DE102020113220B4 - Hinge actuator for a torque clutch - Google Patents

Abstract

Hinge actuator (1) for a torque clutch (2), having at least the following components: - at least one actuating finger (3,4) for transmitting an actuation path (5) to a torque clutch (2); - a lever (6) with a main extension ( 7) which is connected to the actuating finger (3,4);- a hinge bearing (8) for pivotally supporting the lever (6); and- a traverse (13) in force-transmitting contact with the lever (6), wherein the traverse (13) can be moved along the main extension (7) between a disengaged position (14) and an engaged position (15) and wherein by means of the method of - the lever (6) together with the actuating finger (3,4) is the only spring element that determines the rigidity of the lever (6), characterized in that that the hinge bearing (8) has two bolts (9,10) with a bolt axis (20) and a corresponding bolt receptacle (18,19) each, the bolt receptacle (18,19) each being supported by a bearing bracket (21,22) of the lever (6) is formed, wherein the bearing bracket (21,22) extends along the main extension (7) away from the actuating finger (3,4).

Description

The invention relates to a hinge actuator for a torque clutch, a torque clutch with such a hinge actuator, a drive train with such a torque clutch, and a motor vehicle with such a drive train.

Hinge actuators for actuating a torque clutch, for example a friction clutch for a drive train, for example for a motor vehicle, are known from the prior art. For example in the DE 10 2012 220 436 A1 such a hinge actuator is shown. An alternative embodiment of a hinge actuator is also from DE 10 2012 207 816 A1 known. The problem often arises that the installation space available for a hinge actuator, in particular transversely to the main extension of the lever of the hinge actuator, is extremely limited. However, at the same time the cost pressure is high, especially in the automotive industry, both in terms of unit costs and assembly costs.

Proceeding from this, the object of the present invention is to at least partially overcome the disadvantages known from the prior art. The features according to the invention result from the independent claims, for which advantageous configurations are shown in the dependent claims. The features of the claims can be combined in any technically meaningful way, whereby the explanations from the following description and features from the figures can also be used for this purpose, which include additional configurations of the invention.

• - zumindest einen Betätigungsfinger zum Übertragen eines Betätigungswegs auf eine Drehmomentkupplung;
• - einen Hebel mit einer Haupterstreckung, welcher mit dem Betätigungsfinger verbunden ist;
• - ein Scharnierlager zum verschwenkbaren Lagern des Hebels; und
• - eine Traverse in kraftübertragendem Kontakt mit dem Hebel, wobei die Traverse entlang der Haupterstreckung zwischen einer ausgerückten Position und einer eingerückten Position verfahrbar ist und wobei mittels Verfahren der Traverse der Hebel zum Übertragen des Betätigungswegs verschwenkbar ist.

The invention relates to a hinge actuator for a torque clutch, having at least the following components:

• - At least one actuating finger for transmitting an actuating travel to a torque clutch;
• - a lever with a main extension, which is connected to the actuating finger;
• - A hinge bearing for pivotally supporting the lever; and
• - A traverse in force-transmitting contact with the lever, wherein the traverse can be moved along the main extent between a disengaged position and an engaged position and by means of moving the traverse the lever can be pivoted to transmit the actuating travel.

The hinge actuator also has the feature that the lever together with the actuating finger is the only spring element that determines the rigidity of the lever.

Unless explicitly stated otherwise, ordinal numbers used in the description above and below only serve to clearly distinguish them and do not reflect any order or ranking of the components referred to. An ordinal number greater than one does not mean that another such component must necessarily be present.

Furthermore, the spatially descriptive terms left and right are chosen arbitrarily and can also be used (uniformly) interchangeably. They only serve to provide a good overview, especially with regard to a paired arrangement of components.

In the following, reference is made to the operating axis (for example the axis of rotation of a torque coupling transmitting torque about this axis of rotation) of the hinge actuator if the axial direction, radial direction or direction of rotation and corresponding terms are used without any explicit indication to the contrary. Furthermore, the hinge actuator is referred to as the main extent of the lever, the lever being pivotable about a pivot axis of the hinge bearing, which is aligned transversely (ideally 90°) to the main extent. This pivot axis may be displaceable during the pivoting movement of the lever and/or not in the center of a bearing component, for example not congruent with the central axis of a bolt. The third spatial direction can approximately be understood as the orientation of the actuating path, with the actuating path being aligned transversely (ideally 90°) to the pivot axis and during a pivoting movement of the lever by the pivoting angle corresponding to the actuating path, varying transversely to the main extent. The lever rigidity results from the bending of the lever to the main extent with deflection in the direction of the actuation path, the effective length of the lever changing with actuation by means of the traverse, specifically shortening as the actuation path increases. That is, with the crossbar in the engaged position, the effective length of the lever is maximum and with the crossbar in the disengaged position, the effective length of the lever is minimum. This is explained in more detail below. In addition to its main extension, the lever has a structural extension (parallel to the pivot axis) between a left side and a right side. To this building The actuation path is arranged across the surface. Lateral movement of the lever, i.e. to the left or right, is prevented (possibly with play).

The hinge actuator proposed here is set up, for example, for an axially actuable torque clutch, for example an axially compressible friction clutch. Alternatively, the hinge actuator is generally set up for the transmission of axial forces, preferably with a central shaft rotating about its axis of rotation. The hinge actuator comprises at least one, preferably two, actuating fingers, with two actuating fingers (for example used in a torque clutch) acting on an actuating bearing on the left and right of a rotating shaft, for example a transmission input shaft. The actuating finger is designed to transmit an actuating travel, for example to a torque clutch. The actuating finger is connected to a lever, preferably formed in one piece, with the actuating finger being arranged as an extension of the main extension of the lever. In a simplified model, this main extent corresponds to the lever, with the real component of the lever, for example as a sheet metal component, not necessarily having a symmetry with the main extent and also not necessarily having its greatest direction of extent in the direction of (a central axis in) this main extent. The main extent and the pivot axis span a plane and the actuating surface of the actuating finger lies in this plane. A central axis runs in this plane of the main extent, which in the case of two actuating fingers runs centrally between the actuating fingers and intersects the pivot axis, preferably perpendicularly. For many applications, it is advantageous to design the lever in a cost-effective and space-saving manner, so that a lever as a sheet metal component with stiffening ribs and/or beads is particularly advantageous in this respect. Especially with such an embodiment made of sheet metal, the theoretical plane of the main extension does not run completely through the real component of the lever.

The lever is mounted pivotably about the pivot axis by means of a hinge bearing, so that pivoting the lever (about the pivot axis) to perform an actuation path using the at least one actuating finger describes the basic function of the lever. Furthermore, a traverse is provided with this hinge actuator. The traverse is in force-transmitting contact with the lever in such a way that the lever is pivoted about the pivot axis by moving the traverse along the main extension. The traverse, which is preferably formed by a single or a plurality of, preferably two, support rollers for low-friction force transmission to the lever, can be moved between a disengaged position and an engaged position. Together with the lever, the traverse forms a ramp-like actuation mechanism. For example, the actuation mechanism is formed with a lever ramp on the crossbar (on the back of the lever) and a bearing track on the side opposite the crossbar (for example on a base plate). The slope of the lever ramp and/or the bearing track can be implemented as desired for individual requirements. For a linearly driven traverse (for example by means of a spindle drive with the spindle axis as the linear movement axis), it is advantageous to design the bearing track to be flat.

It should be pointed out at this point that the hinge actuator is actuated via the traverse (as described above), with a rotary electric drive machine being connected to a spindle drive, for example, which causes the relative movement of the ramp-like actuation mechanism of the traverse and, by means of the ramp-like connection with the Lever forces the movement of at least one actuating finger along the actuating path. In a preferred embodiment (due to the installation situation), the actuation force on the actuation finger over the entire actuation path resulting from the movement of the traverse between the engaged position and the disengaged position is (almost) constant.

In the engaged position of the traverse, the lever delivers no or a minimal actuation stroke (e.g. for a minimum required axial preload) and in the disengaged position of the traverse, a maximum actuation stroke via the actuating finger. It should be noted that the main extension is moved with the lever and thus, from the point of view of a coordinate system moved with the lever, the traverse describes a circular or arcuate path, for example with a constant gradient of the lever ramp. Nevertheless, the traverse particularly preferably moves along a rigid spindle axis, the spindle axis being fixed to a fixed component, for example a base plate of the hinge actuator.

As already mentioned above, the traverse is driven, for example, by a spindle drive with a spindle axis, for example a ball screw drive, in which case the traverse itself is designed as a carriage which includes a driven (axially movable) spindle nut or a driven (axially movable) spindle and the driving (rotating) spindle or driving (rotating) spindle nut is driven by a rotary, preferably electric, drive machine driven. The spindle axis is therefore aligned transversely, preferably 90°, to the pivot axis and at a relative ramp angle to the main extension of the lever.

It is now proposed here that no additional spring element is formed, which determines the lever rigidity of the lever. The lever stiffness of the lever is the determining variable of the effective stiffness of the hinge actuator during actuation. In contrast, other rigidities, such as in the hinge bearing or a connection point between separate components, are much lower, preferably negligible. Rather, the lever or the effective length of the lever in accordance with the position of the traverse itself forms the component which determines the lever rigidity, simplified in the manner of a bending beam, for example a cantilever beam. In a preferred embodiment, the at least one actuating finger is part of the bending beam, ie it contributes to the rigidity of the lever. In another embodiment, the lever apart from the at least one actuating finger (taking into account the applied loads) is almost ideally stiff, ie its bending deformation is negligible, and the lever stiffness is determined solely by the at least one actuating finger. In yet another embodiment, the at least one actuating finger (taking into account the loads applied) is almost ideally stiff. In an embodiment with the lever (or at least portions of the lever) as the spring element, the (bearing-side) portion of the lever between the hinge bearing and the traverse is only negligibly deformed and only the (finger-side) portion of the lever between the traverse and the actuating finger (more precisely between the traverse and the actuating surface of the actuating finger) forms the spring element, i.e. in the manner of a cantilever beam. In another embodiment, the (bearing-side) portion of the lever between the traverse and the hinge bearing participates in the lever stiffness, so that the spring element corresponds to a 3-point supported bending beam, with the hinge bearing and the actuating surface of the actuating finger being the two in analogy to a three-point bending test Support and the traverse corresponds to the test stamp.

If there are two actuating fingers, the lever may be twisted (about the main extension) due to tolerances, for example as a result of a difference of up to 0.2 mm [two tenths of a millimeter] in the direction of the actuating path between the actuating fingers in a (completely) relaxed position and/ or the engaged position (minimum actuation stroke). A first actuating finger is then initially alone or (compared to the second actuating finger) more strongly in force-transmitting engagement during the execution of an actuating stroke along the actuating path, and the second actuating finger then follows.

As a result of the omission of a separate (additional) spring element, not only can the costs be reduced, but installation space can also be saved.

It is also proposed in an advantageous embodiment of the hinge actuator that it has two actuating fingers with a finger spacing transverse to the main extension of the lever and that the hinge actuator has a maximum transverse dimension parallel to the finger spacing, the maximum transverse dimension being less than 4 times, preferably less than 2.5 times the finger spacing.

In this embodiment, the width of the hinge actuator is significantly reduced in comparison to previously known embodiments. The finger spacing, ie the transverse dimension of the free space created between two actuating fingers, is determined, for example, by the dimensions of the component to be actuated with axial forces, for example the shaft diameter in an actuating bearing of a torque clutch, and/or the required actuating forces. The maximum transverse dimension of the hinge actuator is the maximum extent between the left and right side and/or the extent at which a conventional hinge actuator has its maximum extent between the left and right side, which was thus previously determining the installation space. At a ratio of just less than 4 times [four times], the lever can be made stiffer or with a thinner sheet metal thickness and therefore cheaper to manufacture. With a ratio of less than 2.5 times, considerable installation space can be saved. In a particularly preferred embodiment, the ratio is approximately 2.2 times the finger spacing. The maximum transverse dimension is then formed at the hinge bearing. The component that determines the installation space is then, for example, a fastening element for mounting the hinge actuator, for example in a transmission of a motor vehicle.

In a first embodiment of the hinge actuator according to the invention, it is proposed that the hinge bearing has two bolts with a bolt axis and a corresponding bolt receptacle in each case, with the bolt receptacles each being formed in a bearing section of the lever that is angled to the main extension and to the bolt axis, preferably by 90° is,
preferably in the disengaged position the lever stiffness of the lever is between 4 kN/mm and 5 kN/mm.

In this embodiment, a bolt receiver is formed in an angled bearing portion of the lever, for example in a (preferably cold) formed tab. The angled bearing section is preferably arranged laterally on the outside of the lever. The respective bolt extends through a corresponding bolt receptacle. The bolt is in turn accommodated in a corresponding bearing mount and can be mounted directly or indirectly by means of the bearing mount (together with the entire hinge actuator). In one embodiment, the bolts are rotationally fixed. In one embodiment, the bolts are mounted in such a way that they also rotate when the lever pivots. In one embodiment, co-movement of the bolts is permitted, but not required. In a preferred embodiment, the pin axis (which is then congruent for both pins) corresponds to the pivot axis of the lever. In one embodiment, the pivot axis is aligned parallel to the bolt axes (which are then congruent or parallel to both bolts). In yet another embodiment, the pivot axis is oriented at an angle to at least one of the bolt axes. The position of the pivot axis is determined by the shape of the pairing of the bolt receptacles and the (bearing-effective) outer surface of the bolts, so that, for example, in a concentric embodiment of this pairing, the pivot axis is congruent with the bolt axis. If any of the shapes of this mating deviates from concentricity and/or the pin axes of the two pins are not congruent, the pivot axis will deviate from the pin axis. For example, the pivot axis is then not fixed via the pivoting movement of the lever, but moves. In a preferred embodiment, such a wandering movement of the pivot axis is within an allowable tolerance and can be described approximately, ie as from a technical point of view, as fixed.

In a preferred embodiment, a relatively high level of lever rigidity is achieved, preferably as a result of a stiffening effect by means of deformed tabs with the bolt receptacle. In a particularly preferred embodiment, in the disengaged position of the traverse, i.e. with a shortened effective length of the lever or with a shortened finger-side portion of the lever, the lever stiffness of the lever, i.e. (at least approximately) the actuating stiffness of the hinge actuator, is between 4 kN/mm [four kilonewtons per millimeter] and 5 kN/mm, for example at about 4.5 kN/mm. This allows customer requirements for a relatively high lever stiffness to be met.

In a second, alternative embodiment of the hinge actuator according to the invention, it is proposed that the hinge bearing has two bolts with a bolt axis and a corresponding bolt receptacle in each case, with the bolt receptacle being formed by a bearing bracket of the lever, with the bearing bracket extending along the main extension away from the actuating finger extends,
preferably in the disengaged position the lever stiffness of the lever is between 1 kN/mm and 2 kN/mm.

In this embodiment, the same applies to the bolts and their bearing mounts, as well as to the resulting pivot axis, as to the previously mentioned embodiment of the hinge bearing, which deviates from this. In contrast to the embodiment with the angled bearing sections, here the bolt receptacles are formed by bearing brackets, which extend as an extension of the lever up to the hinge bearing. In one embodiment, the bearing brackets can be inserted into the hinge bearing, for example approximately in the direction of the main extension and/or approximately in the direction of the spindle axis of the crossbar, in such a way that the bolt receptacle of the respective bearing bracket is located behind (i.e. in relation to the actuation path resulting from the movement of the crossbar from the engaged position toward the disengaged position) is arranged on the respective bolt, with the bolts preferably already being mounted. The lever is secured against automatic dismantling by means of the shape of at least one of the bolt receptacles and/or the assembly alignment that deviates from an operating situation (ie the alignment of the lever between the engaged position and the disengaged position).

The bearing tabs are preferably configured in such a way that the lever stiffness of the lever is reduced compared to the embodiment with the angled bearing sections. In a particularly preferred embodiment, in the disengaged position of the traverse, i.e. with a shortened effective length of the lever or with a shortened finger-side portion of the lever, the lever rigidity of the lever, i.e. (at least approximately) the actuation-effective rigidity of the hinge actuator, is between 1 kN/mm [ one kilonewton per millimeter] and 2 kN/mm, for example at about 1.7 kN/mm. This allows customer requirements for a relatively low lever stiffness to be met.

In an advantageous embodiment of the hinge actuator, it is also proposed that the bearing brackets run in an arc, preferably S-shape, between the rest of the lever and the bolt in relation to a cross section normal to the bolt axis.

In this embodiment of the hinge actuator, the bearing lugs already described above are formed in a curved manner by the lever, which is more flat in the region of the travel path of the traverse, specifically towards or away from the traverse. The cross-section thus lies in a plane to which the bolt axis (in an ideal view) is aligned normal. This cross section describes an arc shape, preferably an S shape, between the rest of the lever and the hinge bearing. This creates a soft connection of the lever to the hinge bearing due to an extension of the bearing brackets compared to a straight or shortest connection. Alternatively or additionally, space in the direction of the actuation path can be saved on the back of the lever by the hinge bearing being arranged deeper in the direction of the actuation path, i.e. closer to the traverse, with an arc shape of the bearing brackets towards the traverse. In many applications, this installation space corresponds to the axial installation space in an application with a shaft that transmits torque about an axis of rotation.

It is also proposed in an advantageous embodiment of the hinge actuator that the lever is secured laterally by means of the hinge bearing, preferably by means of at least one of the bolts according to an embodiment according to the above description.

In this embodiment, the lever is secured laterally, ie to the left and right, by means of the hinge bearing without additional components. For example, a lateral stop is formed to the right and/or to the left, for example by means of a shoulder of a bearing element and/or by means of a wall of a bearing mount. In a preferred embodiment, the lateral securing is formed by means of at least one of the bolts according to one of the above embodiments, preferably by means of both bolts. For this purpose, the bolt has, for example, at least one shoulder (diameter increase), preferably two shoulders, with this shoulder preferably being in force-transmitting contact (eg with play) both with the respective bolt receptacle and with the respective bearing receptacle. In another embodiment, at least one of the bolts is secured by means of a screw, preferably a mounting screw, with the screw extending through or into a corresponding groove or bore of the relevant bolt. Lateral securing on both sides is particularly advantageous in the case of a soft embodiment of the lever, in particular one that is torsionally flexible (around the main extent). With the embodiments proposed here, a simple construction and/or a small installation space requirement can be achieved. It should be noted that the lever is preferably only elastically torsionable under the design loads.

It is also proposed in an advantageous embodiment of the hinge actuator that the lever comprises two partial levers which are connected to one another in one piece by means of at least one lever bridge.

In this embodiment, the lever is divided into two partial levers, for example each assigned to one of two actuating fingers. By providing two partial levers, which are connected to one another solely by means of at least one lever bridge, preferably in one piece, a particularly low torsional rigidity (around the main extent) is created. This allows a large tolerance with regard to the actuating surface of at least one actuating finger, because an angular deviation or an offset of two actuating fingers in relation to the mating surface to be actuated, for example an actuating bearing of a torque clutch, can be compensated for with little resistance. Such a (low) resistance is determined, for example, by (low) lateral forces in the hinge bearing and/or a (low) difference in force on the two separate operating surfaces of the two operating fingers and/or on the traverse, which preferably (left and right) comprises two support rollers . In an embodiment with angled bearing sections, a single lever bridge is preferably provided, which is arranged at a large distance (compared to the embodiment described below) from the at least one actuating finger, so that the actuating finger achieves a sufficiently low torsional rigidity while at the same time having a relatively large one Lever stiffness (due to the angled bearing sections). In an embodiment with bearing brackets, two lever bridges are preferably provided, of which one (first) lever bridge (in comparison to the aforementioned embodiment with a single lever bridge) is arranged close to the at least one actuating finger and the other (second) lever bridge close to the Hinge bearing is arranged so that in the actuating finger and in the hinge bearing not too low torsional stiffness is achieved despite a relatively low lever stiffness (due to the bearing brackets).

• - einen Scharnieraktor nach einer Ausführungsform gemäß der obigen Beschreibung;
• - ein Drehmomentpaket, bevorzugt ein axial verpressbares Reibpaket, welches zum regelbaren Übertragen eines Drehmoments mittels des Scharnieraktors axial betätigbar ist; und
• - ein Betätigungslager zwischen dem Drehmomentpaket und dem Betätigungsfinger des Scharnieraktors,

wobei mittels der Traverse des Scharnieraktors der Betätigungsweg über das Betätigungslager auf das Drehmomentpaket übertragbar ist.According to a further aspect, a torque coupling with an axis of rotation for a drive train is proposed, having at least the following components:

• - a hinge actuator according to an embodiment as described above;
• - A torque package, preferably an axially compressible friction package, which can be regulated Transmission of a torque by means of the hinge actuator can be actuated axially; and
• - an actuation bearing between the torque pack and the actuation finger of the hinge actuator,

wherein the actuation path can be transmitted to the torque pack via the actuation bearing by means of the cross member of the hinge actuator.

The torque clutch proposed here is, for example, a friction clutch or a form-fitting clutch, such as a claw clutch or what is known as a wedge clutch. A torque about the axis of rotation can be transmitted in a separable manner by means of the torque coupling. The torque clutch represents a switching element for transmitting or for separating a torque-transmitting connection, with this task being performed by a torque pack. The torque package can be actuated axially by means of the hinge actuator, designed as a friction package, for example, so that it can be pressed axially, in which case the actuating force exerted by the hinge actuator or the actual actuating stroke resulting from the set position between the disengaged position and the engaged position of the crossbar, optionally translated via a lever spring, is proportional to the desired transmittable maximum torque. The hinge actuator is arranged in such a way that it or its pivot axis (ignoring spring stiffness and any wandering movement of the pivot axis that may be desired during actuation) is fixed, for example by means of assembly screws on a fixed component, and the shaft connected by means of the torque coupling, for example a transmission input shaft (at an embodiment with two actuating fingers) runs between the actuating fingers. The at least one actuating finger acts, preferably via an actuating bearing, on a rotating axial bearing ring and the rotating axial bearing ring directs the actuating force from a rotating axial bearing ring to the torque pack. With the help of the actuation bearing, the actuation finger and thus the hinge actuator are torque-free. In the engaged position of the traverse, no actuation travel or only a minimal actuation travel (e.g. for a desired minimum preload) is exerted on the actuation bearing, and in the disengaged position of the traverse a maximum actuation travel (e.g. for maximum compression of a friction pack) is exerted on the actuation bearing .

For the (controllably) separable transferability of a torque, the torque clutch has an axially actuatable torque assembly, for example an axially compressible friction assembly. The controllability of a transferability of a torque also includes shifting, i.e. disconnecting and (complete) connecting, as in the case of a dog clutch, as well as a stepless (or, for example, incremental due to the control) control of the maximum transferrable torque amount in the case of a friction clutch, for example for smoothing out excess torque. In the case of a friction pack, at least two friction plates and at least one clutch disk are usually provided. In a simple embodiment, a single clutch disc is provided between a first friction plate, an axially movable pressure plate, and a second friction plate, preferably an axially fixed counterplate, and can be pressed therebetween for frictional torque transmission by means of a pressure force. This contact pressure is generated or (servo-)assisted by the hinge actuator, with the actuation force that is emitted often being converted into the contact pressure by means of a lever spring. As a result of the contact pressure, there is a frictional force over the surface friction pairings between the area of the clutch disc intended for frictional engagement and a (respective) corresponding counter-friction area of the respective friction plate, which, multiplied by the mean radius of the friction surface formed, results in a transmittable torque. Multiplied by the number of friction pairings, this results in the transferable (maximum) total torque of the friction clutch. In the uncompressed state of the friction pack, no torque or only a permissible low drag torque can be transmitted. The friction clutch is designed, for example, as a double clutch with two friction packs, with the respective counter-plate preferably being formed by a common central plate. It should be pointed out at this point that the hinge actuator is actuated via the traverse, with a rotary electric drive machine being connected to a spindle drive, for example, which linearly moves the carriage-like traverse and, by means of the ramp-like connection with the lever, along the movement of the at least one actuating finger of the actuation path. In a preferred embodiment, the actuation force on the actuation finger is (almost) constant over the entire actuation path resulting from the movement of the traverse between the engaged position and the disengaged position.

The hinge actuator proposed here can be installed in a particularly small amount of space and with little stress, the hinge actuator being designed to be less complex and easy to assemble. In the case of a double clutch, for example, two (e.g the axis of rotation twisted) of the hinge actuator proposed here is provided.

According to a further aspect, a drive train is proposed, having at least one drive machine with a machine shaft, at least one consumer and a torque clutch according to an embodiment according to the above description,
wherein the machine shaft is connected to the at least one consumer in a torque-transmitting manner in a controllable manner by means of the torque coupling.

The drive train proposed here includes a torque clutch, for example a friction clutch, in one embodiment according to the above description, the torque clutch transmitting torque from the prime mover or its machine shaft to at least one consumer, for example the drive wheels in a motor vehicle, by means of a hinge actuator according to a Embodiment according to the above description given actuating force or contact pressure on the torque pack, such as a friction pack, switchable, so detachable, accomplished. This by no means excludes reverse torque transmission from the consumer to the machine shaft, in a motor vehicle, for example, to use the engine brake to decelerate the motor vehicle and/or to recuperate braking energy. The drive machine is, for example, an internal combustion engine and/or an electric drive machine. In one embodiment, the input side of the torque clutch is connected to the machine shaft in a torque-proof manner and the output side is connected (at least indirectly, for example via a gear) in a torque-proof manner to the at least one consumer.

The torque coupling proposed here is particularly advantageous for a drive train in which the available installation space for a hinge actuator is small and preferably a high tolerance for the at least one actuating finger is necessary or desirable for cost reasons. This tolerance can be compensated for without high resistance by means of a low torsional rigidity in the hinge actuator proposed here.

According to a further aspect, a motor vehicle is proposed, having at least one driving wheel, which can be driven by means of the drive train according to an embodiment according to the above description.

The installation space is particularly small in motor vehicles due to the increasing number of components and it is therefore particularly advantageous to use a drive train of small size. With the desired so-called downsizing of the drive machine with a simultaneous reduction in the operating speeds, the intensity of the disturbing torsional vibrations and also with increasing torques or a reduction in the torque clutch the demand on the actuating forces is increased. A similar problem arises with so-called hybridization, in which an electric drive machine is used more and more frequently or even forms the main source of torque and the smallest possible internal combustion engine is to be used, which, however, has to be switched on and off the drive train more frequently. It is therefore a challenge to use a hinge actuator to provide sufficient actuating force with low parts costs and little available installation space.

This problem is exacerbated in the case of passenger cars in the small car class according to the European classification. The aggregates used in a passenger car in the small car class are not significantly smaller than in passenger cars in larger car classes. Nevertheless, the space available in small cars is much smaller. The drive train proposed here is particularly advantageous for a motor vehicle in which the available installation space for a hinge actuator is small and preferably a high tolerance for the at least one actuating finger is necessary or desirable for cost reasons. This tolerance can be compensated for without high resistance by means of a low torsional rigidity in the hinge actuator proposed here.

Passenger cars are assigned to a vehicle class according to, for example, size, price, weight and performance, with this definition being subject to constant change according to market needs. In the US market, vehicles in the small and micro car classes are assigned to the subcompact car class according to European classification, and in the British market they correspond to the supermini or city car class. Examples of the subcompact class are a Volkswagen up! or a Renault Twingo. Examples of the small car class are an Alfa Romeo MiTo, Volkswagen Polo, Ford Ka+ or Renault Clio. Well-known hybrid vehicles are the BMW 330e or the Toyota Yaris Hybrid. An Audi A6 50 TFSI e or a BMW X2 xDrive25e, for example, are known as mild hybrids.

• 1: ein Scharnieraktor mit gewinkelten Lagerabschnitten in perspektivischer Ansicht;
• 2: der Scharnieraktor gemäß 1 in Seitenansicht;
• 3: der Scharnieraktor gemäß 1 in einer perspektivischen Schnittansicht;
• 4: ein Scharnieraktor mit Lagerlaschen in perspektivischer Ansicht;
• 5: der Scharnieraktor gemäß 4 in Seitenansicht;
• 6: der Scharnieraktor gemäß 4 in geschnittener Hinteransicht;
• 7: der Scharnieraktor gemäß 4 in einer perspektivischen Schnittansicht; und
• 8: ein Antriebsstrang mit einem Scharnieraktor in einem Kraftfahrzeug.

The above-described invention is described below before the relevant technical background reason explained in detail with reference to the accompanying drawings, which show preferred embodiments. The invention is in no way restricted by the purely schematic drawings, it being noted that the drawings are not true to scale and are not suitable for defining size relationships. It is presented in

• 1 : a hinge actuator with angled bearing sections in a perspective view;
• 2 : the hinge actuator according to 1 in side view;
• 3 : the hinge actuator according to 1 in a perspective sectional view;
• 4 : a hinge actuator with bearing brackets in a perspective view;
• 5 : the hinge actuator according to 4 in side view;
• 6 : the hinge actuator according to 4 in sectional rear view;
• 7 : the hinge actuator according to 4 in a perspective sectional view; and
• 8th : a drive train with a hinge actuator in a motor vehicle.

In 1 a hinge actuator 1 is shown in a perspective view. Here, the hinge actuator 1 (optionally) has a base plate 38 on which the lever 6 has a main extension 7 (cf 2 ) is mounted so that it can pivot about a pivot axis 39 defined by a hinge bearing 8 (optionally preassembled as a structural unit), here (optionally) by means of a left-hand mounting screw 23 (as shown) and a right-hand mounting screw 24 (as shown). The main extension 7 is between the pivot axis 39 and the actuating surfaces 40,41 of the actuating fingers 3,4 are defined (cf 2 ). Left and right refers here and in the following only to the representation perspective of the 1 . The hinge actuator 1 has a maximum transverse dimension 42 transversely to the main extent 7 , which is defined as the maximum extent between the left and right side of the base plate 38 at the hinge bearing 8 . The linear movement of the traverse 13 (or the support roller 43) is introduced into the lever 6 and thus causes the lever 6 (or the main extension 7) to pivot about the pivot axis 39. In the (shown) engaged position 15 of the traverse 13, the lever 6 provides no or a minimal actuating stroke (e.g. for a minimum required axial preload) and in the (not shown) disengaged position 14 a maximum actuating stroke over the (here two) with the Lever 6 connected and arranged in extension of the main extension 7 of the lever 6 actuating fingers 3.4. The left actuating finger 3 and the right actuating finger 4 are spaced apart from one another by a finger spacing 44 (dimension of the free space between the actuating fingers 3.4, for example for a shaft). In the embodiment shown here, the lever 6 comprises two partial levers 25,26. The left actuating finger 3 is formed with the left partial lever 25 and the right actuating finger 4 with a right partial lever 26 in a one-piece extension along the main extent 7 . The partial levers 25, 26 are connected to one another in one piece by means of a lever bridge 27 (single here). This (single) lever bridge 27 is equipped with a (compared to the embodiment described below according to 4 until 7 ) Arranged in the direction of the main extension 7 at a large distance from the actuating fingers 3.4, so that the actuating fingers 3.4 have a sufficiently low torsional rigidity while at the same time having a relatively high lever rigidity (due to the angled bearing sections 66,67). On the lever side, the hinge bearing 8 comprises an angled left bearing section 66 with a left bolt receptacle 18, in which a left bolt 9 is accommodated on the lever side, and an angled right bearing section 67 with a right bolt receptacle 19, in which a right bolt 10 is accommodated on the lever side. On the fastening side, the hinge bearing 8 comprises a left receiving element 11, in which a left bolt 9 is mounted on the fastening side, and a right receiving element 12 (cf 2 ), in which a right bolt 10 is mounted on the fastening side. In the embodiment shown, the pin axes 20 and the pivot axis 39 are congruent. Furthermore, a bracket 45 and the traverse 13 together with a support roller 43 and a spindle drive 46 (or its bellows) with a spindle axis 47 can be seen, which are explained in more detail below .

In 2 is the hinge actuator 1 according to 1 shown in a side view. The traverse 13 is arranged with its (paired here) support rollers 43 between a bearing track 48 on the base plate 38 and a lever track 49 on the back (related to the front-side actuating surface 40,41 of the actuating fingers 3,4) of the lever 6.

It is easy to see here that the traverse 13 is in the engaged position 15 and the support roller 43 is moved by means of the spindle drive 46 along the spindle axis 47 to the indicated disengaged position 14 on the bearing track 48 and the position oriented obliquely to the bearing track 48 Lever track 49 rolls off. This causes the lever 6 or the main extension 7 to pivot about the pivot axis 39 . Thus, the operating force is 50 along of the actuation path 5 with a high transmission ratio, for example for a torque clutch 2 (cf 8th ) generated. Furthermore, in this embodiment, the bolt axis 20 runs congruently with the pivot axis 39 of the hinge actuator 1 (perpendicular to the plane of the drawing, as shown). The bracket 45 is here (optionally) fixed by means of at least one round rivet 51 on the base plate 38 and thus the cross member 13 together with the spindle drive 46 . Bolt receptacle 19 (visible here in the picture on the right) is precisely aligned by means of a dowel pin 52, as with reference to the embodiment according to FIG 4 until 7 is explained.

In 3 is a hinge actuator 1 according to 1 shown in sectional view. The support roller 43 of the hinge actuator 1 can be seen here, which is mounted on the bearing track 48 and on the corresponding lever track 49 (cf 2 ) and is movable between an engaged position 15 (shown here) and a disengaged position 14. Here the one lever bridge 27 is positioned along the main extension 7 between the engaged position 14 and the disengaged position 15 . In this embodiment, a relatively high level of leverage is achieved as a result of the stiffening effect by means of deformed tabs with the left bolt receptacle 18 and the right bolt receptacle 19.

In 4 an alternative embodiment of a hinge actuator 1 is shown in a perspective view. For this purpose, reference is made to the previous description with regard to the functioning of a hinge actuator 1 and only the differences are highlighted. The maximum transverse dimension 42 is here at the hinge bearing 8, which is determined here by the receiving elements 11,12. In this embodiment, the hinge bearing 8 comprises a left bolt 9 with a bolt axis 20 on the fastening side and a corresponding left bolt receptacle 18 on a left bearing bracket 21 on the lever side (on the left of the spindle drive 46 according to the illustration). Correspondingly, on the right side, the hinge bearing 8 comprises a right bolt 10 with a bolt axis 20 on the fastening side and a corresponding right bolt receptacle 19 on a right bearing bracket 22 on the lever side. In the (ideal) embodiment shown, the bolt axes 20 are in relation to one another and (optionally) to the pivot axis 39 congruent. The bearing brackets 21,22 extend along the main extent 7 away from the actuating fingers 3,4, here (optionally) in an S-shape. The design of the bolt mounts 18,19 is in 5 explained in more detail. Here the left-hand actuating finger 3 with a left-hand partial lever 25 and the right-hand actuating finger 4 with a right-hand partial lever 26 are also formed in one piece as an extension of the main extension 7 of the lever 6 . The two partial levers 25, 26 are connected to one another in one piece by means of a first lever bridge 27 and a second lever bridge 28. The first lever bridge 27 is (in comparison to the previously described embodiment with a single lever bridge 27) arranged in the direction of the main extension 7 close to the actuating fingers 3, 4 and the second lever bridge 28 is arranged close to the hinge bearing 8, so that the actuating fingers 3, 4 and in the case of the hinge bearing 8, despite a (desired) relatively low lever stiffness (as a result of the bearing brackets 21, 22), the torsional stiffness is not too low.

In 5 the hinge actuator 1 according to the alternative embodiment is off 4 in a side view analogous to the representation of the hinge actuator 1 in 2 shown. It is so far on the descriptions of the 4 and the 2 referred. According to the representation, the left bolt 9 and the corresponding left bolt receptacle 18 on the left bearing bracket 21 are shown in this side view, with (optional) the right bolt 10 and the corresponding right bolt receptacle 19 of the right bearing bracket 22 being identical. Here, the left-hand bearing bracket 21 (S-shaped) can be inserted into the hinge bearing 8 approximately in the direction of the main extension 7 in such a way that the left-hand bolt receptacle 18 on the left-hand bearing bracket 21 is behind (i.e. in relation to the actuation path 5 of the lever 6) the left-hand bolt 9 is arranged. Furthermore, here in the embodiment, the pin axis 20 runs congruently with the pivot axis 39 of the hinge bearing 8 (perpendicular to the plane of the figure, as shown). The bracket 45 is (optionally) fixed to the base plate 38 by means of at least one round rivet 51 and the left receiving element 11 is aligned with the bracket 45 and the base plate 38 by means of a dowel pin 52 . A (left) bearing mount 16 is formed in the left-hand receiving element 11, on which the (left-hand) bolt 9 is mounted. The lever 6 can be pivoted about the pivot axis 39 by means of the (left) bolt receptacle 18 in order to exert the actuating force 50 or an actuating stroke along the actuating path 5 by means of the actuating surface 40 (shown here on the left). The description of the left side of the hinge actuator 1 also applies (optionally) to its right side.

In 6 is the hinge actuator 1 according to 4 shown in a sectional rear view. The cutting line is broken (vertical breaking line 65 for the left receiving element 11), so that the cutting plane for the left bolt 9 (on the right as shown) is located further forward in relation to the image plane than the cutting plane for the right bolt 10. Here it is easy to see that the left pin 9 in the left bearing mount 16 and the right pin 10 in the right bearing mount 17 is added. Furthermore, the left bolt 9 and the right bolt 10 for laterally securing the lever 6 (via the bearing brackets 21,22) each have an inner shoulder 53 and an outer shoulder 54, with pars-pro-toto the paragraphs 53,54 only marked with the right bolt 9. In cooperation with the respective receiving element 11,12 and the bearing bracket 21,22 in question, the bolt in question is secured laterally 9,10. The inner paragraph 53 and the outer paragraph 54 enclose the respective bearing surface of the bolt 9,10 (optional) like a groove, the bearing surface being in force-transmitting contact with the respective bolt receptacle 18,19 of the bearing brackets 21,22. The position of the bearing mounts 16 , 17 relative to the bracket 45 is fixed by means of a dowel pin 52 and a cam 55 formed on the respective receiving element 11 and a corresponding cam mount 56 in the bracket 45 .

In 7 is a hinge actuator 1 according to 4 shown in sectional view. Reference is made here to the analog representation in 3 referred.

In 8th a drive train 30 (optionally in front of a driver's cab 57 and optionally in a transverse arrangement, ie with an engine axis 58 transverse to the longitudinal axis 59 of the motor vehicle 37) is shown in a schematic view from above. The left-hand drive wheel 35 and the right-hand drive wheel 36 are here (optionally) driven by the drive train 30 . The drive train 30 includes a prime mover 33 (shown here as a three-cylinder internal combustion engine) and a torque clutch 2 coupled to the prime mover 33 via a machine shaft 34. Torque can be transmitted separably about the axis of rotation 29 or the congruent motor axis 58 by means of the torque clutch 2. A torque pack 31 is provided for the separability, which is here, for example, as a friction pack with a pressure plate 60, a counter plate 61, which are connected to the machine shaft 34 with a clutch cover 62 in a torque-transmitting manner, and a friction disk 63 arranged axially in between, which is connected via a gear (with dashed line indicated schematically) is connected in a torque-transmitting manner to the drive wheels 35,36. The actuating force 50 of the hinge actuator 1 can be transmitted here via a lever spring 64, which is supported on the clutch cover 62, and an actuating bearing 32 to the torque pack 31 of the torque clutch 2, and the torque pack 31 can thus be separated (normally closed configuration) or closed (normally open configuration ).

With the hinge actuator proposed here, installation space can be saved and at the same time the costs can be significantly reduced.

Reference List

1

hinge actuator

2

torque clutch

3

left actuating finger

4

right actuating finger

5

actuation path

6

lever

7

main extension

8th

hinge bearing

9

left bolt

10

right bolt

11

left pick-up element

12

right pick-up element

13

traverse

14

disengaged position

15

indented position

16

left bearing mount

17

right bearing mount

18

left bolt mount

19

right bolt mount

20

bolt axle

21

left bearing bracket

22

right bearing tab

23

left mounting screw

24

right mounting screw

25

left partial lever

26

right partial lever

27

first lever bridge

28

second lever bridge

29

axis of rotation

30

powertrain

31

torque package

32

actuation bearing

33

prime mover

34

machine shaft

35

left drive wheel

36

right drive wheel

37

motor vehicle

38

base plate

39

pivot axis

40

left button

41

right button

42

maximum transverse dimension

43

support roller

44

finger spacing

45

hanger

46

spindle drive

47

spindle axis

48

storage track

49

lever track

50

operating force

51

round rivet

52

dowel pin

53

inner paragraph

54

outer heel

55

cam

56

cam recording

57

driver's cabin

58

motor axis

59

longitudinal axis

60

pressure plate

61

counter plate

62

clutch cover

63

friction disc

64

lever spring

65

fault line

66

left storage section

67

right storage section

Claims (10)

Hinge actuator (1) for a torque clutch (2), having at least the following components: - at least one actuating finger (3,4) for transmitting an actuating travel (5) to a torque clutch (2); - a lever (6) with a main extension (7) which is connected to the actuating finger (3,4); - A hinge bearing (8) for the pivotable mounting of the lever (6); and - a traverse (13) in force-transmitting contact with the lever (6), wherein the traverse (13) can be moved along the main extension (7) between a disengaged position (14) and an engaged position (15) and wherein by means of the method of - the lever (6) together with the actuating finger (3,4) is the only spring element that determines the rigidity of the lever (6), characterized in that that the hinge bearing (8) has two bolts (9,10) with a bolt axis (20) and a corresponding bolt receptacle (18,19) each, the bolt receptacle (18,19) each being supported by a bearing bracket (21,22) of the lever (6) is formed, wherein the bearing bracket (21,22) extends along the main extension (7) away from the actuating finger (3,4). Hinge actuator (1) for a torque clutch (2), having at least the following components: - at least one actuating finger (3,4) for transmitting an actuating travel (5) to a torque clutch (2); - a lever (6) with a main extension (7) which is connected to the actuating finger (3,4); - A hinge bearing (8) for the pivotable mounting of the lever (6); and - a traverse (13) in force-transmitting contact with the lever (6), wherein the traverse (13) can be moved along the main extension (7) between a disengaged position (14) and an engaged position (15) and wherein by means of the method of - the lever (6) together with the actuating finger (3,4) is the only spring element that determines the rigidity of the lever (6), characterized in that that the hinge bearing (8) has two bolts (9,10) with a bolt axis (20) and a corresponding bolt receptacle (18,19) each, the bolt receptacles (18,19) each being in one of the main extension (7) and to the bolt axis (20) angled bearing section (66,67) of the lever (6) is formed Hinge actuator (1) after claim 1 or 2 , wherein two actuating fingers (3,4) with a finger spacing (44) transverse to the main extension (7) of the lever (6) and the hinge actuator (1) has a maximum transverse dimension (42) parallel to the finger spacing (44), wherein the maximum transverse dimension (42) is less than 4 times the finger spacing (44). Hinge actuator (1) after claim 1 , wherein in the disengaged position (14) the lever stiffness of the lever (6) is between 1 kN/mm and 2 kN/mm. Hinge actuator (1) according to one of Claims 1 or 4 , wherein the bearing brackets (21,22) based on a cross section with the bolt axis (20) Nor male run in an arc between the rest of the lever (6) and the bolts (9,10). Hinge actuator (1) according to one of the preceding claims, wherein the lever (6) is secured laterally by means of the hinge bearing (8). Hinge actuator (1) according to one of the preceding claims, wherein the lever (6) comprises two partial levers (25,26) which are connected to one another in one piece by means of at least one lever bridge (27,28). Torque clutch (2) with an axis of rotation (29) for a drive train (30), having at least the following components: - A hinge actuator (1) according to any one of the preceding claims; - A torque pack (31) which can be actuated axially for the controllable transmission of a torque by means of the hinge actuator (1); and - An actuation bearing (32) between the torque assembly (31) and the actuation finger (3,4) of the hinge actuator (1), the actuation path (5) opening via the actuation bearing (32) by means of the traverse (13) of the hinge actuator (1). the torque package (31) is transferrable. Drive train (30), having at least one drive machine (33) with a machine shaft (34), at least one consumer (35, 36) and a torque clutch (2). claim 8 , wherein the machine shaft (34) is connected to the at least one consumer (35, 36) in a torque-transmitting manner by means of the torque clutch (2) in a controllable manner. Motor vehicle (37) having at least one driving wheel (35, 36) which, by means of the drive train (30), claim 9 is drivable.

Images