EP1913276A1

EP1913276A1 - Control device for a motor vehicle

Info

Publication number: EP1913276A1
Application number: EP06762832A
Authority: EP
Inventors: Georg Scheck
Original assignee: Brose Fahrzeugteile SE and Co KG
Current assignee: Brose Fahrzeugteile SE and Co KG
Priority date: 2005-07-29
Filing date: 2006-07-26
Publication date: 2008-04-23
Also published as: WO2007014686A1

Abstract

The invention relates to a control device (1) for a motor vehicle comprising a coupling system (3) which is provide on input (ANS) and output (ABS) sides and coupled to a drive system (2), on the input side, and to an adjusting element (4, K) on the output side, wherein said coupling system (3) comprises a part (10) provided with a symmetrical rotatable contact surface (6) and a securable spring spread or wrap-around type friction tight element (11, 11') whose ends (11a, 11b; 11'a, 11'b) are mutually remote. The coupling system (3) also comprises a triggering device (G) interacting with the friction tight element (11, 11') by the action of an adjustment torque (M<SUB>v</SUB>) applied from the input (ANS) to the output (ABS) side and the triggering device releases the friction tight element (11, 11') tensed against the symmetrical rotatable contact surface (5) after having passed a trigger path and generated a triggering torque (M<SUB>AUS</SUB>).

Description

Description Adjustment device for a motor vehicle

The invention relates to an adjusting device for a motor vehicle, with a drive system and with an adjusting element coupled thereto via a coupling system.

Such adjusting device is used for actuating an adjusting element of a motor vehicle. In this case, an adjusting element is understood as meaning a closing part which is connected to a vehicle body or slidingly guided with respect to the latter, for example a tailgate, a sunroof, a vehicle window, a vehicle door, a boot lid or an engine compartment lid, for closing a body opening. The drive system preferably has an electric motor, which is usually coupled to the output-side adjusting element via a transmission designed to transfer force within a force flow.

For automatic actuation of the adjusting element connected to the drive system, adjustable length tube assembly with two telescopically guided adjustment tubes (tube-in-tube system) may be provided, wherein an adjustment of the adjustment, for example on a tailgate, and the other adjusting tube on the Vehicle body is stored. When transmitting an adjusting torque generated by the drive system to the adjusting element, the tube arrangement converts a rotary adjusting movement into a translatory adjusting movement, so that, due to the coupling of the tube arrangement with the adjusting element, this length of displacement between two end positions, namely a closed position and an open position , is moved depending on the direction of rotation of the rotary adjustment movement.

In order to avoid a risk of injury to an operator and on the other hand damage to the drive system in such an adjustment that allows automatic or external actuation of the adjustment of a motor vehicle, a mechanical transmission system may be provided, the drive side with the drive system and the output side with the Ver is coupled. The switched between the drive system and the adjustment transmission system thus serves on the one hand for transmitting an adjusting torque generated on the drive side to the adjustment. On the other hand, the transmission system decouples the adjusting element from the drive system when an additional or external force acts on the Ver adjusting element whose reaction to the drive system is to be prevented.

An adjusting device for a pivotable body part, with a motor drive and with a transmission system which is effective as a sliding clutch, is known, for example, from DE 198 33 612 A1 or from DE 198 44 265 A1.

The invention has for its object to provide an adjusting device of the type mentioned above, which allows a particularly reliable and reliable as possible operation of an adjusting element, in particular a tailgate, a motor vehicle. In particular, a particularly comfortable manual operation of the automatically driven adjusting element should be possible.

This object is achieved by the features of claim 1. Advantageous variants, refinements and developments are the subject of the dependent claims.

For this purpose, the adjusting device comprises a coupling system with a drive side and an output side for the mechanical coupling of a drive system with an adjusting element, in particular a tailgate of a motor vehicle. As a friction partner for generating a force or frictional connection, the coupling system comprises a frictional engagement element and a component which has a rotationally symmetrical contact or friction surface against which the frictional engagement element can be braced to produce a holding torque. The clutch system further comprises a drive element coupled to the drive system and an output element coupled to the adjustment element. The coupling system is thus coupled on the drive side with the drive system and the output side with the adjusting element, wherein the drive element or the driven element may be formed by the preferably hollow cylindrical component or coupled thereto or connected. As a frictional engagement element, the clutch system comprises a spreading spring or a spreading band or a wrap spring, which is also designed to wrap around or expediently in the manner of a spreading spring. The frictional engagement element interacts with the rotationally symmetrical contact surface of the component in such a way that a relative movement relative to the contact surface can be blocked due to a contact pressure or frictional force generated as a result of a prestressing of the frictional engagement element. Blocking is here understood to mean a cancelable or releasable holding in the manner of a friction locking or locking mechanism. For this purpose, the frictional engagement element has at least one prestressed or prestressable spring turn, wherein the respective turn or spring ends are spaced apart from one another.

In a wrap spring, the frictional engagement element has a number of spring coils with angled and mutually facing spring ends. In the embodiment as a spreading band, the frictional engagement element has a single spring coil with spaced-apart belt or spring ends.

In the expansion band design, the frictional engagement element preferably has two further spring ends in the form of support arms, which are expediently integrally formed in one piece or in one piece with the expansion band to the freiendseitigen spring ends.

In particular, in the embodiment of the frictional engagement element as a spread the rotationally symmetrical contact surface is the inner surface or inner wall of a hollow cylindrical member or hollow body, while in the embodiment as a wrap spring alternatively the outer surface or -wandung of such a cylindrical member can serve.

A certain bias of the frictional engagement element can already be generated, in particular in the embodiment as a wrap spring, by virtue of the fact that its several spring coils are braced against the contact surface. Preferably, however, additionally or alternatively, a blocking force is coupled into the coupling system for prestressing or tensioning the frictional engagement element. For this purpose, suitably In both embodiments or variants of the frictional engagement element, a boost lever is provided for generating or amplifying the prestress.

In particular, when using a wrap spring whose two, compared to the voltage applied to the contact surface and the component windings expediently angled or bent spring ends are held together by the boost lever. As a result, a force acting on the reinforcing lever as a result of its leverage with a corresponding division of force is transmitted to both winding or spring ends in the direction of increasing tension of the frictional engagement element and thus increases its tension against the contact surface.

In the embodiment of the frictional engagement element as a spreading band, the reinforcing lever is guided between the belt-plane spaced-apart opposing freiend- side band or spring ends. In addition, the reinforcing lever is supported on the freiendseitigen spring ends spaced and in the space enclosed by the expansion band inside supporting arms such that to produce the required for the construction of the trigger torque Anpress- or friction force each have a freiendseitiges spring end and an effective as a support arm spring end in pairs lie opposite. The reinforcing lever, which is preferably used both in the expansion band and when using a wrap spring, generates or reinforces the contact pressure or friction force and thus increases the friction and thus the frictional engagement of the frictional engagement element with the cylindrical component of the coupling system. As a result, the desired or required release torque is generated in a particularly simple and reliable manner.

Triggering moment is here understood as a result of the action of an output side directed toward the drive side of the clutch system adjusting torque, in particular due to an external force or an adjusting force on the adjustment, predetermined or adjusted by the clutch torque or torque, with the achievement of a steady increase one due to an increasing tension of the frictional engagement element is superimposed against the contact or friction surface which cooperates with this as a frictional partner of a likewise from the clutch system and there of the Tripping device generated force or moment effect. With the onset of this torque effect, which can be generated by spring, magnetic and / or leverage, the clutch system reacts to the still effective adjusting torque with a reduction of the torque increase in the manner of overriding the holding torque or with a torque drop. Along the triggering path, at the beginning of the path, the force of the triggering device begins, the same moment or torque of the clutch system opposite the adjusting torque may increase slightly, approximately or remain substantially constant or even fall off. The torque curve within the triggering path depends on the type and / or dimensioning of the force or torque effect of the triggering device and can therefore be set or specified in this way.

On the one hand, a particularly effective clamping of the frictional engagement element with generation of the holding torque with a blocking effect is achieved both in the embodiment as a wrap spring and in that as an expansion band, so that the clutch system locks and a sufficiently large release torque occurs when an adjusting torque or an adjusting force acts on it can be adjusted. The lock or blocking and the generation of the release torque is carried out at least from the output side to the drive side and thereby symmetrical in both rotational or adjustment directions. The release torque is set or predetermined such that the adjustment preferably remains in each end or intermediate position along a possible adjustment path and thus held in the respective position.

On the other hand, the blocking or blocking of the frictional engagement element can be canceled in the blocking in the same direction triggering or switching path, with the result that at the end of the triggering path, the frictional engagement in the sense of reducing its tension is released from the corresponding friction or contact surface, with the result the frictional engagement element can be moved relative to the contact surface, possibly with the generation of a certain sliding torque. For this purpose, an adjusting torque acting on the coupling system or a corresponding adjusting force at the path end of the triggering path for touching or contacting the triggering device at one of the spring ends of the friction closing element, so that this end of the spring is released from the contact surface or lifted. After releasing the frictional engagement element, the adjusting moment leads to a relative movement between the frictional engagement element and the contact surface or the component having it according to the law of friction with a transition from a system-related static friction to sliding friction. This principle of blocking and releasing the frictional engagement element acts the same in both directions or directions of rotation due to the symmetrical structure of the coupling system. However, a release of the blocking of the frictional engagement element takes place only upon reaching a release torque, the generation of which requires the holding torque built up by the coupling system.

While the holding torque is generated as a result of the frictional force or the frictional engagement between the friction partners and thus by friction, the release torque is generated by a force and / or leverage independent of the friction coefficient of the friction partners. The triggering torque set on the basis of this force or torque effect is therefore always the same regardless of the surface condition of the frictional engagement element and the contact surface. Only the sliding friction between the friction partners generated by the coupling system at the path end of the release path is dependent on the coefficient of friction, ie. H. depending on the coefficient of friction (μ) of the participating friction partners.

The force and leverage is constructed by means of the triggering device and thereby by means of a force element or coupling component and / or a lever or Kipphebelelementes, wherein the triggering device takes over both the force function and the time required for the generation of a moment lever or Hebelarmfunktion. The force function can be generated or built up by means of an elastic spring element or magnetically. The spring element can be used to provide the lever arm to a rotation axis spaced in the coupling system. Alternatively, a coupled spring and lever element may be provided. The force or force and lever element, in particular a spring element zugerordnetes, also causes a restoring force, so that the clutch system with decreasing adjusting torque or when eliminating the external system acting on the coupling system Adjusting force with rebuilding the holding torque automatically in the initial state, ie falls back to the original or rest position.

The release torque is the reaction of the coupling system to a force acting on the adjustment, for example, manual adjustment. Therefore, if the tripping torque is reached as a result of an adjusting force acting on the adjusting element, then the holding torque is practically suppressed due to the superposition of the tripping torque, with the result that the frictional engagement element is released from the contact surface and slides along it. The static friction torque and thus also the sliding torque along the further adjustment path of the adjusting element adjoining the triggering path can be greater or preferably smaller than the triggering torque, depending on the desired operating convenience, depending on the torque effect generated by spring, magnet and / or lever force the manual adjustment of the adjusting element based on the structure, the mode of action and / or the component or force rating of the triggering device is set, predetermined or determined.

A distortion of the frictional engagement element is basically by a widening of the wrap spring or the wrap spring or Spreizbandes. In the arrangement of the wrap spring on the outer surface of the cylindrical member for this purpose acts a force (contraction force) for contraction of the winding or spring ends. Similarly, a release of the frictional engagement element basically by a contraction of the wrap spring or the Schlingfederbandes causing relative movement of at least one of the winding ends relative to the contact surface. When the wrap spring is arranged on the outer surface of the component, the ends of the coil are pressed apart or expanded.

The coupling system fulfills the one hand, the task of a motorized actuation of the adjusting element in the open or closed position, the power flow from the drive side (drive) to the output side (output) out with sufficient for actuating the adjustment, depending on the amount of generated or generated release torque Verstellmoment or a corresponding adjustment force to Ü. If in this case the drive system is self-locking, in particular due to nes this associated self-locking gear, so based on the adjustment acting adjusting torque in the drive system. In this case, a force or torque is absorbed by the drive system until the holding torque generated by the clutch system is suppressed by superposition with the tripping torque and the tripping path is traversed, with the result that the clutch system decouples the drive side from the output side.

The self-locking drive system is thus effectively acting as a brake. In addition, the transferable from the drive to the output torque - or a corresponding adjustment - to actuate the adjustment and a transferable from the output to the drive (manual) operating torque - or a corresponding adjustment - opposite equal to the release torque. In this case, the frictional engagement element is braced both for transmitting the drive-side adjusting torque to the adjusting element and for holding the adjusting element in each final or intermediate position independently of the respective directions of rotation until reaching the tripping torque in the corresponding effective direction of the blocking required for the respective direction of rotation. The cylindrical component may in this case be both drive element and output element of the coupling system. The cylindrical member is then rotatably supported and preferably arranged in a bearing housing. The bearing housing mainly takes over protective functions for the components or components of the coupling system.

If, on the other hand, the drive system is not self-locking, then the clutch system is additionally effective as a brake. The drive torque from the drive system to the adjusting element is then preferably transmitted by a rigid coupling from the drive side to the output side of the clutch system. In this transmission direction, the brake function of the clutch system is ineffective by this is released from the drive side to the output side, so that the power flow is transmitted from the drive system directly to the adjustment and no holding torque is generated. However, in the opposite direction of transmission from the output side to the drive side effective adjustment torque is supported in a rotationally fixed housing or bearing housing, which then expediently additionally forms the rotationally symmetric contact surface. On the output side, the braking function is thus effective by blocked the frictional engagement and the clutch system generates the holding or release torque.

The blocking effect and braking function remains until the suppression or superposition of the holding torque generated by the coupling system from the release torque. After suppression of the holding torque as a result of the superposition of the release torque, the drive system moves with the output or with the output side adjustment due to the rigid coupling between the output element and the drive element of the clutch system. In the case of a non-self-locking drive system, the torque that can be transmitted on the drive side and the output side, ie. H. the drive torque and the adjustment or release torque unequal.

The holding torque superimposed and leading to its suppression triggering torque is built or generated within the trip path, the path beginning with the onset of the force of the triggering - and thus upon reaching the release torque - and its end with the release of the blocking of Reibschlusselementes - and thus with transition to Adhesive or sliding friction - is defined. Although the frictional engagement element is still loaded in the blocking direction within the elastic triggering path, so that the coupling system remains in the blocked state even after reaching the tripping torque. However, acting in the blocking direction blocking or pressing force is superimposed on the frictional engagement element generated by the triggering force and lever or torque effect, which counteracts a further increase or a further increase in the holding torque.

Depending on the design or interpretation of this force and leverage, the length of the trip path may be different. The coupling of the additional force and leverage effect of the triggering device means that with increasing, constant or decreasing adjusting torque within the triggering path, this practically exclusively depends on the dimensioning or adjustment of the force and the lever arm of the triggering device, but not on the coefficient of friction between the friction clutch Friction element and the contact surface depends. Upon reaching the tripping torque and after passing through the triggering path, the contact pressure or friction force in the sense of releasing the tension of the frictional engagement element increasingly reduced in the blocking direction and relieves the frictional engagement element as a result of activation of one of the spring ends. The triggering device can serve both to load the frictional engagement element and to relieve or release the frictional closure element in the blocking direction.

Depending on the configuration and / or dimensioning of the force or torque effect of the triggering device, the force or torque effect generated by the clutch system within the triggering path can be that of a real or preloaded spring, a maximum prestressed spring, a degressive spring or a particular spring-loaded rocker arm correspond. The spring effect of the triggering device can be generated by means of a compression spring, a tension spring or a torsion spring. Alternatively, a magnet for generating this force or torque may be provided. The leverage of the release device force element can be generated by means of a switching or rocker arm. Depending on the design of the drive system as self-locking or non-self-locking, the shift lever or rocker arm can be coupled to the output side or to the drive side of the clutch system.

The advantages achieved by the invention are, in particular, that a power-operated or motor-driven adjusting element of a motor vehicle is reliably held on the one hand in an open position, but on the other hand, a manual actuation or adjustment of the adjusting element in an end position, for example in the closed position, allows. Furthermore, the adjusting element can also be manually stopped or reversed during the automatic or motor drive in the open or closed position. Due to the switchable coupling action of the adjusting device damage to the drive system is reliably prevented in any case. These functions or functionalities are particularly desirable in the case of an automatically operable tailgate of a motor vehicle, and it can be assumed that manual actuation of the tailgate is regularly performed in addition to automatic or motorized operation. When the adjustment element is in one of the end positions, in particular in the open position, the coupling system generates a release torque ensuring the end position. In order to be able to bring the adjusting element manually from this end position into the other end position, for example into the closed position, the blockage generated by the coupling system can be released manually or manually and thereby easily released or pushed over by the coupling of the triggering moment. For this purpose, the force coupling of the triggering device causes a blocking action, blocking or inhibition of the frictional engagement element releasing or relieving force effect is generated within the particular elastic triggering path at one of the driven side to the drive side acting manual actuation of the adjustment.

Embodiments of the invention will be explained in more detail with reference to a drawing. Show:

1 is a torque-angle diagram with typical torque curves of a mechanical coupling system of an adjusting device according to the invention,

2 is a schematic representation of the rear region of a motor vehicle with a pivotably hinged tailgate and with an adjusting device for pivoting the tailgate,

3 is a schematic representation of the adjusting device of Figure 2,

4a and 4b are schematic block diagrams of a friction clutch or as

Friction brake effective coupling system,

5 to 7 show a schematic cross-section through a wrap spring variant of an effective as a friction brake clutch system with a trigger element containing a spring element in different

Movement phases when acting on a drive-side and drive-side torque, 8 to 10 an embodiment of the wrap spring variant with a release device in the powerless state and under the action of a drive-side torque,

Fig. 11 is a schematic cross-section through part of another

Wrap spring variant with a release device with mutually braced piston,

12 is a schematic cross section through an alternative Schlingfeder- variant with a triggering device with tension spring,

13 and 14 are schematic cross sections through coil spring variants with a magnetic elements having triggering device,

15a and 15b are schematic cross-sections through a loop spring variant of a

acting as a friction clutch clutch system with lying in a housing planetary gear and outboard wrap spring and with a rocker lever triggering device in the initial state or in a decoupled state,

16a and 16b in front and rear view of a wrap spring variant of a self-adjusting clutch system with a two levers and two tension springs triggering device,

Fig. 17a and 17b in front and rear view of a wrap spring variant as

Lock effective coupling system with a gain lever and with a two levers and two compression springs release device,

18 is a schematic view of one half of a wrap spring variant of a clutch system effective as a release clutch, 19 is a schematic cross section of a loop spring variant of a

Clutch system with reinforcement lever and with a spring-loaded rocker arm having triggering device,

20 is a schematic representation of a loop spring variant of a clutch system with a reinforcement lever and with a spring-loaded slider and with a triggering device with actuating levers and tilting slides,

Fig. 21 in cross section a variant of an effective as a friction brake

Coupling system of an adjusting device with a spreading belt as frictional engagement element and with a toggle lever having a triggering device in a rest or starting position,

22 is a detailed view of the triggering device of the coupling system of FIG. 21 under the action of a driven-side torque,

FIGS. 23 to 26 different embodiments of a coupling system with an expansion band as frictional engagement element,

27 shows an illustration according to FIGS. 21 to 26 of an embodiment of the coupling system with a detent ball,

28 to 30 different Spreizband variants of the coupling system with a rocker arm with slider,

31a and 31b in cross-section an embodiment of an effective as a friction clutch coupling system of an adjusting device with a spreader as frictional engagement element and with a spring lever having release device in rest or release position, 32a and 32b show a variant of an effective as a friction clutch coupling system with a spreader and a release spring having a release device in rest or disengagement, and

Fig. 33 shows a variant of an effective as a friction clutch coupling system with a spreader and with a rocker arm having release device with slider.

Corresponding parts are provided in all figures with the same reference numerals.

Fig. 1 shows different force or torque curves in a moment-angle diagram (M, ω). The illustrated torque curves Mi, M ₂ , M ₃ correspond to the reaction of a clutch system 3 to an acting from its output side ABS to the drive side ANS turning or adjusting moment My. For this purpose, the coupling system 3 according to the figures 2 to 4 is coupled on the drive side with a drive system 2 and the output side with an adjusting element 4 of an adjusting device 1 of a motor vehicle. The torque curves Mi, M ₂ M ₃ represent different or differently generated triggering torques MAU _S during a manual actuation of the adjusting element 4 in the form of a motorized or automatically movable tailgate K of a motor vehicle by the drive system 2.

Each of the illustrated torque profiles Mi, M ₂ , M ₃ contains a plurality of regions a, b, c. Within a relatively short first region defined or defined by systemic elasticities, there is a steep instantaneous increase, in which a frictional engagement element effective in the manner of a spreading or wrap spring, designated by 11, 11 'in the following exemplary embodiments, is designated by a reference numeral 5, preferably rotationally symmetrical contact surface increasingly biased and is blocked due to the resulting contact pressure or frictional force under construction of a correspondingly increasing holding torque M _H.

The area b following the area a represents a triggering path within which a triggering moment M _A US is reached or generated. At the end of the path This trip path b also the blocking of the strained frictional engagement element is released. For this purpose the theoretically until the destruction of Reibschlusselementes or the coupling system rising holding torque M _H inducing frictional engagement is having between through the Reibschlusselementes and the rotationally symmetrical contact surface, subsequently designated 10 component friction pairs formed is reduced to the extent that the frictional engagement element that at the end of the path of the trip path b can then move with a certain friction or sliding friction to generate a corresponding sliding torque M _{G of} the clutch system 3 relative to the contact surface or along this.

The path beginning of the triggering path b in the transition of the areas a and b is determined by the use of the force of a subsequent triggering device designated G. The end of the trip path b is determined by the transition of a slight torque increase due to a prevailing in the region of the end of the trip path b between the friction friction for comparatively low sliding friction with correspondingly low and at least approximately constant sliding torque MQ within the adjoining the trip path b range c.

Within the range or tripping path b, on the one hand, a force is applied to one of the spring ends of the frictional engagement element 11 in the tensioning or blocking direction. On the other hand, a triggering element of the triggering device G is guided along the release path b in the blocking direction until it rests against the other end of the frictional engagement element 11. The respective torque curve within the triggering path b depends on the type of force action of the triggering device G.

Thus, the torque curve M ₁ within the triggering path b corresponds to the force or torque effect of a preloaded spring element, wherein at the path beginning of the tripping path b the output-side adjusting moment Mv has reached or just exceeds the predetermined or adjusted preload torque of the spring element. Along the triggering path b, within which at least one of the ends or spring ends of the frictional engagement element is loaded or subjected to force in its blocking direction, the torque curve Mi corresponds to the slightly as long as rising spring characteristic of the spring element until the trigger element or a corresponding triggering device on the loaded spring end opposite, to be solved end or spring end of the frictional engagement element is applied. As a result of the consequent additional contact force on the unloaded spring end of the friction closing element takes place - in the area before the end of the trip path b (Fig. 1) - a small torque increase to the triggering torque MAUS that is equal to the frictional torque Mm in this case (MAUS = Mm ). The friction-value or friction-dependent sliding torque MGI that arises after releasing the locking of the frictional engagement element 11 may be smaller than, equal to or even greater than the triggering moment MAUS of the moment profile Mi. Depending on the prevailing speed or acceleration conditions, a typical transition between static friction and sliding friction may exist at the boundary between regions b and c.

Within the elastic release path b represented by the region b, the torque curve Mi produced as a result of the effective adjusting force F or of the effective adjusting moment M _v on the adjusting element 4 or on the tailgate K as a reaction of the coupling system 3 can correspond to a real, in particular toughened rotation , Tension or compression spring slightly increase or run in a manner not shown in the manner of an ideal, ie a fully biased Feeder of at least approximately constant. Also, within the triggering path b, the torque curve according to the solid line may initially rise until a tip or vertex d is reached, in order to then continuously decrease in accordance with a relaxing spring. In this torque curve M ₂ , which corresponds to the force effect of a spring-loaded tilting element of the triggering device, the friction torque M _R2 at the end of the trip path b is much smaller than the release torque M _A US- Due to the also smaller sliding torque MG ₂ is also the adjusting torque Mv along the range c correspondingly low, which allows a comparatively high level of comfort in the manual operation of the tailgate k.

In addition, within the tripping path b, the torque curve M _{3 can} decrease continuously or approximately exponentially in accordance with the dashed line when the tripping torque MAUS is reached. In this torque curve M ₃ , the magnetic force of the Triggering torque MR ₃ at the end of the trip path b is again much smaller than the release torque M _A US- The torque curve M ₃ characterizes - as the torque curve M ₂ - a practically or almost complete disengagement of the clutch system 3. Due to the comparatively klei - NEN sliding torque MG3 a correspondingly high comfort in the manual operation of the tailgate k is achieved in this variant.

When using a tilting element as a triggering device can - as indicated by the dotted line - also virtually every lying between the illustrated Mo- mentenverläufen M ₂ and M ₃ torque curve M 'set, then in particular no or only a slight increase in torque within the triggering path b he follows.

The areas a and b thus represent an initially increasingly biased in the blocking direction frictional engagement element of the clutch system, which blocks a from the output side ABS to the drive side ANS acting towards torque and thus an output side adjusting torque M _v within the range a. In the area b, ie at the beginning of the path, within or at the end of this triggering path b, a tripping torque MAU _{S is} achieved, by means of which the holding torque M _{H is} suppressed, at the end of the trip path b blocking the frictional engagement _element overcoming the respective frictional torque M _R1iR2 , _{R3 is} solved. At the end of the triggering path b, the tripping device or a force element releases the frictional engagement element in the blocking direction from the contact surface, also referred to below as the component surface, so that the frictional engagement element slips. In the subsequent region c, depending on the force effect, a moment of validity MGI, G2, G ₃ sets in.

Preferably, therefore, the drive-side adjusting moment M _v to be applied within the triggering path b decreases progressively until the end of travel is reached, wherein within the triggering path b the frictional engagement element is still braced in the blocking direction. At the end of the trip path b, at which the frictional engagement element is increasingly released from the corresponding rotationally symmetrical contact surface in a direction of loosening directed in the blocking direction, the tripping torque MAUS is already reached in the torque curves M ₂ and M ₃ . To the Loosening the frictional engagement between the friction partners 5, 11, the triggering torque MAU _S must therefore be reached or exceeded and the triggering path b must be passed through. The tripping path b corresponds to a correspondingly set or predeterminable switching cycle of the tripping device G between an initial or rest position and an abutment position on each spring end of the frictional engagement element to be released.

If no adjustment force F acts on the adjustment element 4 or if the tailgate K is released and is in an arbitrary position between the two end positions, ie between a closed position and an open position, then the frictional engagement element is loaded again in the blocking direction. The clutch system 3 will thus lock again and consequently the tailgate K will remain in the current or instantaneous position. The reason for this is that the adjusting moment Mv currently acting along the respective torque curve Mi, M ₂ , M ₃ or M 'is undershot, and that the triggering device G is automatically returned to the starting or rest position as a result of an acting restoring force.

FIG. 2 shows the rear region H of a motor vehicle which has a tailgate K, which is pivotably hinged to the roof edge region D about a pivot axis T. The tailgate K is associated with an adjusting device 1, which is driven by a motor drive designated below as a drive system 2, so that the tailgate K can be automatically pivoted about the pivot axis T for opening and closing a loading space provided in the rear region H of the motor vehicle.

According to Figure 3, the adjusting device 1 comprises a coupling device or a coupling system 3, the input side (drive side) coupled to the drive system 2, so this is downstream. On the output side (output side), the coupling system 3 via transmission elements in the form of a gear Z and a provided with a longitudinal toothing L push rod S with the tailgate K is coupled. For this purpose, the push rod S is on the one hand with the gear Z in engagement and on the other hand with the tailgate K in combination.

The coupling system 3 is thus the drive side with the drive system 2 and the output side with the below also referred to as adjustment 4 tailgate K. connected or coupled. The output-side coupling of the coupling system 3 with the adjusting element 4 can also be effected in the manner indicated schematically in FIG. 2 by means of a tube arrangement which converts a torque generated by the drive system 2 to the adjusting element 4 or to the adjusting element by converting a rotational movement into a translatory adjusting movement Tailgate K transmits. This is thus between two end positions, namely the closed position and the open position, automatically movable. For this purpose, the drive system 2 comprises in an unspecified manner an electric motor whose torque can be translated by means of a transmission into a drive torque M _A N acting on the clutch system 3. This drive torque MAN, which is also referred to below as the drive-side torque, is transmitted via the clutch system 3 and the pipe arrangement to the adjusting element 4 or to the tailgate K for generating the desired adjusting movement.

With the coupling system 3 is to ensure that a closing of the tailgate K under the action of an external force or adjusting force F (Figure 1), which is applied by a vehicle user directly to the tailgate K itself by this takes the tailgate K and in the closed state transferred without damaging the drive system 2 can take place. The same applies to a manual opening of the tailgate K by a vehicle user.

For this purpose, the coupling system 3 is designed such that this is decoupled from the drive system 2 under the action of the outer adjustment force F or a displacement moment caused thereby M _v when a certain threshold value is exceeded to be adjusted motor vehicle part K or adjustment. This allows a manual opening and closing of the tailgate K without damaging the drive system 2 or its electric motor or transmission.

The drive system 2 or the electric motor and / or the transmission as a drive can be self-locking or non-self-locking. In a self-locking drive system 2, the clutch system 3 is effective as a clutch or friction clutch, while the clutch system 3 in a non-self-locking drive system. 2 is effective as a brake or friction brake, which basically corresponds in structure to the friction clutch.

The schematic block diagrams in FIGS. 4a and 4b show the force relationships between drive-side drive system 2 (drive ANS) and drive-side adjustment element 4 (drive output ABS) in a clutch system 3 acting as a clutch or as a brake. As illustrated in Figure 4a, in the clutch is practically indistinguishable, whether a torque from the drive ANS to the output ABS (drive-side torque MAN) or from the output ABS to the drive ANS (output-side rotational or adjusting torque Mv), for example, against a Gegenmoment, is transmitted. Thus, in the case of the clutch, the drive ANS or the output ABS can be coupled to a preferably cylindrical housing or component (hollow body) having the rotationally symmetrical contact surface or be connected to it directly or firmly. In the clutch, the output side and thus effective from the output ABS to drive ANS effective adjustment force F due to the self-locking of the drive system 2, for example, due to the self-locking of the electric motor downstream transmission, introduced into the drive ANS.

According to FIG. 4b, in the case of the brake, the torque MAN of the drive ANS is transmitted via the drive claw N _AN containing the clutch system 3 and to the output ABS via the output claw N _{AB which} can be coupled rigidly thereto. In the opposite direction from the output ABS to the drive ABS, a corresponding output-side torque Mv would occur via the output-side and the drive-side claws NAB. N _A N transferred to the drive ANS, which would rotate due to its non-self-locking. To prevent this, the clutch system 3 is arranged as a brake in the power flow between the output ABS and drive ANS, which is ineffective in the direction of the drive ANS to the output ABS out. Accordingly slips in the transmission of a drive torque MAN on the output side ABS through the frictional engagement element. Only in the opposite direction from the output ABS to the drive ANS out the frictional engagement element is biased in the reverse direction, but then can be suppressed by means of the triggering MOUSE, which in turn corresponds to the coupling effect. In the case of the brake, therefore, the coupling action of the coupling system 3 is given only in one direction (from the output ABS to the drive ANS), while in the coupling the coupling action is in both directions (from the drive ANS to the output ABS and from the output ABS to the drive ANS) given is. The frictional engagement element is then biased in both directions in the reverse direction and can be suppressed by means of the release torque MAUS. The adjusting force F acting on the drive ANS from the output ABS is supported in the rotationally symmetrical housing or component by prestressing the frictional engagement element in the reverse direction. If an output-side adjusting moment M _v exceeds the tripping torque MAUS as a result of a manual actuation of the adjusting element 4, the blocking effect of the frictional engagement element in the blocking or blocking direction is released.

In the clutch, a drive torque MAN acting on the output ABS from the drive ANS is adjusted such that the respective triggering torque MAU _{S is} not exceeded within the torque range generated by the drive system. This

However, the release torque MAUS is reached by the output ABS towards the drive ANS during a manual actuation of the adjusting element 4, so that the clutch slips. Accordingly, if the adjustment element 4 is first actuated in a clutch, but then released again, then the blocking effect of the clutch system 3 is restored when the outer adjustment torque M _{v is} the associated actual torque value M _n (ω), where n = 1, 2, 3, along the respective torque curve Mi to M ₃ or M 'according to FIG. 1 falls below.

In the case of the brake, this also required self-locking is provided by the clutch system 3 itself, otherwise the adjusting element 4 and the tailgate K would fall down in the closing direction on reaching the triggering moment M _A US due to the NichtSelbsthemmung the drive system. Accordingly, the clutch system 3 is effective both as a brake and as a clutch, since otherwise the blocking effect of the clutch system 3 - with reaching a tripping moment MAUS - could not be suppressed. In the case of the brake, the drive ANS always rotates with the output ABS due to the coupling via the drive and output claws N _AN , N _A B. The embodiments described below are in particular a clutch when the drive ANS or the output ABS is formed by the cylindrical component, which is also referred to as an adjusting housing or a ring gear. On the other hand, it is in the embodiments described below, then in particular to a brake when within the component or the ring gear - and surrounded there by the frictional engagement element - driving and driven-side claws or tabs N _A _N> NAB are provided.

5 shows a schematic cross section through a coupling system 3 with a hollow cylindrical component or adjusting housing 10, referred to below as a housing. A frictionally engaging element in the form of a wrap spring 11 is inserted with prestress into the housing 10 and is connected to the housing by frictional engagement , The wrap spring 11 has angled spring ends 11a, 11b. These protrude into the interior, d. H. in the interior of the housing 10, so that depending on the direction of a force attack on the angled spring ends 11 a, 11 b, the wrap spring 11 is expanded and accordingly more or increasingly clamped or contracted with the housing 10. In the case of contraction of the wrap spring 11 reduces its effective diameter, so that the tension is released with the housing 10 and the wrapper 11 slips in the housing 10. The wrap spring 11 can then be rotated about an adjustment axis 12 in the direction of rotation of the force application. The hollow cylindrical housing or component 10 forms the inside wall side, the rotationally symmetrical contact surface 5 as a friction partner of the designed as a wrap spring 11 Reibschlusselementes.

Within the wrap spring 11, a drive element 13 connected to the adjustment axis 12 is arranged, which contains a basic body designed as a slotted cylinder ring with stops 13a to 13d acting in the peripheral direction. Of these are radially outer stops 13a, 13b with play the angled spring ends 11a and 11b of the wrap 11 against. Within the drive element 13, a cylindrical-ring-shaped main body of an output element 14 is arranged rotatably about the adjustment axis 12. The output element 14 has radially projecting claws 14a, 14b which face the radially inner stops 13c and 13d of the drive element 13 with circumferential clearance. Between the angled spring ends 11 a, 11 b of the wrap spring 11 and the claws 14 a, 14 b of the output element 14 is a subsequently referred to as a triggering device G transmission element in the form of a compression spring 15 is arranged. This takes up a driven-side torque M _v up to a definable release moment MAU _S and thus blocks an output-side adjusting force F.

Under the action of a drive-side torque MAN, which starts from the drive system 2 for opening and closing the tailgate K of the motor vehicle, the bias of the wrap spring 11 by conditioning one of the two radially outer stops 13a, 13b of the drive member 13 to one of the two angled spring ends 11a, 11 b of the wrap 11 canceled. Thus, the drive-side torque M _A N can be transmitted to the output element 14 within the housing 10 with simultaneous rotation of the wrap spring 11.

5 shows a schematic illustration of a rotation of the drive element 13 corresponding to the arrow A in a clockwise direction as a result of a drive torque MAN directed toward the drive side ABS from the drive side ANS, while the drive element 14 exerts a counter torque corresponding to the arrow B in the counterclockwise direction. As a result of the drive-side torque MAN, the stop 13a of the drive element 13 engages the angled spring end 11a of the wrap spring 11 on that side which leads to a reduction of the effective diameter of the wrap spring 11. As a result, the tensioning of the wrap spring 11 with the housing 10 is released, so that the frictional engagement between the wrap spring 11 and the contact surface 5 is released and the wrap spring 11 can be rotated within the housing 10 while the output element 14 is entrained.

If, on the other hand, according to the schematic illustration of FIG. 6, an output-side adjusting moment M _{v occurs} in the counterclockwise direction according to the arrow C when the clutch system 3 is not driven, the compression spring 15 between the claw 14b and the spring end facing away from it is rotated via the rotating output element 14 11a compressed. This leads to an increase in the tension of the wrap spring 11 with the adjustment housing 10, so that the output side rotary moment M _{v is} blocked. With reference to a tailgate K of a motor vehicle, the tailgate K is thus held in its open position, for example after an opening of the tailgate K, as a result of a drive-side torque MAN.

With the rotation of the output element 14 as a result of the output-side torque Mv, lifted from the compression spring 15 claw 14a sets under increasing compression of the compression spring 15 against the stop 13c of the drive member 13 and moves this in the same direction of rotation C. After overcoming the triggering path b of the torque curve Mi as shown in FIG. 1 corresponding rotational angle play between the stops 13a, 13b and the angled spring ends 11a, 11 b of the wrap spring 11, the stopper 13b applies to the angled spring end 11 b of the wrap 11, in order subsequently to release the tension of the wrap spring 11 with the housing 10 while generating the release moment MOUS determined by the dimensioning of the compression spring 15. As a result, the wrap spring 11 slips at a constant output or sliding torque M _G i, which is smaller than the release torque M _A US = M _R - |. Thus, the tailgate K can be adjusted with substantially constant force F in the direction corresponding to the arrow C, that is, further opened or closed. The coupling system 3 according to FIGS. 5 to 7, which operates identically in both directions of rotation due to the symmetrical structure, accordingly operates according to the torque curve Mi according to FIG. 1 and as a brake according to FIG. 4b.

8 to 10, an embodiment of the coupling system 3 is shown, which is also effective as a brake according to FIG. 4b and the torque curve M _{1 of} FIG. 1 follows. This embodiment is particularly suitable for a pinch protection.

In the powerless state shown schematically in Fig. 8, the coupling system 3 is in turn aligned symmetrically. Between claws 14a, 14b of the driven element 14 and the angled spring ends 11a, 11b of the wrap spring 11, the triggering device G is in turn arranged with a compression spring 15. In the circumferential direction with a greater mutual distance from each other, second claws 14c, 14d project radially from the main body of the driven element 14, and the larger ones engage radially Game as the stops 13a, 13b of the drive member 13, the angled spring ends 11a, 11b of the wrap 11 are opposite. In this case, the pressure spring 15 as a force element on either side due to tolerances either the angled spring ends 11a, 11b of the wrap spring 11 or between the first jaw 14a, 14b of the output element 14 at. The stops 13a, 13b of the drive element 13 are with circumferential side clearance play the angled spring ends 11a, 11b of the wrap 11 on those sides opposite to the rotation of the drive member 13 to a reduction of the effective diameter of the wrap 11 and thus to a Repeal their tension would lead to the housing 10. The second jaws 14c, 14d of the output element 14 are due to the greater mutual distance the angled spring ends 11a, 11b of the wrap 11 with larger in the circumferential direction, in turn the triggering path b corresponding rotational angle clearance.

A drive-side torque MA _N in one or the other direction of rotation in turn leads to a reduction of the effective diameter of the wrap spring 11, so that their suspension with the housing 10, rotation of the wrap spring 11 takes place in the corresponding direction of rotation with entrainment of the output element 14 ,

Acts on the other hand an output-side torque M _v to the coupling system 3 a, then the conditions schematically illustrated in FIGS. 9 and 10 a. An output-side torque M _v corresponding to the arrow E counterclockwise leads to a co-movement of the output element 14 via the first jaw 14 b. In addition, the compression spring 15 is compressed due to the tension of the wrap 11 with the housing 10 and the consequent fixed position of the angled spring end 11a. After passing through the triggering path b and the rotational angular play and with reaching the triggering moment M _A US solves the angled end of the spring 11 b imposing second jaw 14 d of the output element 14, the blocking of the wrap spring 11, resulting in a reduction of the effective diameter of the wrap spring 11 and Thus, a repeal their tension with the housing 10th Fig. 10 shows a schematic representation of the effect of a clockwise acting according to the arrow P drive-side torque MAN opposite, acting in counterclockwise direction according to the arrow E output-side torque M _v . The drive-side torque MAN leads to an immediate AnIa- ge of the stop 13a at angled end of the spring 11 a and thus to a repeal of the tension of the wrap spring 11. The opposing output-side torque Mv leads only after passing through the trip path b and with the release torque MOUSE TO Slipping of the wrap spring 11 and thus to a manual override of the drive-side torque M _A N-

While in the embodiments according to FIGS. 5 to 7 the force or torque effect of the output element 14 takes place or works in the manner of a parallel connection both against the compression spring 15 and against the drive element 13, the force or moment effect takes place in the embodiment according to FIGS to 10 in the manner of a series connection. This embodiment, in which an additional engine torque of the drive system 2 would not affect the tripping force or the tripping torque MAUS, is therefore particularly suitable in connection with a jamming protection or system of the motor vehicle.

FIG. 11 shows a schematic partial cross section through a further variant of a clutch system 3 effective as a brake according to FIG. 4b, in which the triggering device G has a piston arrangement 16 connected to the output element 14 with two pistons arranged in a housing 20 connected to the output element 14 21, 22 and a pressure spring 17 which presses them apart. The KoI ben 21, 22 are the angled spring ends 11 a, 11 b of the wrap 11 on the side opposite, on the force application to a widening of the wrap spring 11 and thus to a gain of frictional or non-positive engagement of the wrap 11 on the housing 10 leads.

The drive element 13 corresponds to the embodiment according to FIGS. 8 to 10. The stops 13a, 13b are opposed to the angled spring ends 11a, 11b of the wrap spring 11 on the side leading to a reduction in their effective diameter and thus to a repeal or reduction the prestressed plant the wrap spring 11 leads to the contact surface 5 of the housing 10. The output member 14 has, in addition to the piston assembly 16 receiving housing 20 on two claws 14a, 14b, with the greater mutual distance the angled spring ends 11a, 11b of the wrap 11 are opposite to the stops 13a, 13b of the drive member 13. Also in this Embodiment performs a drive-side torque M _AN as a function of the direction of rotation for abutment of one of the two stops 13a, 13b of the drive member 13 at one of the two angled spring ends 11a, 11b of the wrap 11, so that these contracted and thus their tense system on Housing 10 is released.

At a driven-side torque M _v depending on the direction of rotation of one or the other piston 21, 22 of the driven element 14 connected to the piston assembly 16 against one or the other angled spring end 11 a, 11 b pressed. As a result, a force is exerted on one of the two angled spring ends 11a, 11b, which leads to an increase in the tension of the wrap spring 11 with the housing 10. Only when the output-side torque Mv overcomes the biasing force of the arranged between the two pistons 21, 22 compression spring 17 and the trip path b is traversed, is applied to one of the angled spring ends 11a, 11b of the wrap spring 11 piston 21 and 22 in the housing 20 pushed in. In this case, the claw 14b, 14a of the driven element 14 lying opposite the relevant piston 21, 22 passes during the passage of the triggering path b of the torque curve M ₁ according to FIG. 1 to bear against the side of the opposite angled spring end 11a or 11b, respectively with reaching the tripping torque MAU _S TO a reduction of the effective diameter of the wrap 11 and thus to a repeal whose braced system on the housing 10 leads. Thus, in this embodiment as well, the tripping torque MAU _S according to the torque curve Mi of FIG. 1 is almost exclusively determined by the spring force of the compression spring 17 of the tripping device G having this and the piston arrangement 16 and is largely independent of the friction conditions of the clutch system 3.

The embodiment of a clutch system 3 which acts as a brake according to FIG. 4b and is illustrated in a schematic cross section in FIG. 12 represents a kinematic conversion. Turning to the embodiment shown in FIGS. 8 to 10. Instead of a compression spring, the triggering device G has a tension spring 18. Their ends are connected both to first claws 14a, 14b of the output element 14 and to the angled spring ends 11a, 11b of the wrap spring 11. Second claws 14c, 14d of the output element 14 projecting radially from a cylinder-disk-shaped base body are arranged between the first jaws 14a, 14b and thus also between the angled spring ends 11a, 11b of the wrap spring 11. From the likewise a cylindrical disk-shaped base body having drive element 13 is a drive-side driver 23 radially from. This is in the rest position of the coupling system 3 with rotational angular play between the angled spring ends 11a, 11b of the wrap spring 11 and extends there on the claws 14c, 14d on both sides beyond approximately to the claws 14a, 14b of the output element 14th

In the case of a drive-side torque MAN, the drive-side carrier 23 engages, depending on the direction of rotation, against one or the other angled spring end 11a, 11b of the wrap spring 11. The driver 23 causes thereby on the reduction of the effective diameter of the wrap spring 11, a repeal their strained contact with the housing 10 and a corresponding entrainment of the output element 14 via the other angled spring end 11 a, 11 b of the wrap spring 11 and one of the two second jaws 14 c, 14d.

Depending on the direction of rotation, one of the two jaws 14a, 14b of the output element 14 moves beyond the respective spring end 11a or 11b at an output-side torque Mv. In this case, held at the other end of the spring 11 b, 11 a tension spring 18 by means of the corresponding jaws 14 a, 14 b tensioned and consequently the wrap spring 11 increasingly braced against the housing 10 until one of the two second jaws 14 c, 14 d after passing through the triggering path b according to 1 to the torque spring 11a or 11b released from the tension spring 18, and this upon reaching the tripping torque MAUS, resulting in a reduction of the effective diameter of the wrap spring 11 from the contact surface 5 formed by the housing 10 solves. This causes slippage of the wrap spring 11 of the clutch system. 3 The illustrated in FIGS. 13 and 14 embodiments of the again as a brake according to FIG. 4b effective coupling system 3 is based on a modified operating principle in which the triggering device G a driven-side torque M _v until reaching the tripping torque MAUS according to the torque curve M _{3 of} FIG 1 opposes a locking force. For this purpose, the triggering device G, for example, two magnetic elements 24, 25. This, to the angled spring ends 11, 11 of the wrap b 11 adhering magnetic elements 24, 25 detach only then from the angled spring ends 11a, b 11, when an output-side torque M _v a specific value, namely, the triggering moment MAU _S, reached or exceeds. The sliding torque MG ₃ at the end of travel of the tripping path b is then smaller than the tripping torque MAU _S according to the torque curve M ₃ according to FIG.

The clutch system 3 shown in a schematic cross section in FIG. 13 has, analogously to the embodiments described above, a drive element 13 arranged inside the wrap spring 11 with a radially projecting drive side driver 23a and an output element 14 with two claws 14a spaced apart in the circumferential direction , 14b and a driven-side driver 23b. This driver 23b, which is the same as the drive-side driver 23a between the angled spring ends 11a, 11b of the wrap spring 11 is arranged, has a smaller width than the drive-side driver 23a. The two-sided play of the output-side driver 23b to the angled spring ends 11a, 11b of the wrap spring 11 is greater than the two-sided game of the drive-side driver 23a.

The magnetic elements 24, 25 of the triggering device G, between which a weak compression spring 26 is arranged, adhere to the angled spring ends 11a, 11b of the wrap spring 11. The compression spring 26 is used in conjunction with a guide housing 27 for position stabilization of the magnetic elements 24, 25th

In the case of a drive-side torque MA _N , the drive-side carrier 23a engages one of the two angled spring ends 11a, 11b of the wrap spring 11. As a result, the effective diameter is reduced and thus lifted the tight system of wrap 11 on the housing 10. As a result, the other drive-side torque MAN are transferred to the driven element 14 for adjusting the adjustment device 1, taking along the wrapper 11 sliding or sliding along the contact surface 5 of the housing 10.

When acting for example in a counterclockwise output-side torque Mv and according to the torque curve M _{3 of} FIG. 1 with reaching the release torque MAUS triggers the claw 14b of the output member 14, the magnet 25 from the spring end 11 b of the wrap 11 from. After passing through the trip path b of the output side driver 23b presses against the opposite spring end 11a, so that it is released from the contact surface 5 of the housing 10 and the wrap 11 is tightened while reducing their tension with the housing 10.

An advantage of this embodiment is that until reaching the triggering moment M _A US a constant counterforce is effective, namely the magnetic force of the magnetic elements 24, 25, which does not change with the displacement caused by the output-side torque Mv adjustment.

The variant shown in FIG. 14 corresponds in construction and function to the embodiment shown schematically in FIG. 13, with the proviso that, instead of a cylindrical disk-shaped main body, a drive claw is provided as drive element 13. This is arranged between the magnetic elements 24, 25 of the triggering device G and connected thereto by means of weak compression springs 29a, 29b. The claw-like drive element 13 has recesses for receiving the compression springs 28, 29 and stops for the magnetic elements 24, 25, so that when compressed compression springs 28, 29, the magnetic elements 24, 25 abut directly on the claw-like drive element 13. This and the compression springs 28, 29 and the magnetic elements 24, 25 are arranged in a tubular guide means 27, with which the magnetic elements 24, 25 on the angled spring ends 11a, 11b of the wrap spring 11 and the claws 14a, 14b of the output element 14 are aligned ,

With a drive-side torque MAN in one or the other direction of rotation, the claw-type drive element 13 presses on one or the other magnet This presses on one of the two angled spring ends 11a, 11b of the wrap spring 11, so that their bias is canceled by reducing the effective diameter and the rotational movement of the drive member 13 is transmitted to the output member 14.

With a driven-side torque M _v , the mode of action of this clutch system 3 is analogous to the mode of operation of the clutch system 3 according to FIG. 13.

The coupling system 3 according to FIGS. 5 to 14 has a simple and robust construction and can be produced with few components. An adjustment is up to the predetermined release torque MAUS, with the clutch system 3 can be suppressed for a transition to a freewheeling operation, regardless of friction conditions safely blocked, while with the achievement of the triggering MOUSE and after passing through the triggering path b an adjustment is ensured. When the torque increases, the frictional engagement element in the form of the wrap spring 11 does not slip before it reaches the release torque MAUS and thus blocks an unintentional adjustment of an adjustment element 4. After reaching the release moment MAU _S on the one hand and the travel end of the release travel b on the other hand, the output side adjustment is Adjustment element 4 or an actuation of the tailgate K with constant counterforce or constant counter or sliding torque MQ allows.

The force effect of the tripping device G is directed counter to the force of a driven-side torque Mv such that the output element 14 acts directly or indirectly on the angled spring ends 11a, 11b of the wrap spring 11 in the sense of increasing their effective diameter. This ensures that the setting of the tripping torque MAU _S depends solely on the force or force of the triggering device G and thus is independent of the coefficient of friction. Upon reaching this release torque M _A US and after passing through the trip path b, the output-side torque M _v leads to a reduction in the effective diameter of the wrap spring 11 and thus allows a further adjustment of the adjusting device 1 with constant counterforce. When using a spring element 15 to 18 whose spring force of the force of a driven-side torque M _{v is} opposite. Upon reaching a triggering moment MOUSE corresponding force and after passing through the triggering path b, the length of the spring element 15 to 18 has changed by such a degree that the triggering device G indirectly or directly on the angled spring ends 11a, 11b in the sense of reducing the effective Diameter of the wrap spring 11 acts.

The coupling system 3 described is based on friction and contains as a friction closing element z. B. a wrap spring 11 which rests with bias on the rotationally symmetrical contact surface 5 of the cylindrical member or adjusting housing 10 and the spring ends 11 a, 11 b are angled from the voltage applied to the cylindrical contact surface 5 part of the wrap 11. The angled spring ends 11a, 11b act with the about an adjustment axis 12 of the adjusting device 1 rotatable drive element 13 - and this with the drive system 2 - and with the output element 14 - and this with the adjusting element 4 - in such a way that a drive-side torque M _A N of the drive ANS with reduction of the effective diameter of the wrap spring 11 substantially frictionless to the output ABS is transmitted. In contrast, a driven-side torque M _{v is} blocked up to a predetermined release torque MAUS, which is smaller than a producible by bracing the wrap 11 with the housing 10 holding torque M _H. Only when the holding torque M _H suppressed output-side rotation or release torque MAU _S , the tension of the wrap 11 is solved with the housing 10 so that the wrap spring 11 can slip along the corresponding contact surface 5 and the output side torque M _v or a driven-side adjusting F is transmitted to the drive element 13. As a result, for example, an electric motor open tailgate K can be adjusted manually.

An adjusting device 1 of the type mentioned and their components are therefore before damage or destruction upon exposure to an external adjustment force F on the tailgate K, for example, by manually opening and closing the tailgate K and / or manual tailgate operation in case of failure of the electric motor drive system. 2 protected. Between the drive and output 2 or 4 provided clutch system 3 in the form of a friction brake or clutch secures a set by means of the electric motor drive system 3 opening angle of the tailgate K.

The effective as a slip clutch according to Fig. 4a or in the manner of a Gehemmes

Coupling system 3 for force or torque transmission according to the torque curve M ₂ or lying between this and the torque curve M ₃ torque curve M 'according to Figures 15a and 15b comprises a planetary gear 30 with a driven by the drive system 2 central sun gear 31 and z. B. three with the sun gear 31 engaged and driven by this outer planetary gears 32 to 34. These roll on the inner gear surface 35 of a rotational axis 31a of the sun gear 31 concentrically surrounding, hereinafter referred to as a ring gear cylindrical member or housing 10 and are supported while on the inner gear surface 35 from. The planetary gear 30 can be designed as a gear transmission with corresponding external teeth of the sun gear 31 and the planetary gears 32 to 34 and an associated internal toothing on the inner gear surface 35 of the ring gear 10. Alternatively, the planetary gear 30 may be designed as a friction gear with corresponding outer friction surfaces on the sun gear 31 and the planet wheels 32 to 34 and an associated, designed as a friction surface inner gear surface 35 of the ring gear 10.

The planetary gears 32 to 34 form the output ABS of the clutch system 3 by their axes of rotation 32 a, 33 a and 34 a mounted together on a (not shown) output member (14), which in the orbital motion of the planet gears 32 to 34 along the inner gear surface 35 of Ring gear 10 performs a corresponding rotational movement. This driven element is in turn operatively connected on the output side with the transmission system 3 downstream of the transmission elements Z, L, S (FIG. 3).

An in turn designed as a wrap 11 Reibschlusselement acts with its inner surface 36 on a rotationally symmetrical outer friction or contact surface 5 of the ring gear 10 a. A ring gear 10 located outside of the moving parts formed by the sun gear 31 and the planetary gears 32 to 34 allows a ring gear 10 Transmission of the drive side introduced from the drive system 2 via the sun gear 31 in the clutch system 3 torque MAN via the planetary gears 32 to 34 on the output ABS and thus on the adjusting element 4. A from the output ABS to the drive ANS effective adjusting moment M _v is in blocking or braking state of the ring gear 10 at this past and in the release state on this passed.

The two angled spring ends 11a, 11b of the wrap spring 11 are mounted in a housing 37. This also takes a triggering device G with a screw or compression spring 38 and a lever assembly 39 with two in a knee joint 39a pivotally interconnected levers 39b, 39c. The

Compression spring 38 is supported with a spring end 38a on a bottom surface 37a of the housing 37 and with the other spring end 38b on the lever assembly 39 in the region of the knee joint 39a.

The biased by the compression spring 38 levers 39b, 39c of the lever assembly 39 cause the two spring ends 11a, 11b are pressed apart and thereby the wrap spring 11 is biased such that it presses with its inner surface 36 against the outer contact surface 5 of the ring gear 10 , For this purpose, each one of the two levers 39b, 39c acts on one of the two spring ends 11a and 11b of the wrap spring 11.

The spring constant of the compression spring 38 and thus the biasing force generated by this is chosen such that the generated by the drive system 2 and introduced via the planetary gear 30 in the clutch system 3 torque M _AN does not lead to a rotation of the ring gear 10. The ring gear 10 is thus held against rotation during normal operation of the adjusting device 1 - that is to say when the drive system 2 is energized and thus during engine operation - by means of the wrap spring 11. The clutch system 3 according to FIGS. 15 a and 15 b is effective as a clutch according to FIG. 4 a and behaves in accordance with the torque curve M ₂ according to FIG. 1.

The degree or degree of spreading of the two spring ends 11a, 11b and thus the moment at which the wrap spring 11 abuts with its inner surface 36 on the outer contact surface 5 of the ring gear 10 is limited by the fact that the two the lever 39b, 39c of the preloaded by the compression spring 38 lever assembly 39 with projecting from the bottom surface 37a wall portions 37b and 37c of the housing 37 are brought into abutment. Therefore, if the two levers 39b, 39c have taken an angular position in which they are supported on the wall sections 37b, 37c of the housing 37, the distance between the two spring ends 11a, 11b and thus the maximum moment with which the wrap 11th with its inner surface 36 can act on the outer contact surface 5.

In the clutch system 3 according to FIG. 15a, on the output side, an external rotational or adjusting torque Mv is introduced via the output element 14 supporting the planetary gears 32 to 34, which torque is greater than the torque resulting from that force, which the compression spring 38 actuates via the levers 39b. 39 c on the spring ends 11 a, 11 b of the wrap 11 exerts. As a result, under the action of the external torque M _v introduced via the planetary gears 32 to 34, the ring gear 10 is twisted together with the wrap spring 11, overcoming the biasing force of the compression spring 38 in the effective direction of the external moment M _v . Depending on the direction of rotation, one or the other spring end 11a, 11b of the wrap spring 11 then engages with a housing-side stop 37c or 37d provided for this purpose.

The respective housing-side stop 37c, 37d is arranged such that the according to FIG. 15b pressed against the corresponding housing-side stop 37c spring end 11a is no longer in engagement with the associated lever 39b of cooperating with the compression spring 38 lever assembly 39. While this is supported on the wall portion 37b of the housing 37, the respective other lever 39c of the lever arrangement 39 continues to act on the associated, other spring end 11b of the wrap spring 11.

As a result of the interaction of the one spring end 11a with the associated housing-side stop 37c, the wrap spring 11 is converted by deformation or widening into a state in which a slipping or twisting of the ring gear 10 with respect to the wrap spring 11 is possible. In this case, by the triggering device G a sliding moment of friction MG2 corresponding to its spring torque is generated, which in turn is smaller than the friction torque M _R2 . If the adjustment torque M _v introduced from the outside or a corresponding adjustment force F is canceled or at least reduced to such an extent that the pretensioning force of the compression spring 38 can no longer be overcome, the wrap spring 11 absorbs the spring ends 11 a, 11 under the action of the lever arrangement 39 B transferred forces again the work or rest state shown in Figure 15a. The ring gear 10 is then again held against rotation under the action of the drive side introduced by the drive system 2 forth torque MAN.

The frictional engagement element of the clutch system 3 in the form of the wrap spring 11 according to FIGS. 15a and 15b, which can be coupled on the input side with the drive system 2 and on the output side with the adjustment element 4 of the adjustment device 1 of a motor vehicle, acts in the power flow between the drive system 2 and the adjustment element 4 lying component in the form of the ring gear 10 to hold this in a defined position with respect to the wrap spring 11. The wrap 11 is by means of the triggering device G against the associated component

10 biased.

Under the action of a force introduced on the output side 4 on the adjustment 4 or adjusting force F (adjusting moment M _v ), the wrap spring 11 can be brought into a deformed state in which the adjusting element 4 is decoupled from the drive system 2 such that the adjusting element 4 under the Exposure of the external force F can be adjusted. For this purpose, a spring end 11a, 11b of the wrap spring 11 can be brought into engagement with a stop 37c, 37d under the action of the external force F (adjusting moment M _v ) introduced on the output side in order to trigger the deformation of the wrap spring 11. In the deformed state of the wrap spring 11, the triggering device G engages the other end of the spring 11 b and 11 a, to counteract the deformation of the wrap 11. The triggering device G acts in the working state of the wrap

11 directly or via the lever arrangement 39, in particular with two levers 39b, 39c pivotable relative to one another on a knee joint 39a, indirectly on both spring ends 11a, 11b of the wrap spring 11. This is rotated at the initiation of the output side force F (adjusting torque Mv) together with the associated component 10 of the clutch system 3 against the action of the triggering device G, so that a Fede- rendθ 11a, 11b of the wrap spring 11 engages with the associated stop 37c, 37d.

In the coupling systems 3 shown in FIGS. 16 and 17, which act as a coupling according to FIG. 4a for force or torque transmission in accordance with the torque curve Mi according to FIG. 1, a cylindrical component or ring gear 10 forms an output element 14 which is connected to the adjusting element 4 in the form, for example, in turn, a tailgate K of a motor vehicle can be coupled. The rotationally symmetrical inner wall of the adjusting housing 10 forms the contact surface 5, with which in turn cooperates a Schlingefeder 11 as frictional engagement element.

A coupling of the coupling system 3 with the drive system 2 via a running in the manner of a central, for example rectangular shaft drive element 13 on which a cam lever 40 is disposed radially displaceable against the force of a weak compression spring 41. For this purpose, the shaft or axle-like drive element 13 is guided in a slot 40 a of the cam lever 40. The cam lever 40 is formed oval or elliptical, wherein the slot 40a extends in the longitudinal direction y. The cam lever 40 has a cam 40b, which is positioned according to the illustrated coordinate system in the longitudinal direction y to the slot 40a and thus to the drive element 13 at a distance.

The cam 40b of the cam lever 40 engages in intersecting slot-like or slightly arcuate slotted guides 42a, 43a of lever members 42, 43 which are each rotatably mounted on the drive member 13 via a central opening 42b, 43b. The width of the arcuate slotted guides 42a, 43a is greater than the diameter of the cam 40b. The lever elements 42, 43 are each connected via a tension spring 44, 45 with a spring end 11 a and 11 b of the wrap spring 11. For this purpose, two spreading fingers 42c, 42d and 43c, 43d are integrally formed on the lever elements 42, 43, of which a spreading fingers 42c, 43c at the respective spring end 11a and 11b of the wrap spring 11, while the other spreading fingers 42d, 43d to this order approximately the length of the tension spring 44 and 45 is spaced. The side facing away from the cam 40b side of the drive element 13 in the slot 40a of the cam lever 40 and on the one hand on the drive element 13 and on the other hand acting as an abutment narrow edge 40c of the slot 40a of the cam lever 40 supporting compression spring 41 causes the cam 40b against both Flanks 42e, 43e of the arcuate slots or slide guides 42a and 43a is pressed. The cam 40b has in the slide guides 42a, 43a no self-locking and therefore - depending on the position of the spring ends 11a, 11b of the wrap 11 - dodge in the y direction. However, a radial deflection of the cam lever 40 is prevented at a force acting on the drive member 13 Antriebsmo- MAN MAN by the flattened drive member 13 in the slot or longitudinal slot 40a of the cam lever 40 canted.

In this embodiment according to FIG. 16, the release device G is formed, in particular, by the tension springs 44, 45 and the slide guides 42a, 43a or their flanks 42e, 42f or 43e, 43f.

As a result of a drive torque M _A N or an adjusting moment M _v , depending on the direction of rotation, the cam 40b is pressed against the respective flank 42e, 43e of the arcuate slots or slide guides 42a, 43a, so that the respective lifting element 42, 43 simultaneously Clamping of the tension spring 44 and 45 and by passing through a triggering path b rotates. After passing through the triggering path b of the cam lever 40b reaches the opposite edge 43f, 42f of the other lifting element 43, 42, which then over the corresponding spring end 11b, 11a cooperating spreader fingers 43c and 42c, the blocking of the wrap spring 1 1 solves.

The clutch system 3 according to FIGS. 17a and 17b, which in turn is operative according to the torque curve Mi (FIG. 1) and the clutch according to FIG. 4a, is an embodiment with a boost lever V. This is connected to each other at an angle of approximately 180 ° opposite spring ends 11 a, 11 b of the wrap 11 held or fixed. Instead of tension springs compression springs 46 'and 47' are provided which einliegen in recesses 48 and 49 of the gain lever V. These Recesses 48, 49 are aligned with corresponding recesses 50, 51 of the lever elements 42 and 43, which are effective as transmission levers.

In this embodiment according to FIG. 17, the triggering device G is formed by the s compression springs 46 ', 47' and the slide guides 42a, 43a and their flanks 42e, 42f and 43e, 43f.

Likewise, a drive torque M _A N introduced via the drive element 13 into the clutch system 3 also causes an output-side adjusting torque Mv via the hollow o 10 initially via the boost lever V to reliably block or block the wrap spring 11, if only slightly is biased. The reason for this is that a depending on the direction of rotation on one of the spring ends 11a, 11b acting force on the booster lever V also acts on the opposite other spring end 11b and 11a in the reverse direction of the wrap. 5

However, an output-side adjustment torque Mv or a drive torque MAN, in turn, during the passage of the triggering path b, depending on the direction of rotation initially to an increasing compression of the corresponding compression spring 46 'or 47', with the result of increasing tension of the coil spring 11. After running through the trip path b and with increasing compression of the opposing compression spring 47 ', 46' due to the lever action by means of the corresponding lifting element 43, 42, the corresponding spring end 11 b or 11 a again loaded in the blocking direction, but in the direction of a decrease in the effective diameter of the wrap spring 11, so that their blocking is solved again. 5

In this embodiment, the sliding torque MGI corresponds to the spring moment of the compression spring 46 ', 47' plus the driving torque of the wrap spring 11. However, this driving torque goes to zero, on the one hand, the biasing moment of the wrap spring 11 due to the reinforcing effect by the gain lever V o is very small. On the other hand, the release of the blocking of the wrap spring 11 acts on the reinforcing lever V turn on both spring ends 11 a, 11 b, so that they are lifted at the same time from the contact surface 5 of the ring gear 10. This leads to an overall comparison with the embodiment according to FIG. at the same time low sliding moment M _GI and thus to a correspondingly comfortable variant.

In the embodiment according to FIG. 18, in turn, a wrap spring 11 bears against the cylindrical inner wall of a hollow-wheel-like component 10 which acts as a contact surface 5 under prestress. The ring gear 10 forms the output side ABS and thus the output element 14 of the clutch system 3. A turn inwardly angled spring end 11a of the wrap spring 11 is surrounded by a mounted on a central axis 52 of the clutch system 3, hereinafter referred to as a lever member 42 transmission lever, which with a nose 42g with the interposition of a bolt 55 an actuating lever 53 faces. The lever member 42 and the actuating lever 53 are braced against each other by means of a tension spring 54. For this purpose, the tension spring 54 is held, on the one hand, on a cam 42h arranged or formed on the lever element 42 and, on the other hand, on the free bolt 55, which rests in a trough-shaped contact contour 53a of the actuating lever 53 and is supported there.

On a arranged on the central axis 52, approximately rectangular drive element 13 is a spring-loaded or spring-loaded by means of a compression spring 41 slide-56 arranged with a penetrated by the drive member 13 slot-like recess 56a and 56b with a cam arranged in an obliquely extending longitudinal slot 53b of the actuating lever 53 intervenes. The spring force of the compression spring 41 causes a contact of the cam 56b of the driving slide 56 on the inner surface contour or flank 53c of the longitudinal slot 53b of the actuating lever 53rd

The same arrangement with a lever element or transmission lever and with an actuating lever and with another tension spring and another free bolt is mirror-symmetrical to the central axis 52 within the ring gear 10 in cooperation with the other spring end 11 b of the wrap spring 11 is provided, but omitted for clarity ,

In this embodiment of Fig. 18, the triggering device G is formed by the springs 54, the bolts 55 and the contours or control edges 53 a and 42 j. In an effective counterclockwise drive torque MAN on the drive member 13 and a clockwise effective output side adjusting torque Mv on the ring gear 10 corresponding or cooperating with the output member 14 initially leads to tilting of the drive member 13 in the slot-like recess 56a of the driving slider 56th Thus the nose or cam 56b of the follower slider 56 is pressed against the inner surface or flank 53c of the operating lever 53. As a result, the operating lever 53 tends to rotate against the force of the tension spring 54 by the operating lever 53, the free pin 55 in the direction of the spring ends 11 a and 11 b pushes up.

After lying within the trip path b, comparatively short path portion of the bolt 55 slips due to the inclined contact surface of the actuating lever 53 to the transmission lever 42 with the result that the force or torque according to the torque curve M _{2 of} FIG. 1 along the remaining tripping path b drops relatively quickly or severely. Towards the end of the trip path b down the cam 56b of the follower slider 56 contacts the inner edge 53c opposite the outer edge 53d of the longitudinal slot contour of the actuating lever, not shown, which cooperates via the lever member also not shown with the opposite end of the spring 11 b of the wrap 11 and this in the direction contracting decreasing diameter. As a result, the drive element 13 and the output element 14 of the coupling system according to FIG. 4 a effective coupling system 3 are decoupled from each other.

Since the bolt 55 rests on the path end of the triggering path b and in particular in the region c of FIG. 1 on a sloping contour 42j of the lever member 42, the bolt 55 slips back on returning the operating lever 53 and there in the recess 53a, so that the coupling system 3 is stretched again.

A coupling system 3, which is also effective according to the torque curve M ₂ (FIG. 1) and as a clutch (FIG. 4 a), having a boost lever V is shown in FIG. 19. The reinforcing lever V is in turn held at the opposite at an angle of about 180 ° spring ends 11a, 11b of a wrap spring 11, which also rests with low bias in a hollow cylindrical member or ring gear 10. In In this embodiment, the hollow cylindrical member 10 forms the drive member 13, while the output member 14 by two claws 14a, 14b and provided on the opposite side of the gain lever V, cup or circular arc-shaped claw 14c within the ring gear 10 and the wrap spring 11 is formed.

Between the output claws 14a and 14b protrudes an approximately U-shaped spring lever 57, the U- or spring legs 57a, 57b are supported on a power lever 58 freiendseitig. The power lever 58 is clamped to the spring lever 57 via a tension spring 54. The power lever 58 is rotatable about the central axis 52 and spaced apart with its lever arms 58a, 58b at a certain clearance to the boost lever V.

In this embodiment of FIG. 19, the triggering device G is formed by the spring 54 and the spring lever 57. Also, the power lever 58 of the triggering device G be assigned.

Depending on the direction of rotation, one of the output claws 14a, 14b presses against the upper end of the biased spring lever 57. As a result, the power lever 58 rotates about the central axis 52 until one of its lever ends or lever arms 58a, 58b against the cooperating with the spring ends 11a, 11b of the wrap spring 11 reinforcing lever V suppressed. The gain lever V distributes the applied force on both spring ends 11a and 11b of the wrap spring 11, with the result that it is increasingly blocked with a corresponding reinforcing effect.

Upon reaching or exceeding the toggle or vertex d within the trip path b of the torque curve M ₂ or M 'shown in FIG. 1, the spring lever 57 tilts as a result of its storage in corresponding contact contours 58c, 58d of the power lever 58 via one of the spring legs 57a, respectively 57b. As a result, the tension spring 54 is increasingly stretched or tensioned with decreasing lever arm, which in turn leads to a torque reduction within the triggering path b from the vertex d of the torque curve M ₂ according to FIG. In this case, the wrap 11 is again blocked within the trip path b continues. As a result of a corresponding angle of rotation, depending on the direction of rotation, the circular arc-shaped output claw 14c abuts against the amplification lever V at the end of the triggering path b. The corresponding spring end 11a, 11b of the coil spring 11 is then moved in the direction of decreasing diameter , Due to the coupling of the spring ends 11a and 11b via the reinforcing lever V and the opposite spring end 11b and 11a is applied in the direction of decreasing diameter of the wrap spring 11. Consequently, the blocking of the wrap spring 11 is released so that the coupling system 3 decouples the drive element 13 from the output element 14 and thus the output side ABS from the drive side ANS, generating the sliding torque M _G 2.

In a drive system 2 without self-locking, the clutch system 3 according to FIG. 19 can also be used as a brake according to FIG. 4b. In this case, the ring gear 10 are fixed and the drive member 13 operates in a manner not shown in the form of a claw or nose parallel to the output claw 14c of the output member 14th

FIG. 20 again shows an embodiment of the coupling system 3 with a wrap spring 11, whose spring ends 11a, 11b, which are opposite each other by approximately 180 ° and bent inwards, cooperate with a reinforcement lever V. The mode of operation of this clutch system 3 in the manner of a brake device of a ring gear 10 without drive or drive element is analogous to that according to FIG. 15.

In the ring gear 10 is a coil spring 11 with slight bias on the contact surface 5 forming inner wall. In which the inwardly angled spring ends 11a, 11b of the wrap spring 11 embracing the gain lever V are two tilting slide 59a, 59b pressed by the legs of a mounted on the gain lever V torsion spring 60 against stops 61a, 61b. In recesses 59c, 59d of these slides 59a, 59b engage two operating levers 53 'and 53 "mounted on the central axis 52. Between horizontal lever ends 53d, 53e the actuating lever 53', 53" on the one hand and lugs 59e, 59f of the slide 59a or 59a, respectively. 59b others On the other hand, a weak compression spring 48, 49 is arranged in each case. In two intersecting slots or longitudinal slots 53'b, 53 "b of vertical portions of the actuating lever 53 'and 53" protrudes into a nose or cam 56b of a slider 56, which is mounted in a stationary housing 62 and a compression spring 41 is pressed in the direction of the central axis 52.

In this embodiment according to FIG. 20, the triggering device G is formed in particular by the torsion spring 60 and the tilting slides 59a, 59b.

Due to the permanently acting spring force of the compression spring 41, the slide 56 mounted in the housing 62 is permanently against the inner surfaces or flanks 53'c, 53 "c of the oblong holes 53'b and 53" b without play. The abutment angles are selected such that the cam 56b of the slide 56 does not hinder a tolerance-induced rotation of the spring ends 11a, 11b of the wrap spring 11 and thus of the elongated holes 53'b, 53 "b, one of a flank 53'c or 53 "c directed toward the cam 56b causes tilting of the slider 56 in the housing 62, which leads to self-locking, so that the slider 56 does not evade.

As a result of acting on the output member 14 in the form of the ring gear 10 Abriebungs adjusting torque Mv in a rotational direction or in consequence of a drive torque M _AN in the opposite direction effective forces are indirectly via the gain lever V in the spring ends 11a, 11 b of the wrap spring 11 initiated ,

If, for example, an output force F is introduced at a distance k from the spring end 11a, this force F is distributed into a first force Fi and a comparatively small second force F ₂ according to the relationships:

F ₁ = F ^■ (2h + k) / (2h + 2k) F ₂ = F ^■ k / (2h + 2k)

The force F ₁ driving the wrap spring 11 in a rotational movement counteracts the force F ₂ acting in the opposite direction. While the force F ₂ is much smaller than the force _f1. However, the ^coefficient of rope friction m = e ^{μω of} the windings of the wrap spring 11 ^resting against the contact ^surface 5 is sufficient in order to be independent of the ^{proce- dure.} Voltage of the wrap spring 11 to prevent slippage of the wrap spring 11 against or along the contact surface 5 and thus of the ring gear 10 as a result of the force F ₁ . The bias of the wrap spring 11 is only required to initiate a force in the wrap spring 11 and to avoid a detachment of the wrap spring 11 from the ring gear 10.

When a force acts at the same point in the opposite direction, two forces act in the opening direction on the spring ends 11a, 11b. In this case, the wrap spring 11 is supported on the actuating levers 53 ', 53 "contracts with decreasing diameter, so that the output element 14 with respect to the mutually coupled internal structure of the clutch system 3 with the gain lever V, the operating levers 53', 53", the Drive element 13, the sliders 56 and 59a, 59b and the wrap spring 11 can rotate smoothly.

Upon rotation of the output element 14 this or the ring gear 10 tries to take the slightly biased wrap spring 11 and with this also the said internal structure of the clutch system 3. However, this is prevented by the slide 62 mounted in the housing 56, with his slider end-side cam 56 b is supported on the inner surface of the operating lever 53 'in a clockwise rotation on the inner surface of the operating lever 53. The supporting force is transmitted to the left spring arm via the horizontal lever end 53d of the operating lever 53' and the tilting slider 59a 60a of the torsion spring 60 or via the horizontal lever end 53c of the actuating lever 53 "and the tilting slide 59b passed to the right spring arm 60b of the torsion spring 60. At a force resulting from an adjusting moment Mv above the biasing force of the torsion spring 60, the tilting slide 59a or 59b differs.

As a result of the force separation or lever arm between the force F and the spring force, a torque is produced, for example, on the tilting slide 59a, which presses the lower surface or nose 59e in the direction of the region of the reinforcement lever V below the spring end 11a. After a short, lying within the trip path b actuating travel of the tilting slide 59a, this therefore differs in the direction of the spring end 11a of the wrap 11 and gives the lever end 53d of the operating lever 53 'free. While the tilting slide 59a remains held on the reinforcing lever V, the actuating lever 53 'can still turn counter to the spring force of the compression spring 48 by such a short distance within the triggering path b until the nose or cam 56b of the slide 56 approaches that of the inner flank 53 "c opposite outer edge 53" d of the longitudinal slot 53 "b of the actuating lever 53" abuts. At the end of the trip path b, in turn, the blocking of the wrap spring 11 is released, so that the coupling system 3 effective as a brake according to FIG. 4b is decoupled. The sliding moment MG2 resulting from the torque progression M ₂ , M ₃ or an intermediate torque curve M 'corresponds approximately to the moment of the weak compression springs 48, 49.

If the force on the contact surface 5, then the compression spring 60, the respective actuating lever 53 ', 53 "push back again after it is engaged in the recess 59c, 59d of the tilting slide 59a and 59b.

The slider 56 may also be externally actuable by means of a motor or the like. The slider 56 can then be pulled outward until the cam 56b bears against the outer flanks 53'd, 53 "d of the longitudinal slots 53'b, 53" b, so that the actuating levers 53 ', 53 "are rotated and the wrap spring 11 As a result, in turn, the driven element 14 - and in a variant, not shown in detail, the drive element 13 integral with the output element 14 - with respect to the mutually coupled internal structure of the coupling system 3 with the lever V, the operating levers 53 ', 53rd ", the slides 56 and 59a, 59b and the wrap 11 rotate freely and the adjustment run smoothly.

The section through a coupling system 3 of an adjusting device 1 shown in FIG. 21 again shows a cylindrical component or housing 10, in the hollow-cylindrical interior of which a frictional engagement element in the form of a wrap spring or expansion belt 11 'with a single turn is inserted with prestressing , The spreader 11 'has a plurality of spring ends 11' a to 11 'd, of which outer, cranked spring ends 11'a, 11'b at the end of the spreader 11' are arranged. At the ends angled support arms 11 'c, 11'd of the spreader 11 'are formed inner spring ends. Within the expansion band 11 ', four drive cams or claws 13a to 13d of a drive element 13, which are rotatable relative to each other about an adjustment axis 12, are provided, which in turn is connected to a manual or electromotive drive system 2.

An output element 14 which is plugged onto the adjustment axis 12 with a bore 14j (shown hatched on the right) has output cams or claws 14a, 14b arranged symmetrically with respect to the adjustment axis 12. These are the angled support arms 11 'c and 11'd of the spreader 11' opposite. Two stops 14f, 14g of the output element 14, which are radially remote from the articulation on the adjustment axis 12, interact with two of the drive cams 13c and 13d of the drive element 13, respectively. The distances between the drive cams 13a, 13b and the spring ends 11'a and 11'b are equal to the distances between the drive cams 13c, 13d and the stops 14f, 65a and 14g, 65b, respectively.

Within the spreading band 11 'is additionally arranged (shown hatched on the left) reinforcing lever V, which is attached via a slot 63a on the adjustment axis 12. With the different hatching of the output element 14 and of the amplification lever V, the coverage area of both parts is shown hatched crosswise.

The reinforcing lever V has a lever arm 63b, with play between the outer bent spring ends 11 'a, 11'b of the spreader 11' and with side edges 63c, 63d also with play the angled support arms 11'c and 11 'd of the spreader 11 'faces. At the end diametrically opposite the lever arm 63b, the amplification lever V has a recess 64 which substantially coincides with a recess 14e of the output element 14.

In the initial state shown in Fig. 21, thus, the recesses 14e and 64 are aligned with each other. Two stops 65a, 65b of the amplification lever V arranged laterally of the recess 64 are analogous to stops 14f, 14g of the output element 14 in the range of movement of the drive claws 13c and 13d of the drive element 13. The drive claws 13a, 13d of the drive element 13 are in the rest position. or starting position of the adjusting device 1 to the mutually away flanks of the bent spring ends 11 'a, 11' b of the spreader 11 'and the stops 14f, 65a and 14g, 65b of the output element 14 and the gain lever V the same distance.

A triggering device G for torque control disposed within the recesses 14e, 64 of the output element 14 or the amplification lever V has a lever arrangement 66 with two toggle levers 66b, 66c connected to one another via a lever joint 66a and a tension spring 67. This connects two first lever arms of the toggle lever 66b, 66c with each other. The toggle levers 66b, 66c abut with respective second lever arms on the circumferentially opposite sides of the recesses 14e, 64 of the output element 14 and the amplification lever V, respectively.

If a torque M _{v is} exerted on the output element 14 in a clockwise direction, the edge of the recess 14 e of the output element 14 resting against the second knee lever 66 c presses against the second knee lever 66 c. In this case, the first knee lever 66b is supported on the lateral flank of the recess of the reinforcement lever V. The toggle lever 66b, 66c against the lateral flanks of the recesses 14e, 64 biasing tension spring 67 clamps the arranged at a shallow angle knee lever 66b, 66c. In the initial or inoperative position of the adjusting device 1, the coupling system 3 thus generates a relatively large holding moment M _H.

Since, in the rest or initial position of the adjusting device 1, as a result of the tension spring 67 connecting the toggle levers 66b, 66c, the first knee lever 66b pushes away the lateral flank of the recess 64 of the reinforcement lever V in the clockwise direction, the lever arm 63b of the reinforcement lever V presses against the opposite to the bent bent end of the spring 11 'a aligned flank of the bent spring end 11' b. As a result, the spreader 11 'endeavors to also rotate in a clockwise direction. At the same time, however, the reinforcement lever V is supported with approximately twice the force with its side flank 63a on the support surface of the angled spring arm 11'c. Due to the wrap-around reinforcement of the expansion band 11 'thus its slippage is prevented in the clockwise direction. Since with increasing output-side turning or adjusting torque M _v and the friction or Increased braking torque accordingly, there is a self-reinforcing effect or locking effect in the manner of a Reibgesperres. A very small bias of the spreader 11 'thus already enough to block the frictionally engaging element designed as a spreader 11'. An output-side adjusting torque Mv is therefore blocked as a result of acting on the adjusting element 4 of the adjustment 1 adjusting force F to produce a correspondingly large holding torque M _{H of} the clutch system 3.

Due to the blocked gain lever V remains as shown in FIG. 22, the recess shown in solid line 64 of the gain lever V. In contrast, the shown with a thin solid line recess 14e of the output member 14 moves due to the output side torque in a clockwise direction. Consequently, the knee levers 66b, 66c are compressed against the action of the tension spring 67 due to the mutually displaceable recesses 14e, 64 via the lever joint 66a. As a result, a large change in the angle between the toggle levers 66b, 66c occurs. A tripping torque M _A us generated by the tripping device G formed by the lever arrangement 66 and the tension spring 67 therefore drops to a small part of the initial value in the rest or starting position. To the same extent, the tilting of the gain lever V and thus the jamming of the spreading belt 11 'is repealed. In this case, after a certain angle of rotation ω, which corresponds to the elastic triggering path b according to FIG. 1 of the torque curve M2 shown schematically there, the stop 14a of the output element 14 presses against the angled spring arm 11'c of the spreading band 11 '. As a result, the spread belt 11 ', which is only slightly strained, can be rotated in the clockwise direction against a small sliding torque MG2 caused by its contact with the contact surface 5 of the housing 10.

By dimensioning the triggering device G for torque control, for example by determining the spring constant of the tension spring 67 and by the interpretation of the lever arms or toggle 66b, 66c of the lever assembly 66, a triggering MOUSE can be defined, up to which the coupling system shown in FIG blocked a driven-side rotational or adjusting torque Mv. When reaching or exceeding the tripping torque MAUS and after passing through the tripping seweges b according to the torque curve M _{2 of} FIG. 1, the tilting of the gain lever V is reduced, and thus the output side adjustment torque M _v transmitted to the drive system 2. If, on the other hand, the output-side adjusting moment Mv drops as a result of, for example, a reduction of the adjusting force F on the adjusting element 4 below the tripping moment MOUSE, then the lever arrangement 66 is again braced as a result of the tension spring 67, with the result that the amplification lever V becomes more or less tilted. In conjunction with the wrap-around reinforcement of the spreading belt 11 ', in turn, its slippage along the contact surface 5 is prevented, so that the output-side adjusting moment M _{v is} blocked.

In the case of a drive-side torque or drive torque M _A N, depending on the direction of rotation, one of the two lower drive claws 13 c, 13 d of the drive element 13 abuts against the mutually aligned stops 14 f, 65 a or 14 g, 65 b of the output element 14 or the amplification lever V. Since this in the rest or initial position with play the bent spring ends 11 'a, 11' b and the angled support arms 11'c, 11'd of the spreader 11 'faces, no strain of the spreader 11' by means of Reinforced lever V generated. By the drive-side torque M _A put at the same time the upper drive dogs 13a, 13b of the drive member 13 to the mutually away flanks of the bent spring ends 11'a, 11 'b of the spreader 11' at. The small bias of the expanding band 11 'is thus canceled due to contraction of the upper spring ends 11'a, 11'b, so that the boost lever V is rotated together with the driven member 14 in the rotational direction of the driving-side torque.

According to the illustration according to FIG. 4b, a drive-side torque is thus transmitted from the drive ANS to the output ABS with only a slight frictional or sliding moment, which is opposite to an adjusting force F acting on the adjusting element 4.

If the drive-side torque MAN is counteracted by a driven-side torque Mv, the output element 14 is pushed back by the drive element 13 as far as the starting position, so that the entire clutch system 3 can subsequently be moved with low friction. When switching off the drive system 2 - and thus at a termination of the drive-side torque M _A - and at the same time continuing action of a driven-side torque Mv due to a corresponding adjustment force F, the gain lever V tilted slightly and braces the spreader 11 '. Due to the low bias of the expansion band 11 ', the coupling system 3 and thus the adjusting device 1 is blocked, so that the entire holding torque M _H is available.

If the drive-side torque M _A N acts in the direction of a driven-side torque Mv, for example in a clockwise direction, then the stops 14g, 65b of the output element 14 or of the boost lever V - due to its play - slightly move away from the drive pawl 13d of the drive element 13 the lever arm 63b of the reinforcing lever V engages the bent end of the spring 11 'b of the spreading band 11', the opposite bent-off spring end 11b of the spreading band 11 'having little play with the lever arm 63b of the reinforcing lever 4. Touches the drive claw 13a of the drive member 13, the opposite edge of the bent end of the spring 11'a, so the spreader 11 'is slightly contracted. The drive member 13 then moves the disposed within the housing 10 system parts of the coupling system 3 in constant contact of the spreader 11 '. As soon as the drive-side torque M _{A is} reduced, the reduced effect of the drive claw 13a on the bent-over spring end 11 'a of the expansion band 11' causes it and thus the torque exerted by the output element 14 to be blocked again.

In FIGS. 23 to 30, various embodiments of the triggering device G of a clutch system 3 effective as a brake according to FIG. 4b are shown. These embodiments are based on the principle of the coupling between the drive system 2 and the adjusting element 4 of the adjusting device 1 - and thus the coupling of the drive ANS and output ABS - with suppression of a predetermined holding torque M _H , ie with reaching the tripping torque MAUS and after - Run the trip path b to slip through and thereby reduce the generated by the clutch system 3 counterforce. In this case, the torque progression M ₂ according to FIG. 1 is always realized, in which, in order to achieve the most comfortable, easy manual actuation of the adjusting element 4, it is not at all times during the entire process. Adjustment path (areas d and c in Fig. 1), the holding torque M _H must be continuously suppressed.

FIG. 23 shows an embodiment of the triggering device G for torque control, in which two knee or rocker arms 66b, 66c connected to each other via a lever joint 66a are supported on support regions 14h and 14k of the driven element 14 (shown hatched on the right). The lever joint 66a of the lever arrangement 66 is mounted on a radially directed recess 68 of the (left hatched) reinforcing lever V. The lever joint 66a is connected to the adjustment axle 12 via a tension spring 67, so that the rocker arms 66b, 66c generate a pretensioning force between the output element 14 and the reinforcement lever V.

Analogously to the clutch system 3 illustrated in FIGS. 21 and 22, tension forces between the lever arm 63b of the reinforcement lever V and the cranked spring end 11 'occur here as well in a clockwise output-side torque M _v which is less than or equal to a predetermined release torque MAUS. b of the spreading belt 11 'on. Corresponding tension forces also occur between the side flank 63a of the reinforcement lever V and the angled support arm 11 'c of the expansion belt 11'. When reaching or exceeding the predetermined tripping torque M _A US by means of the triggering device G and after passing through the tripping path b within the torque curve M _{2 of} FIG. 1, the output claw 14b of the output element 14 lays against the drive claw 13d of the drive element 13 while reducing the Gegenmomentes due to entrainment of the spreader 11 'on. Thus, the coupling system 3 in the clockwise direction and thus the adjusting element 4 of the adjusting device 1 are moved.

In the embodiment illustrated in FIG. 24, the toggle levers 66b, 66c are supported by the recess 64 of the reinforcement lever V both on the support region 14h, 14k in the recess or recess 14e of the output element 14 and on support regions 64a, 64b. The further construction and the function otherwise corresponds to the embodiment according to FIG. 23. In the embodiment according to FIG. 25, the triggering device G has a tilting element 69 for torque control. This is biased relative to a contact surface of the recess 14e of the output element 14 via a tensioned on the adjustment axis 12 and on a bolt 69a of the tilting element 69 tension spring 67. A pin or bolt diametrically opposite the lever arm 62 of the reinforcing lever V engages in a radially aligned recess 69b of the tilting element 69.

In the coupling system 3 according to FIG. 25, a rotation of the output ABS in a clockwise direction as a result of entrainment of the rocker arm 69 by the support region 14k of the recess 14e of the output element 14 via the bolt 70 leads to a tilting of the tilting element 69 against the biasing force of the tension spring 67 in the counterclockwise direction , In addition to the tilting of the tilting element 69 about the bolt 70, the rotation of the output ABS leads to tilting of the amplification lever V. As a result of a rising output-side torque M _v , the output element 14 is moved further in the clockwise direction. In this case, the tilt angle of the tilting element 69 changes to such a degree that the tripping torque generated by the clutch system 3 M _A US or counter torque according to the torque curve M _{2 of} FIG. 1 falls to a small part of the initial value. To the same extent reduces the tilting of the gain lever V and thus the jamming of the spreading belt 11 '.

From a certain output torque Mv due to a force acting on the adjusting element 4 of the adjusting 1 adjusting force F or from a certain angle of rotation, the output cam 14a of the output element 14, the only slightly strained spreader 11 'on the angled spring arm 11' c against a slight friction or sliding torque MG2. If the output-side torque M _{v is} withdrawn, the tilting element 69 jumps back under the action of the tension spring 67 back into its initial position, so that the entire initial torque of the torque curve M 'between the torque curves M ₂ and M ₃ is available.

26 represents a kinematic reversal to the arrangement according to FIG. 25. The tilting element 69 lies with upper corners on the support regions 64a, 64b of a recess 14e of the lever arm 63b diametrically opposite Reinforcement lever V on. Between the a recess of the rocker arm 69 limiting, radially aligned legs 69c, 69d, a claw 141 of the output element 14 is arranged. Accordingly, the tilting element 69 is also tilted at a driven-side torque M _v , so that with increasing output-side torque Mv due to a change in the angular position of the tilting element 69, the counter-torque is reduced. Thereby, a previous tilting of the reinforcing lever V and thus jamming of the spreader 11 'in the housing 10 is degraded until after a predetermined elastic deflection path b corresponding rotation angle of the output cam 14a or 14b of the output element 14, the angled lever arms 11' c or 11th 'd of the only slightly strained spread belt 11' can turn against a low friction or sliding torque M _G2 .

In the embodiment shown in FIG. 27, the triggering device G for torque control has a latching ball 71 arranged in a radially aligned recess 14m of the drive element 14. This is supported on a locking cam 72 of the gain lever V. The locking cam 72 has a latching surface 72a designed in the manner of a cissoid for the detent ball 71. The detent ball 71 is engaged in the rest or initial position in a groove 72b of the latching surface 72a of the latching cam 72 under the action of a arranged between the detent ball 71 and the bottom of the recess 14m of the output element 14 compression spring 73.

In this embodiment, the driven element 14 has only two output cams 14a and 14b, which are opposite the angled support arms 11'c and 11'd of the spreading belt 11 '. The drive element 13 also contains only two the cranked end of the spring 11 'a and 11'b opposite drive claws 13a and 13b.

If a drive-side torque Mv in one or the other direction of rotation is exerted on the clutch system 3 according to FIG. 27, the detent ball 71 remains in the groove 72b of the detent cam 72 until the predetermined release torque MAUS. When the tripping torque MAU is exceeded _S , the detent ball 71 is moved out of the groove 72b of the latching cam 72 in one direction or the other. The corresponding adjustment is within the trip path b the torque curve M ₂ according to Fig. 1. Here, the tilt of the reinforcement lever V is canceled, eluting with release of the canting of the reinforcement lever to the end of travel V of the release path b out and the jamming of the spread band 11 'is greatly reduced.

For example, in a clockwise acting on the output member 14 torque M _v the output cam 14a presses against the angled support arm 11 'c, so that the only slightly strained spreader 11' can rotate against a low friction or sliding torque MG2. If the adjusting force F is reduced to the adjusting element 4 of the adjusting device 1 and thus the adjusting moment M _v below the tripping torque MAUS of the coupling system 3, the detent ball 71 jumps again into the groove 72b of the latching cam 72. As a result, blocks the slightly biased spreader 11 ', so that the clutch system 3 acts as a brake.

The embodiments shown in FIGS. 28 to 30 contain as triggering device G for torque control arranged in a radially aligned recess 14m of the output member 14 and biased by a compression spring 73 tilting slide 74. This is connected via a rocker arm 74a with a ball or cylinder member 74b, the is stored in a dome 75a of a receiving claw 75 of the gain lever V.

At a driven-side torque My in one or the other direction of rotation of the boost lever V between one of the bent spring ends 11'a, 11'b and one of the angled support arms 11 'c, 11' d of the spreader 11 'due to the lateral swinging out of the tilt slide 74th tilted over the rocker arm 74a. As a result, the spreading band 11 'is jammed against the contact surface 5 of the housing 10. With increasing output-side torque due to an increasing adjusting force F on the adjusting element 4 of the adjusting device 1, the tilting lever 74a of the tilting slide 74 tilts sideways, so that the contact surface of the tilting slide 74 is inclined over the compression spring 73 and thus the triggering moment M _A US along the triggering path b is reduced to a small part of the initial value according to the torque curve M _{2 of} FIG. At the same time, the tilting of the reinforcement lever V and thus the jamming of the expansion band 11 'are reduced. As a result, within the release path b, after a certain angle of rotation, one of the two output cams 14a, 14b of the output element 14 presses against the associated angled support arm 11 'c or 11' d of the wrap spring belt 11 'as well as with the respective other output cam 14b, 14a the associated drive claw 13a or 13b of the drive element 13. Thus, the only slightly strained spreader 11 'against a low friction or sliding torque M _G2 rotate and transfer the output side torque Mv.

If the output-side torque Mv is withdrawn, the rocker springs 74a of the tilt slide 74 back to its original starting position and causes a renewed tilting of the reinforcement lever V. Thus, once the maximum holding torque M _H 'by clamping the Schlingfederbandes 11' with the touch surface 5 of the Housing 10 is provided.

In the embodiment according to FIG. 30, the rocker arm 74a has a ball or cylinder element 74b arranged in the receiving claw 75 of the reinforcing lever V and a return nose 76 opposite the tilting slide 74. By means of this return lug 76, the tilting slide 74 tilted as a result of a driven-side torque M _v can be reset to the initial position by means of the drive claws 13 c, 13 d of the drive element 13 arranged laterally of the triggering device G and the toggle lever 74 a again centered with the tilting slide 74. As a result, according to the function of the embodiment of the clutch system 3 according to FIG. 21, the drive torque MAN, which is made by the drive system 2, can act with a small, opposing frictional or sliding moment M _G2 .

The coupling system 3 according to FIGS. 21 to 30, which acts in the manner of a friction brake (FIG. 4b) or a friction lock, is in turn particularly suitable for an adjusting device 1 for automatically opening and closing a tailgate K hinged to a vehicle body. The coupling system 3 again has a cylindrical shape Housing 10 with a about an adjustment axis 12 rotatable drive member 13 and with an output member 14, between which a frictional engagement element 11 'is arranged. This cooperates with the rotationally symmetrical contact surface 5 of the housing 10. The spreading belt 11 'is with the single turn with a circumferential angle of less than 360 ° with bias to the housing 10 at. The spring ends 11 'a to 11'd of the expansion band 11' interact with the drive element 13 and with the output element 14 on the one hand and with a gain lever V connected or coupled to the output element 14 in such a way that a drive-side torque M _A is substantially frictionless is transmitted to the output element 14 and by means of or via this on the adjusting element 4.

Between two outer, cranked spring ends 11 'a, 11' b of the spreader 11 ', a lever arm 63b of the reinforcing lever V is arranged with play, while between two the cranked spring ends 11'a, 11' b and the adjustment axis 12 arranged radially from the spreader 11th Angled spring ends are effective as support arms 11'c, 11'd. Their end faces are two side edges 63c, 63d of the reinforcing lever V with play opposite, wherein the reinforcing lever V is connected via a slot 63a with the adjustment axis 12. The drive element 13 has a plurality of drive claws 13a to 13d, the stops 65a, 65b of the boosting lever V, output cam 14a, 14b and stops 14f, 14g of the output member 14 and the spring ends 11 'a to 11'd of the spreader 11' in the circumferential direction opposite ,

An output-side torque M _v is blocked up to a predetermined tripping torque MAUS and within a tripping path b. If the output-side torque Mv reaches or exceeds the tripping torque MAUS built up or generated by means of the tripping device G, then, after passing through the tripping path b, the strained spreader belt 11 'is against a low frictional or sliding torque M _G2 in the direction of rotation of the output-side torque M _v rotatable.

In a drive-side torque M _AN , the drive element 13 sets in the circumferential direction of at least one spring end 11 'a to 11'd of the spreader 11', this contracting while canceling the bias and the output element 14 and the gain lever V in the Direction of rotation of the drive-side torque M _A N entrains. At a driven-side torque Mv, which is smaller than the triggering torque MAUS, the output member 14 cams the reinforcing lever V and pushes it radially against a spring end 11'c, 11 'd, resulting in a jamming of the spreader 11' relative to the contact surface 5 of the Housing 10 an adjustment is blocked. At a driven-side torque M _v , which is greater than the release torque M _A US, the canting of the boost lever V and the jamming of the spreader 11 'are reduced, wherein after a triggering path b predetermined rotation angle ω the strained spreader 11' against a slight friction or sliding torque M _G2 is rotatable in the direction of rotation of the output-side torque.

With a drive-side torque M _AN , which is opposite to a driven-side torque M _V , the output element 14 is pressed by the drive element 13 into a neutral middle position and the adjusting device 1 is moved substantially without friction in the direction of rotation of the drive-side torque M _AN . When the drive-side torque M _AN is terminated, the boost lever V is tilted up to the level of the tripping torque MAUS and the adjusting device 1 is blocked.

In a _V directed in the direction of an output-side torque M drive-side torque MAN the amplification lever V sets in the circumferential direction at a spring end 11 'a, 11' b and the driving element 13 pulls the expanding band 11 'slightly together, wherein the moving means 1 in the direction of drive-side torque M _AN with constant contact of the spreader 11 'with the housing 10 is moved, and wherein at the end of the drive-side torque M _AN , the prestressed spreader 11' on the contact surface 5 of the housing or component 10 creates and blocks an adjustment.

The brake system shown in FIGS. 31a and 31b in the manner of a brake device according to FIG. 15 for a brake without drive element which is outside the force flow between drive side ANS and output side ABS has again a cylindrical component or housing 10 in its hollow cylindrical interior a spreading spring or a spreading belt 11 'is used as a frictional engagement element with low pretensioning. The spreader 11 'has outer, cranked spring ends 11'a, 11'b at the end of the spreader 11' and to the Ends of angled support arms 11 'c, 11'd inner spring ends. The housing or ring gear 10 forms the driven element 14 coupled or connected to the adjusting element 4 of the adjusting device 1.

A release lever 77, which is plugged onto the middle or adjustment axis 12 with a slot 77a, is fastened in a rotatable or pivotable manner, just like a spring lever 78, in the lower region of a reinforcement lever V disposed within the expansion band 11 '. The reinforcing lever V has a slot 63b aligned with the slot 77a of the release lever 77. An abutment or lever end 77b of the trigger lever 77 projects between two fixed tabs 79a, 79b.

The reinforcing lever V in turn has a lever arm 63b, which with play between the outer bent spring ends 11 'a, 11'b of the spreader 11' and with side edges 63c, 63d also with play the angled support arms 11'c and 11 'd of the Spreizbandes 11 'faces. On the lever arm 63b opposite the lever end 63g, the amplification lever V has an axis of rotation 80 on which the release lever 77 and the spring lever 78 are held rotatably or pivotably.

Between two of the center or adjustment axis 12 facing fingers or lever arms 78a, 78b of the spring lever 78, a tension spring 67 is mounted. The tension spring 67 surrounds two free-end side two tabs 79c, 79d. A recess 78c of the spring lever 78 opposite the lever arms 78a, 78b surrounds or engages over a further nose 79e fixed to the housing.

The trigger lever 77 projects with its end opposite the end of the system 77b lever end 77c in a recess 81 of the spreader 11 'a. The mutually aligned slots 63a, 67a of the gain lever V and the release lever 77 allow their free lateral mobility within the expansion band 11 '.

Upon rotation of the ring gear 10 and thus of the output element 14 in a clockwise direction as a result of a corresponding output-side adjusting torque M _v , the spreading belt 11 'is taken in the same direction of rotation. As a result, the expansion band 11 'is endeavored with its upper left spring end 11'a and with its middle right end ten arm 11'd take the gain lever V, which thus moves with its lying in the region of the rotation axis 80 lower lever end 63g counterclockwise to the left. At the same time and with the reinforcing lever V, the spring lever 78 is also moved until it hits the lower nose 79e with the right flank 78d of the recess 78c. Again, at the same time, the left lever arm 78a of the spring lever 78 at the left end of the tension spring 67, so that the spring lever 78 can not rotate about the axis of rotation 80 of the gain lever V.

Thus, two forces act on the spring lever 78, namely an (upper) spring force of the tension spring 67 and a (lower) contact force on the nose 79e in the region of the recess 78c. The resulting force presses on the lower rotational axis 80 of the boosting lever V and thus builds up a tightening force with the result that the boosting lever V abuts on the middle right support arm 11'd and the upper left spring end 11'a of the expansion band 11 '. As a result, the expansion band 11 'is tensioned, which results in a blockage of the driven-side ring gear 10.

An increasing output-side adjusting moment M _v on the ring gear 10 leads to an increasing force on the lower nose 79 e, whereby the spring lever 78 wants to rotate about its bearing on the axis of rotation 80 of the booster lever V. This is prevented by the spring force of the tension spring 67, which pulls with respect to the rotation axis 80 upper lever arms 78a, 78b of the spring lever 78 against the two lugs 79c, 79d.

If the defined or predefined triggering moment MAUS of a torque curve M 'lying between those of the torque curves M ₂ and M ₃ according to FIG. 1 is reached as a result of exceeding the preload of the tension spring 67 at the beginning of the path or at the beginning of the triggering path b, the spring lever 78 rotates about the rotation axis 80 in the counterclockwise direction. The spring end of the tension spring 67 assigned to the left lever arm 78a is entrained, while the opposite spring end of the tension spring 67 remains hooked on the right, drive-side or housing-fixed nose 79d (FIG. 31b). The farther the spring lever 78 rotates, the farther the left spring end of the tension spring 67 moves counterclockwise to the left and down. As a result, the tension spring 67 increasingly approaches the pivot point or the axis of rotation 80 of the spring lever 78, while the force application of the engaging in the recess 78c of the spring lever 78 nose 79e on the (right) edge 78d of the spring lever 78 increasingly from the pivot point or from the axis of rotation 80 away. As a result, the torque of the spring lever 78 and thus also the torque of the ring gear 10 within the triggering path b according to the torque curve M _{2 of} FIG. 1 decreases.

As illustrated in Fig. 31b, as a result of the rotation of the ring gear 10 and thus of the output element 14, the trigger lever 77 is driven clockwise in the same direction of rotation together with the boost lever V and the spreader 11 " Within the tripping path b, the tripping torque M _A US has already been reached and the torque curve M _{2 is} generated as a result of the tilting of the spring lever 78 between the vertex b and the path end of the tripping path b (FIG. 1), the abutment end 77b of the tripping lever settles This abutment causes a force on this nose 79b to the left, as a result of which the trigger lever 77 rotates counterclockwise about the axis of rotation 80 on the boost lever V until the lower end of the lever 77c of FIG Reinforcing lever V to the right flank of the recess 81 of the spreader 11 'applies. As a result, a force builds in the fulcrum 80 to lin ks, which counteracts the tensioning force on the gain lever V. This leads to a reduction of the tension of the spreading belt 11 '. At the same time, the support of the lower lever end 63g of the reinforcing lever V causes the spreading belt 11 ', which is now less strained, to slip through along the contact surface 5 of the ring gear 10.

Thus, a double effect is created, on the one hand, by reducing the cause of the jamming or tensioning of the expanding belt 11 'due to the support of the lower lever end 63g of the reinforcement lever V on the spring lever 78 as a result of the applied counterforce of the release lever 77 on the reinforcement lever V, and in which, on the other hand, the slipping effect of the expansion band 11 'along the contact surface 5 is enhanced due to the lower supporting force in the spreading band 11'. Since the distance between the upper lever arm between the contact force and the pivot point 80 is significantly greater than the distance between the two lower forces, a very small additional force is sufficient to release the blocking of the expansion band 11 'and decouple the coupling system 3. This also applies if the current coefficient of friction between the expansion band 11 'and the contact surface 5 of the ring gear 10 is substantially greater than a design friction coefficient at which the clutch system 3 just barely blocked.

Overall, thus results in a torque curve M ₂ , M 'or M _{3 of} FIG. 1 at a force acting on the ring gear 10 and thus on the output member 14 output-side adjusting moment M _v with a force or torque increase within the range a to the plant all Within the subsequent triggering path b, an increase in torque to the apex d may initially take place, on which the tension spring 67 lifts off from the nose 79c or 79d, depending on the direction of rotation of the ring gear 10 or the abrading element 14. Subsequently, within the triggering path b from the vertex d with increasing rotational angle ω, a torque reduction results as a result of the tilting of the spring lever 78. At the end of the triggering path b, a small torque increase due to the friction torque MR ₂ takes place when the tripping lever 77 is applied, whereupon at the end of the trip path b and at the beginning of the region c of the torque curve M ₂ slipping of the spreader 11 'relative to the contact surface 5 of the ring gear 10 takes place. Then, the ring gear 10 and thus the output member 14 can be moved together with the adjusting element 4 and the tailgate ₂ K with constant sliding or slipping moment MQ.

In a reverse rotation of the ring gear 10, the spring lever 78 tilts back into the starting position shown in Fig. 31a, so that the ring gear 10 and the output member 14 can be loaded again in both directions of rotation to the triggering MOUSE corresponding to the torque curve M _{2 of} FIG ,

FIGS. 32a and 32b show a coupling system 3 which is constructed with comparatively few components and functions as a coupling according to FIG. 4a in the initial or in the released state. The hollow cylindrical component or ring gear 10 in turn forms the Ab- A reinforcing lever V is analogous to the embodiment of Figures 31a and 31b between the spring ends 11'a, 11'b and the support arms 11'c, 11'd of a spreader 11 slightly spaced or with play. An arranged on a central or adjustment axis 12 drive element 13 extends in a segment of a circle on the spring ends 11 'a to 11'd opposite side of the adjustment axis 12 within the Schlingfederbandes 11' and turn the output member 14 forming ring gear 10th

The drive element 13 is simultaneously effective as a trigger lever 77 '. The release lever 77 'in turn has a nose or cam 77'c projecting into a recess 81 of the expansion band 11'. Opposing and / or unlatching points 77'd, 77'e of the release lever 77 ', which lie opposite one another, cooperate with lever arms 63e or 63f of the reinforcement lever V and in turn with a tension spring 67 of a release device G together. The tensioned between the lever arms 63e and 63f tension spring 67 braces the gain lever V with the trigger lever 77 'on its control contours forming Verklinkungsstellen 77'd, 77'e. The patch with a slot 63a on the center or adjustment axis 12 gain lever V is in turn free to move laterally.

The principle of the coupling system 3 according to FIG. 31 basically corresponds to that of the coupling system 3 according to FIG. 18, in that instead of a bolt the respective spring end of the spring 67 is guided out of the nose or control contour 77'd and along the control contour 42j of the release lever 77 ' (Fig. 32b).

The coupling system 3 shown in Fig. 33 again operates in the manner of a

Braking device according to FIG. 15 for a brake which is outside the force flow acting as a coupling between the drive side ANS and the driven side ABS (fixed friction brake). In an in turn the output side ABS or an output member 14 of the clutch system 3 forming ring gear 10 is an expansion band or a spreading spring 11 'with little clearance to the contact surface 5 of the ring gear 10 is arranged. The spring ends 11'a and 11'b of the spreader 11 form V-shaped contact surfaces 82a and 82b. Support arms 11'c, 11'd of the expansion band 11 'form lateral supports for a reinforcing lever V, which is connected to its lever end 63b between the freiendseitigen spring ends 11'a and 11'b of the spreader 11 'is guided. The reinforcing lever V is by means of a compression spring 41 without play in the V-shaped spring ends 11 'a, 11'b of the expansion belt 11' out.

A rocker arm 69 is pulled by means of a tension spring 67 under pretension to the gain lever V. Here, the rocker arm 69 via cutting-like bearings 69a, 69b in a recess 83 of the reinforcing lever V on the lever end 63b opposite side and thus decentralized to a bearing contour 84 of the recess 83 of the gain lever V.

A slider 56 fixed to the housing and preferably driven by a motor, in particular an electric motor, surrounds the rocker arm 69 on both sides with slide elements 56c, 56d which can be positioned in three positions P1, P2 and P3 in the longitudinal direction of the rocker arm 69. The clear width of the recess 83 of the reinforcing lever V is dimensioned such that the slide lever 69 receiving between them slide elements or lugs 56c, 56d at least in the position Pi in the recess 83 can be inserted. Two further housing-fixed lugs 79a, 79b are arranged on the contact surfaces 82a, 82b of the spring ends 11'a and 11 'b opposite sides of the spring ends 11'a and 11'b spaced.

For a frictionless relative movement between the spreader belt 11 'and the drive-side ring gear 10, the slider 56 is in the position or position P ₃ in the direction of the contact surface 5 on the freiendseitigen spring ends 11'a, 11'b opposite side of the ring gear 10 against the force of the compression spring 41 moves. Together with the slide 56, the rocker arm 69 and the tension spring 67 as well as the reinforcement lever V are moved toward the freiendseitigen spring ends 11'a, 11'b of the expansion belt 11 'opposite side of the ring gear 10, so that the lever end 63b of the gain lever V from whose position between the two spring ends 11'a, 11'b is pulled out. For this purpose, on the rocker arm 69 at the bearing points 69a, 69b of the reinforcing lever V opposite lever end with the slider elements 56c, 56d cooperating rear handles 85a, and 85b are formed. Due to the slight play between the spreading belt 11 'and the ring gear 10, the output element 14 formed by the ring gear 10 is in the position P _{3 of} the slider 56 practically frictionless rotatable or movable. In this position P _{3 of} the slider 56, the two tabs 79a, 79b fixed to the housing, depending on the direction of rotation, fulfill the task of entraining and reducing the force of the expanding belt 11 within the ring gear 10.

In a movement of the slider 56 in the position P ₁ on the one hand, the reinforcing lever with its lever end 63b frictionally between the two spring ends 11'a, 11 'b of the expansion belt 11 out. On the other hand, in this position Pi of the slider 56, the rocker arm 69 is fixed so that a tilting movement is blocked. Due to the spring force of the compression spring 41 of the boost lever V is pressed via the rocker arm 69 between the spring ends 11 'a, 11'b of the spreader 11', so that this is spread and braced against the contact surface 5 of the ring gear 10.

At an output side adjusting torque M _v , the spreading band 11 'endeavors to move together with the ring gear 10 in the corresponding direction of rotation and to rotate the blocked unit of reinforcing lever V, rocker arm 69 and tension spring 67 with. This is prevented by the housing-fixed slide 56, which bears against the bearing points 69a, 69b opposite lever end of the rocker arm 69. As a result, the reinforcing lever V at the same time depending on the direction of rotation against the spring end 11 'a and the support arm 11' d or against the spring end 11 'b and the support arm 11' c of the expansion belt 11 pressed with the result that due to the frictional engagement between the spreader 11 'and the ring gear 10, a complete blockage of the coupling system 3 takes place. Although the spreading band 11 'strives to rotate due to the force acting on the spring end 11'a or 11'b, depending on the direction of rotation. However, this is due to the relatively large supporting force between the reinforcing lever V and the respective support arm 11'd and 11 ¹ C in conjunction with the Umschlingreibung between the spreader 11 'and the contact surface 5 of the ring gear 10 reliably prevented.

In the middle position or position P _{2 of} the slider 56 are the slide elements 56 c, 56 d with little play on the rocker arm 69 at. In this case, the boost lever V via the rocker arm 69 and the tension spring 67 and the compression spring 41 between the spring ends 11 'a, 11'b and there against the contact surfaces 82a and 82b pressed. An acting on the ring gear 10 and thus on the driven element 14 abtriebsseitiges adjusting torque Mv leads to a movement of the spreader 11 'and the rocker arm 69 with the result that at the beginning of the trip path b according to the torque curve M _{2 of} FIG. 1, the rocker arm 69 depending on the direction of rotation over one or the other bearing 69a, 69b deflects or tilts. Due to the self-locking effect maintained within the triggering path b, which is caused by the further spreading of the expanding belt 11 'maintained by means of the reinforcing lever V, the coupling system 3 still remains in the blocked state.

Since the spring moment of the tension spring 67 of the triggering device G increasingly degrades within the triggering path b due to a movement of the tension spring 67 in the direction of the tilting point, the undercut of the corresponding spring end 11'a and the respective contact surface 82a, 82b moves. 11'b at the end of the trip path b against the respective stationary Gehäusena- se 79a zw. 79b. As a result, in the transition region between the tripping path b and the region c of the torque curve M ₂ according to FIG. 1, the spring ends 11'a, 11'b and thus the spreader belt 11 'are contracted. This, in turn, leads to its slippage along the contact surface 5 of the ring gear 10 due to the now released blocking of the spreader belt 11, so that a comfortable manual adjustment of the adjusting element 4 or of the tailgate K is made possible by generating the corresponding sliding torque M _G2 .

LIST OF REFERENCE NUMBERS

Adjustment device 24,25 magnetic element

Drive system 26 Compression spring

Coupling system 27 guide device

Adjustment element 28,29 compression spring

Contact surface 30 planetary gear

Component / ring gear 31 sun gear

Wrap spring 31a Rotary axis' Spreading band / spring 32-34 Planetary wheel a, b Spring end 32a-34a Rotary axis ¹ Cd Support arm 35 Transmission surface

Adjustment axis 36 inner surface

Drive element 37 housing a, b, c stop 37a bottom surface

Output element 37b, c wall section a, b claw / cam 37c, d stop c, d claw 38 compression spring e recess / recess 38a, b spring end f, g stop 39 lever arrangement h, k support area 39a knee joint j bore 39b, c lever 1 claw 40 cam lever m recess 40a slot

Compression spring 40b cam

Piston assembly 40c Narrow edge

Compression spring 41 Compression spring

Tension spring 42 lever element

Housing 42a slide guide, 22 piston 42b central opening

Driver 42c, d spreading spring a, b driver 42e, f flank 60 torsion spring g nose 60a, b spring arm h cam 61a, b stop j contour 62 housing

Lever element 63a long hole a slide guide 63b lever arm b central opening 63c, d side edge c, d spreading spring 63e, f lever arm e, f flank 63g lever end, 45 tension spring 64 recess, 47 pressure / tension spring 64a, b support area, 49 recess 65a, b stop , 51 recess 66 lever arrangement

Central axis 66a lever joint

Operating levers 66b, c Knee / rocker arms a Contact contour 67 Tension spring b Longitudinal slot 68 Recess c Surface contour / flank 69 Tilting elementAlle d, e Lever end 69a, b Bearing point

Tension spring 70 bolts

Bolt 71 detent ball

Take-off slide 72 Locking cam a recess 72a locking surface b cam 72b groove c, d slide element 73 compression spring

Spring lever 74 Tilting slide a, b U / spring leg 74a Rocker arm

Power lever 74b Ball / cylinder element a, b lever arm 75a dome c, d contact contour 75 receiving claw a, b tilting slide c, d recess e, f nose MR friction torque

76 Reset nose NAB Output claw

77 Release lever NAN Drive claw

77a slot P arrow

77b Investment / lever end Q arrow

77c lever end S push rod

77'd, e Verklinkung T pivot axis

78 Spring lever V Reinforcement lever

78a, b lever arm Z gear

78c recess

79a, b, c, d nose a, c area

79e drive nose b range / switching path

80 axis of rotation

81 recess

82a, b contact surface

83 recess

84 bearing contour

85a, b rear grip

A arrow

ABS output side / output

ANS drive side / drive

B arrow

C arrow

D roof edge area

E arrow

F adjustment force / moment

G force element

H rear area

K tailgate

L spline

M _A tripping torque

MM holding torque

Claims

claims

1. adjusting device (1) for a motor vehicle, having a drive side (ANS) s and an output side (ABS) having coupling system (3) on the drive side with a drive system (2) and the output side with an adjusting element (4, K) coupled,

- Wherein the coupling system (3) has a component (10) with a rotationally symmetrical contact surface (6) and a frictional against this o o closing element (11, 11 ') in the manner of a spreading or wrap spring with spaced spring ends (11 a, 11 b 11 'a, 11'b), and

- Wherein the coupling system (3) having a frictional engagement element (11, 11 ') cooperating triggering device (G), the effect of a from the output side (ABS) to the drive side (ANS) effective Verstellmo- 5 Mentes (M _v ) after Passing through a triggering path (b) and generating a tripping torque (M _A US) triggers a blockage of against the rotationally symmetrical contact surface (5) strained frictional engagement element (11, 11 ').

O

2. Adjusting device according to claim 1, wherein the coupling system (3) is constructed so symmetrical that the frictional engagement element (11, 11 ') from the output side (ABS) to the drive side (ANS) effective adjustment torque (Mv) in each direction both can be clamped as well as released.

5 3. Adjusting device according to claim 1 or 2, wherein the triggering device (G) with the spring ends (11 a, 11 b, 11 'a, 11' b) of the frictional engagement element (11, 11 ') cooperates in such a way that this at the end of the Tripping path (b) in the sense of releasing the blocking is relieved.

0 4. Adjusting device according to claim 3, wherein the coupling system (3) has a reinforcing lever (V), with the spring ends (11 a, 11 b, 11 'a, 11' b) of the frictional engagement element (11, 11 ') interacts that of the Output side (ABS) to the drive side (ANS) towards effective adjusting torque (M _v ) the frictional engagement element (11, 11 ') increasingly braced.

5. Adjusting device according to one of claims 1 to 4, in which the tripping element (MAUS) is adjusted by means of a force generated by the tripping device (G), in particular a spring force or a magnetic force.

6. Adjusting device according to one of claims 1 to 5, wherein the triggering device (G) comprises a prestressed spring element (15, 17, 18, 26, 28, 29, 38; 44, 45; 46, 47; 54, 60, 67; 73).

7. Adjusting device according to one of claims 1 to 6, wherein the triggering device (G) comprises at least one lever element (39; 42,43,53; 57,58; 66,69; 71,72; 74; 77,78).

8. Adjusting device according to one of claims 1 to 7, wherein the inner or outer wall of a hollow cylindrical component (10) forms the contact surface (5).

9. Adjusting device according to claim 8, wherein in self-locking drive system (2), the hollow cylindrical member (10) rotatably supported and as a drive element (13) or as an output element (14) is effective.

10. Adjusting device according to claim 8, wherein in non-self-locking drive system (2), the hollow cylindrical member (10) rotatably held.

11. Adjusting device according to one of claims 1 to 10, wherein the coupling system (3) in the hollow cylindrical member (10) comprises an adjusting axis (12) rotatable drive element (13) and an output member (14), wherein the angled spring ends (11a , 11 b) of the frictional engagement element (11) resting against the contact surface (5) of the component (10) interact with the drive element (13) and with the driven element (14) in such a way that the coupling system (3) controls the drive-side drive torque (MAN ) with ringing of the effective diameter of the frictional engagement element (11) transmits substantially frictionless to the output element (14).

12. Adjusting device according to claims 11, wherein the triggering device (G) of the coupling system (3) between the output element (14) and the angled spring ends (11 a, 11 b) of the frictional engagement element (11) is arranged and on the one hand, a driven-side adjusting moment ( M _v ), which is smaller than the release torque (MAU _S ), receives and / or blocks and on the other hand upon reaching the triggering torque (MAUS) a power transmission from the output member o (14) on the angled spring ends (11 a, 11 b) to reduce the effective diameter of the frictional engagement element (11) releases.

13. Adjusting device according to claim 11 or 12, wherein the coupling system (3) the output side adjusting torque (M _v ) to the predetermined tripping torque 5 (MAUS) by clamping the frictional engagement element (11) with the component (10) blocked.

14. Adjusting device according to one of claims 11 to 13, wherein the drive element (13) the drive-side drive torque (M _A N) both on the ab- 0 angled spring ends (11 a, 11 b) in the sense of reducing the effective

Diameter of the frictional engagement element (11) and, in particular via the triggering device (G), transmits to the output element (14).

15. Adjusting device according to one of claims 1 to 14, wherein at a drive side adjusting torque (M _v ) within the triggering path (b) an elastic deformation of the triggering device (G).

16. Adjusting device according to one of claims 1 to 15, with a in different control positions (Pi, P ₂ , P ₃ ,) adjustable control element (56), 0 - wherein in a first control position (Pi) the coupling system (3) is locked,

- In a second control position (P ₂ ), the coupling system (3) for generating the release torque (MOUSE) is effective, and / or - Wherein in a third control position (P ₃ ), the coupling system (3) is dissolved.

17. Adjusting device according to claim 16, with a motor, in particular electromotive, driven, preferably slide-like, control (56).