of positive locking elements, in which case the locking device is entirely part of the joint assembly.

[0039] The joint mechanism can be designed to include a flap element attached to the pivot unit. This flap element could be, for example, a flap element of an interior component of the vehicle, such as an armrest. This armrest is adjustable / pivotable, as the pivot unit is adjustable between its end positions. Alternatively or additionally, the flap element could be designed as a cover element, for example, for a storage compartment in the vehicle. In this case, the first end position of the pivot unit corresponds to a closed position of the cover element, in which the access opening of the storage compartment is blocked by the cover element to prevent access. If the pivot unit or...When the cover element is moved out of the first end position, for example into the first pivot intermediate position, into the second pivot intermediate position or into the second end position, the cover element is moved into an open position in which the access opening for reaching through is at least partially released.

[0040] The invention further relates to a flap unit for a motor vehicle, wherein the flap unit comprises a joint device designed according to the preceding description.

[0041] Further advantages, features, and details of the invention can become apparent from the following description of possible embodiments and from the drawings. The features and combinations of features mentioned above in the description, as well as those shown below in the figure description and / or in the figures themselves, can be used not only in the combinations specified, but also in other combinations or individually, without departing from the scope of the invention. Brief character description

[0042] The drawing shows in Fig. 1 a schematic diagram of a first embodiment of a flap unit comprising a hinge device; Fig. 2 a schematic diagram of a further embodiment of the flap unit comprising the hinge device; Fig. 3 a perspective view of the flap unit with the hinge device; Fig. 4 a side view of the flap unit, wherein a pivoting unit is shown in a first end position, in a first intermediate pivot position, in a second intermediate pivot position and in a second end position; Fig. 5 a side view of the flap unit with the hinge device; Fig. 6 a top view of the flap unit with the hinge device; Fig. 7 a sectional side view (rear view) of the flap unit comprising the hinge device; Fig. 8 a perspective view of the flap unit, wherein the hinge device comprises a pair of positive locking elements; and Fig. 9 a detailed view of the pair of positive locking elements of the hinge device.

[0043] In the figures, identical / functionally equivalent elements are provided with the same reference symbols.

[0044] The foregoing description describes a joint device 1 and a flap unit 2 together, with particular emphasis on the fact that the flap unit 2 comprises the joint device 1. The flap unit 2 is intended, in particular, for a motor vehicle (not shown), which is designed, for example, as a passenger car and / or truck. The flap unit 2, and consequently the joint device 1, can be arranged, or is arranged, in the interior of a motor vehicle, this interior being designed, for example, as a passenger compartment or passenger cell.

[0045] The flap unit 2 is together with the joint device 1 in Fig. 1Figure 1 shows a schematic diagram of a first embodiment of the flap unit 2 comprising the hinge device 1. The hinge device 1 has a shaft unit 3 which includes a shaft 4 that is rotationally fixed to a shaft receptacle 5 (see Figure 1). Fig. 3 ) is connectable. In the present example, the shaft 4 is elongated and straight, circularly cylindrical. A pivot axis 7 of the joint device 1 is formed by a longitudinal center axis 6 of the shaft 4. This means that the joint device 1 has the pivot axis 7, whereby the pivot axis 7 and the longitudinal center axis 6 of the shaft 4 coincide.

[0046] Furthermore, the joint device 1 has a support unit 8 fixedly arranged on the shaft, which comprises a support element 9 or a plurality of support elements 9. In the present example, the support element 9 is designed as a support pin, the support pin extending transversely away from the shaft 4. This means that a distal end of the support pin or the support element 9 projects radially beyond an outer circumferential surface 10 of the shaft 4.

[0047] The joint device 1 further comprises a pivoting unit 11 pivotably arranged on the shaft 4, which includes a hub portion 12 arranged on the shaft and a lever portion 13 directly connected to the hub portion 12. The lever portion 13 is arranged transversely to the shaft 4, or transversely to the longitudinal center axis 6 – i.e., transversely to the pivot axis 7. The pivoting unit 11 is pivoted about the shaft 4, in particular about its longitudinal center axis 6, between a first end position P1 (see Fig. 4) and a second end position P2 (see Fig. 4 ) swiveling or rotatable.

[0048] It is also in Fig. 1 The figure shows that a flap element 14 is arranged on the pivoting unit 11, in particular on its lever component 13. The flap element 14 is in Fig. 1 (and in Fig. 2 ) shown transparently and only indicated. Furthermore, the flap element 14 is pivotably arranged with respect to the shaft 4 or with respect to the longitudinal center axis 6, that is, with respect to the pivot axis 7, and in particular, it may be provided that the flap element 14 is arranged to be fixed against displacement along the shaft 4 or along the longitudinal center axis 6. In the present case, the flap element 14 is a cover element 15 of a storage compartment 16 or for the storage compartment 16 (see Fig. 3The flap element 14 is, in particular, a flap element of the flap unit 2, which can, for example, be an interior element of the motor vehicle. For example, the flap unit 2 is arranged in / on a center console in the interior of the passenger car and / or the center console is at least partially formed by the flap unit 2. In particular, it can be provided that the flap unit 2, and especially the flap element 14, has a support surface 17, which is designed, in particular, as an armrest surface. Accordingly, a user of the flap unit 2, for example, a driver of the passenger car, is able to rest their arm on the flap unit 2 via the support surface 17. It is particularly preferred if the flap element 14 forms both the cover element 15 and the support surface 17, so that the flap unit is particularly flexible.It can be used in a variety of ways in the interior of passenger cars.

[0049] The joint device 1 further comprises a brake unit 18, which includes a first brake structure 19 and a second brake structure 20. The first brake structure 19 is attached to, or fixed to, the hub portion 12 of the pivot unit 11. Accordingly, the first brake structure 19 is pivotably or rotatably mounted on the shaft 4 with respect to the pivot axis 7 of the joint device 1. For example, the first brake structure 19 can pivot with the pivot unit 11 or its hub portion 12 by allowing the pivot unit 11 to pivot about the shaft 4 or about the pivot axis 7. The second brake structure 20 is rotationally fixed to the shaft 4 with respect to the pivot axis 7. The two brake structures 19 and 20 are, as shown in the figure... Fig. 1 as emerges, arranged opposite each other or in opposite directions along wave 4.

[0050] Furthermore, the joint device 1 has a helical spring unit 21 comprising a first end 22 and a second end 23 opposite the first end 22. At the first end 22, the helical spring unit 21 has a first end leg 24, and at the second end 23, the helical spring unit 21 has a second end leg 25. Between the ends 22, 23 and between the end legs 24, 25, the helical spring unit 21 has a helical portion 26, the helical portion 26 extending between the ends 22, 23. In other words, the helical portion 26 is bounded on both sides by the ends 22, 23 along a translational tension direction 27 of the helical spring unit 21. The coil spring unit 21 is further arranged along a torsional tension direction 28 of the coil spring unit 21 directly on the support unit 8 and on the swivel unit 11 and is tensioned in the first end position P1.Here, the pivoting unit 11, in particular its lever component 13, is tensioned by means of the helical spring unit 21 along an outer circumferential direction of the shaft 4 in the torsional tension direction 28. This means that, with the joint device 1 fully assembled, the helical spring unit 21 cannot be released in the opposite direction of the torsional tension 28 when the pivoting unit 11 is in the first end position P1. Furthermore, the helical spring unit 21, in particular its helical component 26, is arranged between the support unit 8 and the brake unit 18, and is clamped between the support unit 8 and the brake unit 18 along the translational tension direction 27. As a result, the brake structures 19, 20 are tensioned towards each other by means of the helical spring unit 21 along the shaft 4, i.e., along a longitudinal direction of the shaft 4, in the opposite direction of the translational tension 27.

[0051] By arranging the helical spring unit 21, in particular via its second end leg 25, on the pivot unit 11 or on its lever arm 13, and by the helical spring unit 21 being tensioned against relaxation in the torsional tension direction 28, the helical spring unit 21 can be relaxed against the torsional tension direction 28 by pivoting the pivot unit 11 about the pivot axis 7 against the torsional tension direction 28. This means that the helical spring unit 21 is relaxed against the torsional tension direction 28 when the pivot unit 11 is disengaged from the first end position P1 by pivoting the pivot unit 11 from the first end position P1 towards the second end position P2 about the shaft 4.

[0052] Furthermore, the brake structures 19, 20 are tensioned towards each other along the shaft 4 by means of the helical spring unit 21, since the translational tension direction 27 and the shaft 4, or rather its longitudinal center axis 6, are arranged parallel to each other. The helical spring unit 21 is supported at its first end 22 along the shaft 4 against the support unit 8, and at its second end 23 against the brake unit 18, in particular against a portion of the brake unit 18 that is translationally displaceable along the shaft 4. In this state, the helical spring unit 21 is tensioned between the brake unit 18 and the support unit 8 in the translational tension direction 27, so that a translational spring force acting along the longitudinal center axis 6 tensions the brake structures 19, 20 against each other. This is because one of the brake structures 19, 20 is rotationally fixed to the shaft 4 with respect to the pivot axis 7 of the joint device 1.

[0053] According to a first alternative of the joint device 1 or the flap unit 2, the second brake structure 20 is arranged to be translationally displaceable on the shaft 4 with respect to the shaft 4 or its longitudinal center axis 6. In contrast, the first brake structure 19 is in this case translationally fixed or displaceable, i.e., translationally immovable, attached to the shaft 4 along its longitudinal center axis 6, by means that the pivot unit 11 is arranged on the shaft 4 in a displacement-resistant manner with respect to the longitudinal center axis 6. Alternatively or additionally, the flap element 14 is rotatable about the longitudinal center axis 6, but translationally fixed to the shaft 4 with respect to the longitudinal center axis 6. In simplified terms, the second brake structure 20 is tensioned by means of the helical spring unit 21 against the translational tension direction 27 and along the shaft 4 in the direction towards the first brake structure 19 or against it.

[0054] Fig. 2shows a schematic diagram of a further embodiment or a second alternative of the flap unit 2 comprising the hinge device 1. In contrast to the one according to Fig. 1 The developed design of the joint device 1 is according to this alternative (see Fig. 2In one alternative of the joint 1, the first brake structure 19 is provided to be translationally displaceable on the shaft 4 with respect to the longitudinal center axis 6. In contrast, according to the second alternative of the joint 1, the second brake structure 20 is provided to be rotationally and translationally fixed on the shaft 4. In this case, the brake structures 19 and 20 are tensioned against each other by means of the helical spring unit 21, whereby the translational spring force pushes the pivot unit 11 along the longitudinal center axis 6 towards the second brake structure 20. This is because, according to the second alternative of the joint 1, the helical spring unit 21 is then arranged directly between the support unit 8 and the pivot unit 11, to which – as already explained above – the first brake structure 19 is attached or fixed.

[0055] A review of the Fig. 1 with the Fig. 2It becomes clear that at least two different arrangements of the elements of the joint device 1 are conceivable. Starting from the support unit 8 and extending along the longitudinal center axis 6 or pivot axis 7, it is conceivable, firstly, that the coil spring unit 21 is arranged after the support unit 8, followed by the pivot unit 11, and then the brake unit 18. In other words, it is intended that the pivot unit 11 is arranged along the shaft 4 directly between the coil spring unit 21 and the brake unit 18. Secondly, it is conceivable that the coil spring unit 21 is arranged after the support unit 8, followed by the brake unit 18, and then the pivot unit 11. This means that the brake unit 18 is arranged along the shaft 4 directly between the coil spring unit 21 and the pivot unit 11.The two alternatives of the joint device 1 are functionally identical, so the following applies to both alternatives in an analogous manner, if necessary.

[0056] Fig. 3 Figure 1 shows a perspective view of the flap unit 2 with the hinge device 1, wherein the flap unit 2, in particular the flap element 14, is shown partially broken out. Fig. 3The pivoting unit 11 and, accordingly, the flap element 14 attached to it are positioned in the first end position P1, such that an access opening 29 of the storage compartment 16 is blocked against access by the flap element 14 or by the cover element 15. This means that the first end position P1 can be a closed position of the flap element 14 or the cover element 15. In other words, the access opening 29 of the storage compartment 16 is completely closed by means of the cover element 15 or the flap element 14 when the pivoting unit 11 is positioned in the first end position P1. In particular, the joint device 1 and the flap unit 2 are designed so that the pivot unit 11 can be locked or secured in the first end position P1, for example by means of a locking device (not shown), so that the pivot unit 11 can be reversibly and non-destructively locked in the first end position P1.

[0057] Furthermore, in Fig. 3 It can be seen that the brake structures 19, 20 are tensioned towards each other by means of the helical spring unit 21 along the shaft 4, that is, along the pivot axis 7. In the first end position P1, the helical spring unit 21 generates a translational spring force that acts against the translational tension direction 27. It can therefore be seen that the helical spring unit 21 is clamped along the shaft 4 between the support unit 8 and the brake unit 18, thereby driving the pivot unit 11 and consequently the first brake structure 19, which is fixed to it, along the longitudinal center axis 6 towards the second brake structure 20. In the fully assembled state of the joint device 1 or the flap unit 2, the brake structures 19, 20 are therefore in direct contact with each other and – when the pivot unit 11 is pivoted about the pivot axis 7 – rub against each other. This rubbing generates a braking torque 30 (see Fig. 5 ) is generated, which is oriented against the pivoting of the pivoting unit 11. In other words, the braking torque 30 opposes the pivoting of the pivoting unit 11, for example, when the pivoting unit 11 is pivoted from the first end position P1 towards the second end position P2. Since the coil spring unit 21 is furthermore clamped in the torsional tension direction 28 between the pivoting unit 11 and the rotationally fixed support unit 8 on the shaft 4, the coil spring unit 21 exerts a torsional spring torque 31 (see Fig. 5 ) on the pivoting unit 11, whereby the pivoting unit 11 is driven out of the first end position P1 by means of the torsional spring moment 31, in particular when the pivoting unit 11 is no longer locked in the first end position P1.

[0058] The helical spring unit 21 thus has a dual function. On the one hand, the helical spring unit 21 generates the torsional spring moment 31, and on the other hand, it generates the translational spring force. This means that the helical spring unit 21 has both a translational spring constant and a torsional spring constant. The translational spring constant and the torsional spring constant are designed and selected such that the braking torque 30 is overcome by the torsional spring moment 31 for at least a portion of the pivoting travel of the pivoting unit 11 between the end positions P1 and P2. This results in the pivoting unit 11 being able to rotate about the shaft 4 or about the pivot axis 7 at least as far as...The pivoting motion continues at least until the torsional spring moment 31 and a counter-torque cancel each other out. The counter-torque is the sum of the braking torque 30 acting against the torsional spring moment 31 and a mass-related torque of the pivoting unit 11 (possibly including the flap element 14).

[0059] Fig. 4 Figure 1 shows a side view of the flap unit 2, with the pivot unit 11 depicted in the first end position P1, in the second end position P2, in a first intermediate pivot position P3, and in a second intermediate pivot position P4. The joint device 1, or flap unit 2, is designed so that the first end position P1 (see Figure 1) is... Fig. 3) corresponds to an angular position of the pivoting unit 11 of 0 degrees. Furthermore, the second end position P2 of the joint device 1 is reached when the pivoting unit 11 – starting from the first end position P1 – is pivoted by more than 90 degrees, in particular 135 degrees, about the shaft 4 or about the pivot axis 7. Between the first end position P1 and the second end position P2, the first intermediate pivot position P3 is provided, which in this example is reached when the pivoting unit 11 or the flap element 14 – starting from the first end position P1 – is pivoted by less than 45 degrees. In this example, the first intermediate pivot position P3 of the joint device 1 is reached when the pivoting unit 11 or the flap element 14 is pivoted by less than 30 degrees, preferably by 20 degrees to 25 degrees, and even more preferably by exactly 25 degrees, from the first end position P1.The joint device 1 further comprises the second pivot intermediate position P4, which is arranged between the first end position P1 and the second end position P2, in particular between the first pivot intermediate position P3 and the second end position P2. In this case, the pivot unit 11 or the flap element 14 is arranged in the second pivot intermediate position P4 when the pivot unit 11 or the flap element 14 has been pivoted 90 degrees about the pivot axis 7 from the first end position P1.

[0060] In connection with the first intermediate pivot position P3, the joint device 1 is designed such that the pivot unit 11 and / or the flap element 14 attached to it are held in the first intermediate pivot position P3 by means of the helical spring unit 21. In other words, it is designed that in the first intermediate pivot position P3, the torsional spring torque 31, the braking torque 30, and the mass-related torque of the pivot unit 11 cancel each other out, resulting in a net torque of zero acting on the pivot unit 11 or on the flap element 14 with respect to the pivot axis 7 in the first intermediate pivot position P3. This means that the pivot unit 11 or the flap element 14 attached to it is held automatically in the first intermediate pivot position P3 without the application of an external force or torque.

[0061] Furthermore, it is provided that the pivoting unit 11, and in particular the flap element 14 arranged thereon, can be pivoted out of the first end position P1 due to the relaxation of the helical spring unit 21 against the direction of torsional tension. This means that—especially after unlocking the flap element 14 or the pivoting unit 11—the helical spring unit 21 is relaxed against the direction of torsional tension 28, whereby the corresponding torsional spring moment 31 overcomes the braking moment 30, in particular until the pivoting unit 11 or the flap element 14 is in the first intermediate pivot position P3. This means that the pivoting unit 11 can be pivoted automatically from the first end position P1 to the first intermediate pivot position P3. For this purpose, only the locking device—if present—needs to be released, for example, by a user.

[0062] Fig. 5shows a side view of the flap unit 2 with the hinge device 1, where the flap unit 2 is shown partially broken out. In Fig. 5 It is particularly evident that the shaft 4 extends through the helical spring assembly 21, specifically through its helical portion 26. This is because the shaft 4 is encompassed by the helical portion 26 in the outer circumferential direction of the shaft 4, with the shaft 4 passing through a spring clearance 32 of the helical spring assembly 21. In particular, the shaft 4 and the helical portion 26 of the helical spring assembly 21 are arranged coaxially with each other. This means that a longitudinal center axis of the helical spring assembly 21 and the longitudinal center axis 6 of the shaft 4 coincide. The translational tension direction 27, the torsional tension direction 28, the braking torque 30, and the torsional spring torque 31 are indicated by the corresponding arrows in the figure. Fig. 5 marked.

[0063] In Fig. 6The flap unit 2 with the joint device 1 is shown in a top view, with the flap unit 2 shown partially cut away. The brake structures 19, 20 each have a friction surface 33, 34, which – for example, as the respective brake structures 19, 20 – face each other or are opposite each other. This means that the friction surfaces 33, 34, for example in the first end position P1, are tensioned towards each other by means of the helical spring unit 21, specifically along the pivot axis 7 or along the longitudinal center axis 6.

[0064] Fig. 7 shows a sectional side view (rear view) of the flap unit 2, which includes the hinge device 1. The corresponding section plane VII-VII is shown in Fig. 6 depicted. In Fig. 7The figure shows that the brake unit 18 has a brake structure body 35 and a brake structure body receptacle 36. The brake structure body 35 and the brake structure body receptacle 36 correspond to each other, such that in the assembled state of the joint device 1, the brake structure body 35 is arranged within the brake structure body receptacle 36. In other words, the brake structure body 35 is received in the brake structure body receptacle 36. In this case, the brake structure body 35 and the brake structure body receptacle 36 each have the shape of a straight circular cylinder. Alternatively, it is conceivable that the brake structure body 35 and the brake structure body receptacle 36 each have the shape of a straight truncated circular cone. In any case, the brake structure body 35 engages along the shaft 4.The brake structure body 35 engages in the brake structure body receptacle 36 along the longitudinal center axis 6 and / or along the pivot axis 7, such that the brake structure body 35 is encompassed by the brake structure body receptacle 36 along the outer circumferential direction of the shaft 4. In particular, the brake structure body 35 is completely encompassed by the brake structure body receptacle 36 along the outer circumferential direction of the shaft 4. When the pivoting unit 11 or the flap element 14 pivots about the pivot axis 7 of the joint device 1, an outer circumferential surface of the brake structure body 35 and an inner circumferential surface of the brake structure body receptacle 36 slide against each other, with friction occurring between the inner circumferential surface of the brake structure body receptacle 36 and the outer circumferential surface of the brake structure body 35. This friction, i.e., when the pivoting unit 11 pivots about the pivot axis 7, generates at least part of the braking torque 30.By appropriately selecting a specific geometry for the brake structure body receptacle 36 and / or the brake structure body 35, it is possible to influence the braking torque 30, particularly during the manufacture of the joint device 1. In other words, the braking torque 30 depends at least partially on a selected or designed geometry of the brake structure body receptacle 36 and / or the brake structure body 35.

[0065] Fig. 8Figure 1 shows a perspective view of the flap unit 2, where the joint device 1 comprises a pair of positive locking elements 37. The pair of positive locking elements 37 has a first positive locking element 38 and a second positive locking element 39. The first positive locking element 38 is formed on the first brake structure 19, while the second positive locking element 39 is formed on the second brake structure 20. The pair of positive locking elements 37 is configured to form a reversibly non-destructively releasable positive lock. This means that the positive locking elements 38 and 39 correspond to each other to close, or form, the reversibly non-destructively releasable positive lock between the pivot unit 11 and the shaft 4. In this example, the first positive locking element 38 formed on the first brake structure 19 projects beyond the first friction surface 33 in the direction of the second brake structure 20.In contrast, the second positive locking element 39 is designed as a recess in the second friction surface 33 of the second brake structure 20. The shape of one of the positive locking elements 38, 39 is designed as a negative of the shape of the corresponding other positive locking element 38, 39, thus enabling one of the positive locking elements 38, 39 to engage with the other. Fig. 8The positive locking elements 38 and 39 are arranged far apart because the pivoting unit 11 is pivoted by 0 degrees relative to the shaft 4, i.e., it is in the first end position P1. Due to pivoting the pivoting unit 11, and in particular by simultaneously releasing the helical spring unit 21 against the translational tension direction 27, the two positive locking elements 38 and 39 can be brought into engagement with each other, thereby closing the positive locking connection between the pivoting unit 11 and the shaft 4. In this state, the pivoting unit 11 is in a positive locking position. This positive locking position is specifically located between the first end position P1 and the second end position P2.Since the positive locking mechanism mediated by the positive locking elements 38, 39 is designed to be reversibly and non-destructively detachable, the positive locking elements 38, 39 can be detached from each other by pivoting the pivoting unit 11 out of the positive locking position, while simultaneously tensioning the helical spring unit 21 in the translational tension direction 27. This is because, due to the triangular cross-sectional shape of the respective positive locking elements 38, 39, the positive locking elements 38, 39 slide against each other as the helical spring unit 21 relaxes, thereby engaging one another. In the present example, by pivoting the swivel unit 11 about the pivot axis 7, the first positive locking element 38 is initially rotated in the direction towards the second positive locking element 39, until the first positive locking element 38 engages in the second positive locking element 39 and the positive locking elements 38, 39 slide against each other on their flanks.As the positive locking elements 38, 39 slide against each other, the helical spring unit 21 relaxes in the opposite direction of translational tension 27, whereby the two positive locking elements 38, 39 are moved closer together. Since the first positive locking element 38 and the pivot unit 11, in particular its hub portion 12, are connected to each other, for example, are formed integrally, the pivot unit 11 is displaced translationally along the pivot axis 7 towards the second brake structure 20 as the helical spring unit 21 relaxes. This means that, as long as the pivot unit 11 is not in the positive locking position, the brake structures 19, 20, in particular their friction surfaces 33, 34, are spaced apart from each other along the shaft 4 or along its longitudinal center axis 6 by one of the positive locking elements 38, 39.In this state, the helical spring unit 21 is under greater tension along the translational tension direction 27 than in the positive locking position. This means that the positive locking elements 38, 39 are secured in the positive locking position by the translational spring force of the helical spring unit 21. Nevertheless, the positive locking can be released particularly easily by moving the pivoting unit 11 out of the positive locking position, thereby tensioning the helical spring unit 21 along the translational tension direction 27. This forming and releasing of the positive locking between the shaft 4 and the pivoting unit 11 is described in [reference missing]. Fig. 9 shown, which is a detailed view of the positive locking element pair 37 of the joint device 1.

[0066] In particular, the positive locking elements 38, 39 are arranged such that the swivel unit 11 can be reversibly and non-destructively locked in the first intermediate swivel position P3 by means of the positive locking element pair 37. Furthermore, a (further) positive locking element pair can be provided by means of which the swivel unit 11 can be reversibly and non-destructively locked in the second intermediate swivel position P4. A further positive locking element pair is also conceivable by means of which the swivel unit 11 can be reversibly and non-destructively locked in the second end position P2. This means that the joint device 1 can have more than the positive locking element pair 37. For example, the joint device 1 can comprise a plurality of positive locking element pairs, so that the swivel unit 11 can be reversibly and non-destructively released and positively locked in a plurality of positive locking positions.It is particularly advantageous if the joint device 1 or the brake unit 18 has a plurality of positive locking elements on the second brake structure 20, which is non-rotatably connected to the shaft 4, whereas only a single positive locking element is formed on the first brake structure 19, which is fixed to the swivel unit 11, and which corresponds to the positive locking elements on the second brake structure 20. REFERENCE MARK LIST

[0067] 1 Joint device 2 Flap unit 3 Shaft unit 4 Shaft 5 Shaft mount 6 Longitudinal center axis 7 Swivel axis 8 Support unit 9 Support element 10 Outer circumferential surface 11 Swivel unit 12 Hub section 13 Lever section 14 Flap element 15 Cover element 16 Storage compartment 17 Support surface 18 Brake unit 19 Brake structure 20 Brake structure 21 Coil spring unit 22 End 23 End 24 End leg 25 End leg 26 Helix section 27 Translational tension direction 28 Torsional tension direction 29 Engagement opening 30 Braking torque 31 Torsional spring torque 32 Spring clearance 33 Friction surface 34 Friction surfaces 35 Brake structure body 36 Brake structure body mount 37 Positive locking element pair 38 Positive locking element 39 Positive locking element P1 End position P2 End position P3 Intermediate swivel position P4 Intermediate swivel position

Claims

1. Articulation device (1) for a flap unit (2) of a motor vehicle, having - a shaft (4) which is connectable to a shaft receptacle (5) of the motor vehicle for conjoint rotation; - a support unit (8) fixedly arranged on the shaft (4); - a pivoting unit (11) which is pivotably arranged on the shaft (4) and is pivotable about the shaft (4) between a first end position (P1) and a second end position (P2); - a brake unit (18) which comprises a first brake structure (19) fixed on the pivoting unit (11) and a second brake structure (20) arranged on the shaft (4) for conjoint rotation, wherein the brake structures (19, 20) directly face each other along the shaft (4), - a helical spring unit (21) - which is arranged directly on the support unit (8) and on the pivoting unit (11) along a torsional loading direction (28) and is clamped in the first end position (P1) of the pivoting unit (11), wherein the pivoting unit (11) is loaded along an outer circumferential direction of the shaft (4) in the torsional loading direction (28) by means of the helical spring unit (21); and - which is arranged and clamped along a translational loading direction (27) between the support unit (8) and the brake unit (18), wherein the brake structures (19, 20) are loaded towards each other along the shaft (4) counter to the translational loading direction (27) by means of the helical spring unit (21), characterized in that a translatory spring force of the helical spring unit (21) is selected or configured in such a way that the brake structures (19, 20) are pressed so firmly against each other by means of the helical spring unit (21) that a brake torque in effect because of the loading of the brake structures (19, 20) against each other and a mass-induced torque of the pivoting unit (11) about the shaft (4) cancel each other out.

2. Articulation device (1) according to Claim 1, characterized in that between the first end position (P1) and the second end position (P2) there is a first pivoting intermediate position (P3) which is remote from the first end position (P1) along the outer circumferential direction of the shaft (4) by a first intermediate position angular dimension of less than 45 degrees, wherein, in the first pivoting intermediate position (P3), the helical spring unit (21) is used to hold the pivoting unit (11) in the first pivoting intermediate position (P3) along the torsional loading direction (28) of the helical spring unit (21).

3. Articulation device (1) according to Claim 2, characterized in that relaxation of the helical spring unit (21) counter to the torsional loading direction (28) causes the pivoting unit (11) to be pivoted out of the first end position (P1).

4. Articulation device (1) according to one of the preceding claims, characterized by a locking element, by means of which the pivoting unit (11) can be blocked in the first end position (P1) in a reversibly non-destructively releasable manner against pivoting out of the first end position (P1).

5. Articulation device (1) according to one of the preceding claims, characterized in that between the first end position (P1) and the second end position (P2) there is a second pivoting intermediate position (P4) which is remote from the first end position (P1) along the outer circumferential direction of the shaft (4) by a second intermediate position angular dimension of more than 45 degrees.

6. Articulation device (1) according to one of the preceding claims, characterized in that the brake unit (18) is arranged along the shaft (4) directly between the helical spring unit (21) and the pivoting unit (11).

7. Articulation device (1) according to one of Claims 1 to 5, characterized in that the pivoting unit (11) is arranged along the shaft (4) directly between the helical spring unit (21) and the brake unit (18).

8. Articulation device (1) according to one of the preceding claims, characterized in that one of the brake structures (19, 20) comprises a brake structure body (35), and the other of the brake structures (19, 20) comprises a corresponding brake structure body receptacle (36) in which the brake structure body (35) engages along the shaft (4), wherein the brake structure body (35) is engaged around by the brake structure body receptacle (36) along the outer circumferential direction of the shaft (4).

9. Articulation device (1) according to one of the preceding claims, characterized in that the brake unit (18) comprises a pair (37) of form-fitting elements, which comprises a first form-fitting element (38) formed on the first brake structure (19) and a second form-fitting element (39) formed on the second brake structure (20), wherein the form-fitting elements (38, 39) correspond with each other to close a reversibly non-destructively releasable form-fitting connection between the pivoting unit (11) and the shaft (4), and the form-fitting elements (38, 39) - can be brought into engagement with each other by pivoting of the pivoting unit (11) into a form-fitting position, with simultaneous relaxation of the helical spring unit (21) counter to a translational loading direction (27); and - can be released from each other by pivoting of the pivoting unit (11) out of the form-fitting position, with simultaneous loading of the helical spring unit (21) in the translational loading direction (27).

10. Articulation device (1) according to Claim 9, characterized in that the form-fitting elements (38, 39) are loaded directly onto each other in the form-fitting position by means of the helical spring unit (21).

11. Articulation device (1) according to Claim 9 or 10, characterized in that the brake structures (19, 20) are spaced apart from each other along the shaft (4) via one of the form-fitting elements (38, 39) when the pivoting unit (11) is arranged outside the form-fitting position, with the helical spring unit (21) being more heavily loaded along the translational loading direction (27) than in the form-fitting position.

12. Articulation device (1) according to Claim 2 and Claim 9, 10 or 11, characterized in that the pair (37) of form-fitting elements is designed in such a manner that the pivoting unit (11) can be reversibly non-destructively releasably locked in the first pivoting intermediate position (P3) by means of the pair (37) of form-fitting elements.

13. Articulation device (1) according to Claim 5 and one of Claims 9 to 12, characterized in that a further pair (37) of form-fitting elements is designed in such a manner that the pivoting unit (11) can be reversibly non-destructively releasably locked in the second pivoting intermediate position (P4) by means of the pair (37) of form-fitting elements.

14. Articulation device (1) according to one of Claims 9 to 13, characterized in that a further pair (37) of form-fitting elements is designed in such a manner that the pivoting unit (11) can be reversibly non-destructively releasably locked in the second end position (P2) by means of the pair (37) of form-fitting elements.

15. Flap unit (2) for a motor vehicle, having an articulation device (1) designed according to one of the preceding claims.