DE102018118126A1 - Drive arrangement for motorized adjustment of a flap of a motor vehicle - Google Patents

Abstract

The invention relates to a drive arrangement (1) for the motorized adjustment of a flap (2), in particular a boot lid, of a vehicle, the drive arrangement (1) being mounted for motorized adjustment on the flap (2) or on one of the flap (2). assigned swing arm, the drive arrangement (1) having a drive unit (4) with a drive (5) and the drive (5) a rotary motor unit (6) with an output shaft (7) and a motor unit (6) connected downstream, has a spindle (9) and a spindle nut gear mechanism (8) which is in meshing engagement therewith, for generating drive movements along the geometric spindle axis (X) of the spindle (9), between the motor unit (6) and that Spindle-spindle nut gear (8) is connected to a worm gear stage (11), which is a worm gear (12) coupled to the motor unit (6) by drive technology and which rotates around a first gear axis se (G) is rotatable, and has a worm wheel (13) which meshes with the worm (12) and which, driven by the worm (12), is rotatable about a second gear axis (G) which is transverse to the first gear axis runs, and wherein the motor unit (6), the worm gear stage (11) and the spindle-spindle nut gear (8) are arranged in a drive train of the drive arrangement (1). It is proposed that a separate functional element (16) is provided for transmitting a torque between the worm wheel (13) and the spindle nut (10), which is connected in terms of drive technology in the drive train between the worm wheel (13) and the spindle nut (10) and that with the spindle nut (10) is rotatably coupled.

Description

The invention relates to a drive arrangement for motorized adjustment of a flap, in particular a boot lid, of a motor vehicle according to the preamble of claim 1, a hinge arrangement with such a drive arrangement according to claim 15 and a flap arrangement with such a hinge arrangement according to claim 16.

In the context of increasing comfort in motor vehicles, the motorized adjustment of flaps is of particular importance. The flap is, for example, a boot lid. Other types of flaps in this sense are, for example, tailgates, bonnets, doors, in particular side or rear doors, or the like.

In the drive arrangement in question, there are various boundary conditions which at least partially contradict each other. A boundary condition is a high level of robustness even in the event of improper operation, in which the drive arrangement may have to withstand high forces acting on the flap without damage. At the same time, however, there is the boundary condition of a cost-effective implementation, so that high robustness with little use of materials is required. Finally, an optimal use of installation space is required so that the drive arrangement does not noticeably impair the space usable for the operator, in particular the luggage space.

The known drive arrangement ( DE 10 001 054 A1 ), from which the invention is based, is used for motorized adjustment of a tailgate or bonnet of a motor vehicle. The drive arrangement has a drive unit with a drive, which has a rotary motor unit and a spindle-spindle nut transmission connected downstream of the motor unit for generating linear drive movements. Due to the installation space, a worm gear stage is connected between the motor unit and the spindle-spindle nut transmission, so that the motor unit extends transversely to the spindle-spindle nut transmission. In order to transmit a torque between the motor unit and the spindle nut spindle gear, the worm gear stage has a worm driven on the motor side and a worm wheel meshing therewith, which is frictionally placed on the spindle nut. In this way, an overload clutch device is provided as a functional component, which is intended to prevent a maximum torque between the worm wheel and the spindle nut from being exceeded.

The known drive arrangement has the disadvantage that no separate functional component is provided which supports holding the tailgate or bonnet in an open position. The drive motor of the motor unit must do this by generating an appropriate torque.

The invention is based on the problem of designing and developing the known drive arrangement in such a way that functional components can be arranged taking into account the best possible use of installation space.

The above problem is solved in a drive arrangement according to the preamble of claim 1 by the features of the characterizing part of claim 1.

What is essential is the fundamental consideration of arranging both the worm wheel and the spindle nut in a first axial region with respect to the spindle axis, namely overlapping in the radial direction, thereby minimizing the axial installation space for these two drive sections. The terms “axial” and “radial” each refer to the spindle axis. At least one additional functional component can then be arranged in an axially offset second axial region, which couples the two drive sections, that is to say the worm wheel and the spindle nut, to one another in terms of drive technology. For this purpose, according to the proposal, a functional element is provided separately from the worm wheel and spindle nut, which, for coupling an additional functional component such as a braking device, overload coupling device or the like. serves and / or is itself part of such an additional functional component. In particular, several additional functional components, for example a braking device and an overload clutch device, can also be integrated into the drive train via the separate functional element arranged in the second axial area. The arrangement of the worm wheel and spindle nut in a first axial area and the functional components in a second axial area, which axially adjoins or axially overlaps the first axial area, makes it possible to achieve particularly compact installation solutions with respect to the axial direction or direction of travel of the spindle axis become.

Specifically, it is therefore proposed that a separate functional element be provided for transmitting a torque between the worm wheel and the spindle nut, which is connected in terms of drive technology in the drive train between the worm wheel and the spindle nut and which is coupled in a rotationally fixed manner to the spindle nut. In the proposed solution, a separation of the worm wheel and spindle nut and the torque transmission are deliberately provided provided between the worm wheel and spindle nut, at least significantly, via the separate functional element. The at least the usual proportion of the torque to be transmitted is thus first transmitted from the worm wheel to the functional element and from there to the spindle nut, or vice versa. At the same time, the functional element can be used to integrate one or more other functional components such as a braking device and / or overload clutch device in the drive train in the axial direction on the worm wheel and spindle nut unit.

According to the preferred embodiment according to claim 2, the worm wheel is axially movable relative to the spindle nut. "Axially fixed" means that the worm wheel is not deflected axially during operation, even in the event of an overload. By contrast, “axially movable” means that during operation, for example in the event of an overload, the worm wheel can be deflected axially relative to the spindle nut.

Claims 3 to 5 relate to an overload clutch device which can be connected as a functional component in the drive train in order to separate the drive train in the event of an overload in the drive train. In particular, in the event of an overload, this can release the rotationally fixed coupling of the worm wheel to the spindle nut, that is, it can disengage the worm wheel and the spindle nut. With a load below the overload limit, i.e. of the limit, the exceeding of which defines an overload, the rotationally fixed coupling between the worm wheel and the spindle nut via the functional element is maintained or restored after a previous release of the coupling due to an overload, so the worm wheel and the spindle nut are engaged again. The functional element is preferably part of the overload clutch device and is used to disengage the worm wheel and the spindle nut in the event of an overload. According to a preferred embodiment, the overload clutch device is a dog clutch (claim 4) and in a further preferred embodiment is a magnetic clutch (claim 5).

As a functional component that can be provided in addition or as an alternative to the overload clutch device, according to the preferred embodiments according to claims 6 to 8, a braking device is provided for braking at least part of the drive train. Part of the drive train that is braked by the braking device is in particular the spindle nut. Additionally or alternatively, part of the drive train that is braked can also be the worm wheel. Here too, the functional element preferably forms part of the braking device. The braking device is preferably a permanent brake, which therefore permanently exerts a braking effect on the part of the drive train to be braked, for example the spindle nut and / or the worm wheel (claim 7). Various configurations of the braking device are possible, for example an embodiment as a friction brake or eddy current brake or magnetic brake. The braking device preferably has at least one pair of friction surfaces or a plurality of pairs of friction surfaces, the latter in particular forming a multi-disc brake (claim 8). The separate functional element can be formed by one or more pairs of friction surfaces or at least form one friction surface of a pair of friction surfaces. The respective pair of friction surfaces can be preloaded on one another by means of a spring arrangement, wherein the spring arrangement can have one or more coil springs, in particular helical compression springs and / or wave springs, in particular shaft compression springs.

According to the further preferred embodiment according to claim 9, the overload clutch device and the braking device can also interact with one another, i.e. an actuation of the overload clutch device, in particular a deflection of the coupling parts forming the overload clutch device relative to one another, can influence, in particular increase, the braking effect. Disengaging the overload clutch device can also result in the braking device acting only on part of the drive train, for example only on the spindle nut or on the worm wheel.

Further preferred configurations of the spring arrangement are defined in claims 10 and 11.

According to the preferred embodiment according to claim 12, the drive has a drive housing with two mutually adjustable housing parts. In particular, the two housing parts, one of which can form a housing cover, are in screw engagement and / or in latching engagement with one another. The spring arrangement is particularly preferably supported axially on the one housing part, in particular the housing cover, which makes it possible to change the spring preload relative to one another via an axial adjustment movement of the two housing parts.

Claims 13 and 14 relate to an axial securing of the drive housing, which blocks or at least complicates an axial movement, in particular an adjusting movement, between the two housing parts mentioned. This applies in particular to an axial movement of one housing part, in particular the housing cover, relative to the other housing part axially towards the housing exterior, that is to say for example a unscrewing movement or an extraction movement. Particularly preferred embodiments of the axial securing are the subject of claim 14. For example, the screw thread can be direction-dependent and can be designed to be self-locking in a direction of rotation, which corresponds in particular to a unscrewing movement, which can be achieved, for example, by means of a sawtooth profile of at least one of the threads of the screw thread. It is also conceivable to provide barbs on the radially outer edge of one housing part, in particular the housing cover, or of a securing element axially securing it, in particular in the form of a serrated ring. It is also conceivable to provide a soft component that lies in the threads and makes it difficult or unsuccessful to unscrew. Furthermore, it is conceivable to radially spread a slotted housing part, in particular housing cover, with a grub screw, so that it is radially jammed in the other housing part. In principle, it is also conceivable to provide at least one locking screw as an axial securing device, which forms a positive connection between the housing parts.

According to a further teaching of independent importance, a hinge arrangement for a flap, in particular a trunk lid, of a motor vehicle is claimed as such. The proposed hinge arrangement has a hinge and a hinge pivot axis assigned to the hinge. A swing arm is coupled to the hinge, which is connected to the flap when assembled.

It is essential according to the further teaching that a proposed drive arrangement for motorized adjustment of the flap acts on the rocker. Reference may be made to all explanations of the proposed drive arrangement. The rocker can be designed between the hinge pivot axis and the flap as a curved section, in particular in the form of a circular section. This enables the drive connection, which otherwise connects the drive unit to the motor vehicle, to be moved forward, as seen in the longitudinal direction of the motor vehicle, without the cross member located between the rear window and the rear cover blocking a flap movement. The geometric surface spanned by the curved section of the rocker is preferably used by the drive unit in terms of installation space, so that an overall particularly compact arrangement results.

According to a further teaching according to claim 16, which is of independent importance, a flap arrangement as such is claimed which has a flap and a proposed hinge arrangement, the flap being connected to the rocker of the hinge arrangement. In this respect too, reference may be made to all explanations regarding the proposed drive arrangement and the proposed hinge arrangement. A high level of structural flexibility is preferably achieved in that a spring arrangement assigned to the flap is provided at least in part separately and spatially separated from the drive arrangement. The use of installation space can be further improved if the output axis of the motor unit and thus the motor unit as a whole is aligned horizontally.

• 1 den Heckbereich eines Kraftfahrzeugs mit einer vorschlagsgemäßen Klappenanordnung, die mit einer vorschlagsgemäßen Antriebsanordnung sowie mit einer vorschlagsgemäßen Scharnieranordnung ausgestattet ist,
• 2 die Antriebsanordnung gemäß 1 in einer ausschnittsweisen Darstellung,
• 3 eine vergrößerte, perspektivische Darstellung der Antriebsanordnung gemäß 1,
• 4 eine Schnittansicht des Antriebs der Antriebsanordnung gemäß 3 gemäß einem ersten Ausführungsbeispiel und
• 5 in a) eine Schnittansicht des Antriebs der Antriebsanordnung gemäß 3 gemäß einem zweiten Ausführungsbeispiel und in b) eine Schnittansicht des Antriebs der Antriebsanordnung gemäß 3 gemäß einem dritten Ausführungsbeispiel.

The invention is explained in more detail below on the basis of a drawing which only shows exemplary embodiments. In the drawing shows

• 1 the rear area of a motor vehicle with a proposed flap arrangement which is equipped with a proposed drive arrangement and with a proposed hinge arrangement,
• 2 the drive arrangement according to 1 in a partial representation,
• 3 an enlarged, perspective view of the drive assembly according to 1 .
• 4 a sectional view of the drive of the drive assembly according to 3 according to a first embodiment and
• 5 in a) a sectional view of the drive of the drive arrangement according to 3 according to a second exemplary embodiment and in b) a sectional view of the drive of the drive arrangement according to 3 according to a third embodiment.

The proposed drive arrangement 1 is used for motorized adjustment of a flap 2 a motor vehicle. The flap 2 is by means of the drive arrangement 1 in the opening direction and / or in the closing direction of the flap 2 adjustable.

At the fold 2 it is here and preferably a boot lid of the motor vehicle. The "trunk lid" application is for the proposed drive arrangement 1 Particularly advantageous because the space available there with the proposed drive arrangement 1 can be used particularly well. This is explained in more detail below.

Basically, the proposed drive arrangement can 1 but also on other types of flaps 2 of a motor vehicle. This includes tailgates, bonnets, doors, in particular side or rear doors or the like. Even sliding doors can at least be opened an adjustment range of the proposed drive arrangement 1 adjust by motor.

A synopsis of the 1 and 2 shows that the drive assembly 1 in the assembled state on one of the flaps 2 assigned swing arm 3 attacks. Basically, the drive arrangement 1 also directly on the flap 2 attack.

The drive arrangement 1 has a drive unit 4 with a drive 5 on. The drive 5 as such is in the perspective view 3 shown enlarged. Here and preferably is the flap 2 just a single drive unit 4 assigned. Basically you can shut up 2 but also two drive units 4 be assigned, each attacking one of two rockers arranged on opposite sides of the motor vehicle trunk. The two drive units 4 are then preferably identical to one another or mirror images of one another.

4 shows that the drive 5 a rotary motor unit 6 with an output shaft 7 having. In the present case, the term “rotary” means that the motor unit 6 via the output shaft 7 rotatory drive movements. In the illustrated and preferred embodiment, it is the output shaft 7 around the motor shaft of the motor unit 6 , Basically, it can also be provided that the motor unit 6 in addition to a drive motor also has a downstream intermediate gear, so that the output shaft 7 is accordingly part of the intermediate gear.

4 further shows that the motor unit 6 a spindle-spindle nut gear 8th for generating, here and preferably linear, drive movements. The spindle-spindle nut gear 8th has a spindle 9 on, in the usual way with a spindle nut 10 combs.

4 finally shows that between the motor unit 6 and the spindle-spindle nut gear 8th a worm gear stage 11 is switched. The worm gear stage 11 has one with the output shaft 7 coupled snail 12 and one with the snail 12 in a conventional manner also intermeshing worm wheel 13 that with the spindle nut 10 is connected to.

The snail 12 is about a first gear axis G ₁ and the worm wheel meshing with it 13 around a second gear axis G ₂ that are transverse and in particular orthogonal to the first gear axis G ₁ runs, rotatable.

The motor unit 6 who have favourited Worm gear stage 11 and the spindle-spindle nut gear 8th are in a drive train of the drive assembly 1 arranged to transmit torque from the motor unit 6 to the spindle 9 serves, which can be moved linearly and two drive connections 14a . 14b the drive arrangement 1 moved relative to each other in this way. The one drive connection 14a connects the spindle 9 swiveling with the flap 2 or, as is the case in the present exemplary embodiment, with that of the flap 2 assigned swing arm 3 while the other drive connector 14b the drive unit 4 , in particular via a drive housing 15 , pivotally connected to the motor vehicle.

It is now essential that to transmit a torque between the worm wheel 13 and spindle nut 10 a separate functional element 16 it is provided that in terms of drive technology in the drive train between the worm wheel 13 and the spindle nut 10 is switched and that with the spindle nut 10 is rotatably coupled. The functional element 16 , which will be described in more detail below, is arranged essentially to the side of the axial region in which the worm wheel is located, in relation to the axial direction in which the spindle axis X extends 13 and the coaxial rotatable spindle nut 10 are arranged ( 4 and 5 ).

The additional functional component 16 is here and preferably the element that is decisive for the torque transmission between the worm wheel 13 and spindle nut 10 is. worm 13 and spindle nut 10 are in direct contact with each other here, but this contact has no significant influence on the torque transmission here and preferably. For the sake of simplicity, it is assumed below that the torque transmission from the worm wheel 13 exclusively via the separate functional element 16 on the spindle nut 10 is transmitted and vice versa.

In the 4 and 5 it is also clearly recognizable that the two drive sections by the worm wheel 13 on the one hand and the spindle nut 10 on the other hand, are arranged radially to one another, the spindle nut 10 here radially inside the worm wheel 13 is arranged. The arrangement is chosen here and preferably so that, based on the spindle axis X, a radial projection of the worm wheel 13 and a radial projection of the spindle nut 10 axially overlap each other, with the radial projection of the worm wheel 13 narrower than the radial projection of the spindle nut 10 is and especially within the radial projection of the spindle nut 10 lies. In relation to the axial direction of the spindle axis X, this arrangement is particularly space-saving. To this axial area in which the spindle nut 10 and the worm wheel 13 radial to each other are arranged, the axial region with the functional element is axially offset 16 intended. The functional element 16 serves for coupling to an additional functional component, for example an overload clutch device 17 and / or a braking device 18 , and / or is itself part of such a functional component 16 , As I said, the spindle nut 10 and the worm wheel 13 in a first axial section and the functional element 16 and thus the functional component, for example the overload clutch device 17 and / or braking device 18 , are arranged in a second axial section, the two axial sections in particular adjoining one another or overlapping with one another in sections, becomes a particularly compact installation solution for a drive arrangement in the axial direction of the spindle axis X. 1 created with one or more of said functional components.

Based on 4 , the 5a) and the 5b) are now various exemplary configurations of a proposed drive arrangement 1 described, which are not mandatory combinations of features, but features of one embodiment can also be provided in the other embodiments.

First of all, in the proposed drive arrangement 1 , as is the case, for example, in the exemplary embodiment in 4 and the embodiment in 5b) is shown the worm wheel 13 relative to the spindle nut 10 be axially fixed, that is, during the operation of the drive arrangement 1 there is no axial deflection of the worm wheel 13 relative to the spindle nut 10 , In principle, however, as in the exemplary embodiment in 5a) is shown, the case is conceivable that the worm wheel 13 relative to the spindle nut 10 is axially movable, that is, in operation, in particular when the overload clutch device is actuated 17 , which will be described in more detail below, can be deflected axially. The deflections are comparatively small, so that the meshing engagement between the screw 12 and worm wheel 13 at least not significantly influenced.

As already mentioned, the drive has 5 here and preferably an overload clutch device 17 that disconnects the drive train in the event of an overload in the drive train. Here and preferably is the separate functional element 16 Part of the overload clutch device 17 and allows that over the functional element 16 manufactured rotatable coupling of the worm wheel 13 with the spindle nut 10 to solve in the event of an overload. In the case of a load below the overload limit, on the other hand, the rotationally fixed coupling is maintained or, after a previous disconnection due to an overload, is restored. Here and preferably the overload clutch device releases 17 in the event of an overload, via the functional element 16 manufactured rotationally fixed coupling against an axial spring force, as is also the case in the exemplary embodiments in FIGS 4 and 5a) the case is.

In the two embodiments in the 4 and 5a) is the overload clutch device 17 around a claw coupling that is a claw element 19 has, of which the separate functional element 16 is formed. The claw element 19 is according to the embodiment 4 relative to the spindle nut 10 axially movable, whereas the worm wheel 13 relative to the spindle nut 10 is axially fixed here. The claw element 19 has claws 20 on that with corresponding claws 21 on the worm wheel 13 interacting together.

In the embodiment according to 5a) however, it is the case that the claw element 19 relative to the spindle nut 10 is axially fixed, whereas the worm wheel 13 relative to the spindle nut 10 is axially movable here. The claw element also points here 19 steal 20 on that with corresponding claws 21 on the worm wheel 13 interacting together.

The claws 20 . 21 the overload clutch device 17 have inclined surfaces which cause the claws to slide as the load increases 20 . 21 enable each other. In this respect, these inclined surfaces form relative displacement contours. As the load increases, the embodiments in FIGS 4 and 5a) the claw element 19 axially deflected against a spring preload, with a non-rotatable coupling between the worm wheel until the overload limit, that is to say the limit whose exceeding defines an overload case, is reached 13 and claw element 19 consists. If the overload limit is exceeded, i.e. if there is an overload in the drive train, the claw elements are 19 and the worm wheel 13 disengaged, which also causes the spindle nut 10 from the worm wheel 13 is disengaged. The same principle also applies to the exemplary embodiment 5a) the basis, although here not the claw element with increasing load 19 but the worm wheel 13 is axially deflected.

Another example of an overload clutch device 17 shows 5b) , Here is the overload clutch device 17 around a magnetic coupling, this being a first permanent magnet arrangement 22 with at least one permanent magnet 23 and a second permanent magnet arrangement 24 with at least one permanent magnet 25 having. The first permanent magnet arrangement 22 is non-rotatable and axially fixed with the worm wheel 13 and the second permanent magnet arrangement 24 is non-rotatable and axially fixed with the spindle nut 10 connected. Here is the first permanent magnet arrangement 22 to the second permanent magnet arrangement 24 so arranged that a magnetic gap, that is, an air gap, between the two permanent magnet arrangements 22 . 24 is trained. The permanent magnet or magnets 23 the first permanent magnet arrangement 22 are relative to the permanent magnet or magnets 25 the second permanent magnet arrangement 24 aligned so that the first permanent magnet assembly 22 and the second permanent magnet arrangement 24 magnetically attract each other to create a coupling locking effect. In principle, however, arrangements of the permanent magnet arrangements are additionally or alternatively 22 . 24 to each other conceivable in which a coupling locking effect is generated by magnetic repulsion.

By the first permanent magnet arrangement 22 and the second permanent magnet arrangement 24 magnetically attract, there is a rotationally fixed coupling between the worm wheel 13 and spindle nut 10 reached. When the load in the drive train increases, the first permanent magnet arrangement rotates 22 and the second permanent magnet arrangement 24 relative to each other, a rotation-proof coupling is still guaranteed until the overload limit is reached. If the overload limit is exceeded, the two permanent magnet arrangements are 22 . 24 rotated to the extent that there is no longer sufficient magnetic attraction and the coupling is released. The spindle nut is then in this state 10 relative to the worm wheel 13 rotatable.

In the embodiment in 5b) is the functional element 16 here and preferably no part of the overload clutch device 17 , although in principle embodiments are also conceivable in which a corresponding functional element is part of a magnetic coupling.

In all of the exemplary embodiments shown here, in addition to the overload clutch device 17 as I said, a braking device as a further functional component 18 provided for braking at least part of the drive train. The braking device 18 is part of the drive 5 and brakes here and preferably the worm wheel 13 and the spindle nut 10 from. In the embodiments in the 4 and 5a) is the braking device 18 in addition to the separate functional element 16 intended. Basically, the functional element 16 but also part of the braking device 18 be or, as in the embodiment in 5b) the braking device is shown by way of example 18 form.

In the braking devices shown in the figures 18 each is a permanent brake, which is designed here as a friction brake. Basically, the braking device 18 but can also be an eddy current brake or magnetic brake. Here and preferably is the braking device 18 designed in such a way that with an increasing load in the drive train, the braking effect of the braking device 18 is increased ( 4 . 5a) ) or remains essentially unchanged ( 5b) ). In principle, it can also be provided that the braking effect is reduced as the load increases. The increase in the braking effect results in the embodiments in the 4 and 5a) with increasing load from the axial deflection between the functional element 16 and worm wheel 13 , In the embodiment in 5b) there is no or at least no significant deflection, which is why the braking effect does not change, or at least not appreciably, with increasing load.

The braking device 18 comprises at least one pair of friction surfaces, here and preferably a plurality of pairs of friction surfaces, wherein in the exemplary embodiment in 5b) the pairs of friction surfaces form a multi-disc brake. The pairs of friction surfaces here and preferably each consist of a friction surface 18a that with the drive housing 15 is rotatably connected, and a friction surface 18b that with the spindle nut 10 is rotatably connected. The respective friction surfaces 18a . 18b can be provided in particular on rotationally symmetrical components such as a brake pad or a brake disc. The pairs of friction surfaces are in frictional engagement with one another and, in the event that they twist relative to one another, each generate a frictional force that generates a braking effect. A spring arrangement 26 ensures that the friction surfaces 18a . 18b to achieve the braking effect on each other, here axially on each other, are biased. The spring arrangement 26 here and preferably has a wave spring, but variants with coil springs are also conceivable. The one from the spring assembly 26 generated biasing force can also be set, as will be explained below.

As previously explained, an axial deflection of the functional element influences 16 or claw element 19 relative to the worm wheel 13 also the functioning of the braking device 18 , The braking effect is increased as the load increases until the overload limit is reached, and this applies equally to the spindle nut 10 and the worm wheel 13 , If the overload limit is exceeded, these are the functional elements 16 and the worm wheel 13 decoupled from each other and can rotate relative to each other. In this case the braking device works 18 then, via the functional element 16 or claw element 19 , only on part of the Powertrain, namely the spindle nut 10 , whereas the worm wheel 13 is no longer braked. In this respect, the overload clutch device interact 17 and the braking device 18 together. In the embodiment in 5b) acts the braking device 18 but, as I said, after exceeding the overload limit in the same way as before, and in fact on both parts of the drive train, namely both on the spindle nut 10 as well as the worm wheel 13 , An interaction between overload clutch device 17 and braking device 18 then does not exist.

Further is in the 4 and 5 to recognize that the drive housing 15 of the drive 5 is formed in several parts and two housing parts 15a . 15b has which are in screw engagement and / or locking engagement with each other. One part of the housing 15a here and preferably forms a housing cover 27 , The other housing part 15b , which is formed here in several parts, encloses the essential movable elements of the drive arrangement in the radial direction 1 , The housing cover 27 serves to axially close the drive housing 15 , with only the spindle 9 through an opening in the housing cover 27 is brought out.

The housing part 15a or the housing cover 27 serves here and preferably also to support the spring arrangement 26 in the axial direction, that is, along the spindle axis X. By means of an axial movement, in particular screwing movement or latching movement, of the housing part 15a or housing cover 27 relative to the other housing part 15b causes an axial adjustment movement of the housing part 15a or housing cover 27 relative to the other housing part 15b and the worm wheel stored in it 13 and / or the spindle nut stored therein 10 , This adjustment movement in turn causes a change in the spring preload of the spring arrangement 26 , So the housing part 15a or the housing cover 27 in the housing part 15b moved in, for example screwed in or pressed in, which corresponds to a snap-in movement, increases the spring preload, whereas in the case of a movement in the other direction, for example in the case of a unscrewing movement or an extraction movement, the spring preload is reduced. Here and preferably causes an axial movement of the housing part 15a or housing cover 27 , which is directed axially to the housing interior, an increase in the spring preload, whereas an axial movement, which is directed axially to the housing exterior, causes a reduction in the spring preload.

In order to ensure that the spring preload set in this way and thus braking effect is maintained, the drive housing 15 here and preferably an axial lock 28 on, an axial movement, in particular axially towards the housing exterior, of the housing part 15a or housing cover 27 relative to the other housing part 15b blocks or at least complicates.

The axial lock 28 can be realized in different ways. For example, this can have a direction-dependent screw thread, via which the one housing part 15a with the other housing part 15b is in screw engagement. The screw thread is designed to be self-locking, in particular in a first direction of rotation, preferably in the direction of rotation of a unscrewing movement, in that, for example, at least one thread, in particular the internal thread and / or external thread, has a sawtooth profile.

Additionally or alternatively, the axial lock can 28 barbs too 29 have, which on the radial edge, in particular the outer edge, of one housing part 15a are provided and with counter-formations, in particular an internal thread, on the other housing part 15b interact with each other. In principle, a separate securing element with such barbs on the edge can also be used 29 be provided that the housing part 15a or the housing cover 27 secures axially to the housing exterior. A housing part 15a or housing cover 27 or a securing element with such barbs 29 is exemplary in 5b) shown. In particular, it is a serrated ring 30 , Such a jagged ring 30 is shaped in such a way that an axial movement of the same is possible in particular only in one direction and preferably only in the axial direction toward the housing interior.

The axial lock 28 can also have a soft component, which means a material that is softer than the material of the components on which the soft component is provided. For example, the soft component can be an elastomer. Such a soft component can be on at least one of the housing parts 15a . 15b , especially on the housing cover 27 , be provided and a screw movement of the housing parts 15a . 15b relative to each other in the threads of the screw thread, via which the one housing part 15a with the other housing part 15b is in screw engagement.

Another variant of an axial lock 28 is in 4 shown. This axial lock 28 has a grub screw 31 on that in a case slot 32 is arranged, which is in the one housing part 15a , especially in the housing cover 27 , extends inward from the radial edge thereof. Screwing in the grub screw 31 causes a radial expansion of the housing part 15a or housing cover 27 in the area of the housing slot 32 and thereby radial jamming relative to the other housing part 15b ,

Yet another variant of an axial lock 28 is exemplary in 5a shown, this here at least one locking screw 33 has a form fit between the one housing part 15a or housing cover 27 and the other housing part 15b forms when it is screwed in. Such a locking screw 33 can be screwed in, for example, in the radial direction or in the axial direction.

According to another teaching, which has independent meaning, is a hinge arrangement 34 for one stone 2 , in particular a boot lid, of a motor vehicle, claimed as such. The hinge arrangement 34 is with a hinge 35 , with a hinge 35 assigned hinge pivot axis 36 , with one with the hinge 35 coupled swing arm 3 that in the assembled state with the flap 2 is connected, and with a proposed drive arrangement 1 on the swingarm in the above way 3 attacks, equipped. In this respect, all statements on the proposed drive arrangement may be made 1 to get expelled.

The swingarm 3 is between the hinge pivot axis 36 and the mouth 2 as, here and preferably in the form of a circular section, curved arc section 38 designed. The arch-like wing 3 allows positioning of the hinge pivot axis 36 at the in 1 shown position without the swing arm 3 with a body part, here cross member, which is between the rear window 37 and the mouth 2 is colliding.

It can be viewed as shown 2 refer to the drive assembly 1 at least with the flap closed 2 , here and preferably both with the flap closed 2 as well as with the flap open 2 , in the projection in the direction of the hinge pivot axis 36 seen within that of the arch section 38 the swingarm 3 spanned geometric surface 39 is arranged. The proposed drive arrangement 1 is therefore housed in a space that is usually unused. Correspondingly, the hinge arrangement according to the proposal results 34 a particularly good use of installation space.

According to another teaching, which is also of independent importance, there is a flap arrangement 40 with one stone 2 , in particular a boot lid and with a proposed hinge arrangement 34 claimed. Proposed is with the swing arm 3 the hinge assembly 34 the flap 2 connected. On all versions of the proposed hinge arrangement 34 on the one hand and to the proposed drive arrangement 1 on the other hand, reference may be made.

Interesting in the valve arrangement shown 40 is the fact that the valve assembly 40 a spring arrangement 41 for spring preloading the flap 2 has, the spring arrangement 41 partly, here and preferably completely, separately and spatially separated from the drive arrangement 1 is provided. This leads to a particularly high degree of freedom in the constructive design of the proposed flap arrangement 40 ,

A synopsis of the 1 and 2 finally shows that the output shaft 7 the motor unit 6 is level when installed. While this means that part of the motor unit 6 , in particular a coil arrangement of the motor unit 6 , Inertia-related torques on the worm gear stage 11 or on the spindle-spindle nut gear 8th exercises. However, this can be accepted, since the output shaft is aligned horizontally 7 the motor unit 6 with a suitable design, particularly good use of installation space goes hand in hand.

QUOTES INCLUDE IN THE DESCRIPTION

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Patent literature cited

• DE 10001054 A1 [0004]

Claims (16)

Drive arrangement for the motorized adjustment of a flap (2), in particular a boot lid, of a vehicle, the drive arrangement (1) acting on the flap (2) or on a rocker (3) assigned to the flap (2) in the assembled state for motorized adjustment, The drive arrangement (1) has a drive unit (4) with a drive (5) and the drive (5) has a rotary motor unit (6) with an output shaft (7) and a spindle (9) connected downstream of the motor unit (6) ) and a spindle-nut gear (8) having meshing engagement with it (10) for generating drive movements along the geometric spindle axis (X) of the spindle (9), between the motor unit (6) and the spindle-nut gear ( 8) a worm gear stage (11) is connected, which has a worm gear (12) coupled to the motor unit (6) for drive technology and which can be rotated about a first gear axis (G ₁ ), and e in a worm wheel (13) which is in meshing engagement with the worm (12) and which, driven by the worm (12), is rotatable about a second gear axis (G ₂ ) which runs transversely to the first gear axis, and wherein the motor unit ( 6), the worm gear stage (11) and the spindle-spindle nut gear (8) are arranged in a drive train of the drive arrangement (1), characterized in that for the transmission of a torque between the worm wheel (13) and the spindle nut (10) a separate functional element (16 ) is provided, which is connected in terms of drive technology in the drive train between the worm wheel (13) and the spindle nut (10) and which is non-rotatably coupled to the spindle nut (10). Drive arrangement after Claim 1 , characterized in that the worm wheel (13) is axially fixed or axially movable relative to the spindle nut (10). Drive arrangement after Claim 1 or 2 , characterized in that the drive (5) has an overload clutch device (17) for disconnecting the drive train in the event of an overload in the drive train, the separate functional element (16) preferably being part of the overload clutch device (17), preferably that the overload clutch device (17) in the event of an overload in the drive train, the rotationally fixed coupling of the worm wheel (13) with the spindle nut (10) is released, further preferably that the overload coupling device (17) releases the rotationally fixed coupling against an axial spring force in the event of an overload in the drive train. Drive arrangement after Claim 3 , characterized in that the overload coupling device (17) is designed as a claw coupling which has a claw element (19) which is formed in particular by the separate functional element (16), the claw element (19) being axially movable relative to the spindle nut (10) and claws (20), which cooperate with corresponding claws (21) on the worm wheel (13), which is axially fixed, in particular to the spindle nut (10), or which is axially fixed to the spindle nut (10) and has claws (20), which with corresponding Claws (21) on the worm wheel (13), which is axially movable in particular with respect to the spindle nut (10), interact in a coupling manner. Drive arrangement after Claim 3 , characterized in that the overload clutch device (17) is designed as a magnetic clutch, preferably that the overload clutch device (17) has a first permanent magnet arrangement (22) with at least one permanent magnet (23) which is connected to the worm wheel (13) in a rotationally fixed and axially fixed manner, and a second permanent magnet arrangement (24) with at least one permanent magnet (25), which is connected in a rotationally fixed and axially fixed manner to the spindle nut (10), the first permanent magnet arrangement (22) and the second permanent magnet arrangement (24) being axially adjacent to one another and one Form the magnetic gap between each other, the at least one permanent magnet (23) of the first permanent magnet arrangement (22) being oriented relative to the at least one permanent magnet (25) of the second permanent magnet arrangement (24) such that the first permanent magnet arrangement (22) and the second permanent magnet arrangement ( 24) each other to produce a coupling Fe Magnetically tighten and / or repel the actuating action, further preferably that the separate functional element (16) is not part of the overload clutch device (17). Drive arrangement according to one of the preceding claims, characterized in that the drive (5) has a braking device (18) for braking at least a part of the drive train, the separate functional element (16) preferably being part of the braking device (18), preferably that the Braking device (18) brakes the spindle nut (10) and / or the worm wheel (13). Drive arrangement after Claim 6 , characterized in that the braking device is a permanent brake and / or that the braking device (18) is a friction, eddy current or magnetic brake. Drive arrangement after Claim 6 or 7 , characterized in that the Braking device (18) has at least one pair of friction surfaces, in particular a plurality of pairs of friction surfaces, for generating the braking effect, which is / are formed in particular by the separate functional element (16), the respective pair of friction surfaces being preloaded against one another by means of a spring arrangement (26) to achieve the braking effect , in particular axially preloaded on one another, it is preferred that the preload force, in particular the axial preload force, of the spring arrangement (26) is increased to increase the braking force. Drive arrangement according to one of the Claims 6 to 8th , characterized in that the overload clutch device (17) and the brake device (18) interact with one another, preferably that after the drive train is separated by the overload clutch device (17), the brake device (18) only on part of the drive train, in particular on the spindle nut ( 10) or on the worm wheel (13), or that after the drive train is separated by the overload clutch device (17), the braking device (18) on both parts of the drive train, in particular on the spindle nut (10) and on the worm wheel (13 ), works. Drive arrangement according to one of the Claims 6 to 9 , characterized in that the spring arrangement (26), which axially biases the respective pair of friction surfaces to achieve the braking effect, provides the axial spring force against which the overload clutch device (17) releases the rotationally fixed coupling when the load in the drive train increases. Drive arrangement according to one of the Claims 8 to 10 , characterized in that the pretensioning force of the spring arrangement (26) is increased when, with increasing load in the drive train, the coupling parts interacting with one another and forming the overload coupling device (17), in particular the separate functional element (16) and the worm wheel (13), axially move apart. Drive arrangement according to one of the preceding claims, characterized in that the drive (5) has a drive housing (15) with two housing parts (15a, 15b), the one housing part (15a), which preferably forms a housing cover (27), in screw engagement and / or latching engagement with the other housing part (15b), preferably that the spring arrangement (26) is supported axially on the one housing part (15a) and an axial movement, in particular screwing movement or latching movement, of the one housing part (15a) relative to the other Housing part (15b) causes an axial adjustment movement of one housing part (15a) relative to the other housing part (15b) and the worm wheel (13) and / or the spindle nut (10) mounted therein, the adjustment movement causing a change in the spring preload, further preferably that the axial movement is a movement directed axially towards the housing interior, in particular a screwing movement and / or Snap movement, which causes an increase in the spring preload, or that the axial movement is a movement directed axially to the housing exterior, in particular a unscrewing movement and / or pull-out movement, which causes a reduction in the spring preload. Drive arrangement after Claim 12 , characterized in that the drive housing (15) has an axial securing device (28) which has an axial movement, in particular an axial movement towards the housing exterior, of the one housing part (15a), in particular the housing cover (27), relative to the other housing part (15b ) blocks or at least makes it difficult. Drive arrangement after Claim 13 , characterized in that the axial lock (28) has a direction-dependent screw thread, via which the one housing part (15a) is in screw engagement with the other housing part (15b), the screw thread being designed to be self-locking, in particular in a first direction of rotation, and / or that the axial lock (28) has barbs (29) which are provided on the radial edge, in particular the radial outer edge, of one housing part (15a) or a separate locking washer and with counter-formings, in particular an internal thread, on the other housing part (15b) interacting in a latching manner, the one housing part (15a) or the separate locking washer in particular forming a prong ring (30), and / or the axial securing means (28) having a soft component which is attached to at least one of the housing parts (15a, 15b), in particular on the Housing cover (27) is provided and with a screwing movement of one housing part (15a) relative to the other eren housing part (15b) in the threads of the screw thread, via which the one housing part (15a) is in screw engagement with the other housing part (15b), and / or that the axial lock (28) a grub screw (31) in a housing slot (32), which in one housing part (15a), in particular the housing cover (27), extends inwards from its radial edge, screwing in the grub screw (31) radially expanding the housing part (15a) in the region of the housing slot ( 32) and thereby causing a radial jamming of the housing part (15a) relative to the other housing part (15b), and / or that the axial lock (28) has at least one locking screw (33) which has a positive fit forms between one housing part (15a) and the other housing part (15b). Hinge arrangement for a flap (2), in particular a boot lid, of a motor vehicle, with a hinge (35) and a hinge pivot axis (36) assigned to the hinge (35), with a rocker arm (3) coupled to the hinge (35), which is connected to the flap (2) in the assembled state, and to a drive arrangement (1) according to one of the preceding claims, which acts on the rocker (3). Flap arrangement with a flap (2) and with a hinge arrangement (34) Claim 15 , with the rocker (3) the flap (2) is connected.

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