Hinge actuator for torque clutch

Abstract

The invention relates to a hinge actuator (1) for a torque clutch (2), comprising at least the following components: at least one actuating finger (3, 4) for transmitting an actuating path (5) to the torque clutch (2); a lever (6) with a main extension (7) connected to the actuating finger (3, 4); a hinge support (8) with a hinge axis (9), about which the lever (6) can be pivoted; a crossbar (10) in force-transmitting contact with the lever (6), which can be moved along the main extension (7) of the lever (6) between an extended position (11) and an extended position (12), by means of which the lever (6) can be pivoted for actuation. The hinge actuator (1) is characterized in that the hinge support (8) comprises an adjustment mechanism (13), by means of which the position of the hinge axis (9) can be adjusted during installation. The hinge actuator proposed here can be installed in particularly narrow construction spaces and can be installed simply and without tension.

Description

Technical Field

[0001] The invention relates to a hinge actuator for a torque clutch, a torque clutch having a rotation axis for a powertrain having such a hinge actuator, a powertrain having such a torque clutch, and a motor vehicle having such a powertrain. Background Art

[0002] Joint actuators for actuating torque clutches, such as friction clutches, for drive trains, such as for motor vehicles, are known from the prior art. Such a joint actuator is shown, for example, in DE 10 2004 009 832 A1 (for example in FIGS. 13 to 17 therein). The following problem generally arises: the construction space available for the joint actuator, in particular the construction space transverse to the main extension of the lever of the joint actuator, is extremely limited. However, at the same time, cost pressure, in particular in the vehicle sector, is high both in terms of unit costs and in terms of installation costs. Summary of the invention

[0003] Starting 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 are derived from the independent claims, including the advantageous embodiments described in the dependent claims. The features of the claims can be combined in all technically meaningful ways and methods, wherein for this purpose, the explanations from the following description and the features from the drawings can also be used, which include supplementary embodiments of the invention.

[0004] The present invention relates to a hinge actuator for a torque clutch, the hinge actuator having at least the following components:

[0005] - at least one actuating finger for transmitting an actuating path to the torque clutch;

[0006] - a lever having a main extension, said lever being connected to the actuating finger;

[0007] - a hinge bearing having a hinge axis about which the lever can be pivoted; and

[0008] A crossbar in force-transmitting contact with the lever, wherein the crossbar is movable along the main extension of the lever between an extended position and an inserted position, and wherein the lever can be pivoted by means of the crossbar for actuation.

[0009] The hinge actuator is characterized essentially in that the hinge support mechanism also comprises an adjustment mechanism, by means of which the position of the hinge axis can be calibrated during installation.

[0010] The hinge actuator proposed here is set up for example for a torque clutch, for example an axially compressible friction clutch. Alternatively, the hinge actuator is generally set up for transmitting axial forces, preferably by means of a central rotating shaft. The hinge actuator comprises at least one, preferably two operating fingers, wherein, for example, when used in a torque clutch, the two operating fingers act on the operating bearing on the left and right of the rotating shaft, for example, the transmission input shaft. The operating finger transmits the operating path to the torque clutch. The operating finger is connected to a lever, for example, formed in one piece, wherein the lever has a main extension. The main extension corresponds to the lever in a simplified model, wherein the actual part of the lever, for example as a plate part, does not necessarily have a symmetry relative to the main extension, and does not necessarily have its maximum extension direction in the direction of the main extension (center axis). The main extension is defined as the following plane: the hinge axis (see the following explanation) extends through the plane, and the operating surface of the operating finger is oriented tangentially to the plane. In the case of two actuating fingers, the center axis extending centrally between the actuating fingers and intersecting the hinge axis, preferably perpendicularly, extends in the plane of the main extension. For many applications, it is advantageous to implement the lever in a cost-effective and space-saving manner, so that the lever is particularly advantageous in this respect as a sheet metal part with reinforcing ribs and / or a bead. In particular, in such an embodiment made of sheet metal, the main extension as a theoretical plane does not necessarily extend completely through the actual part of the lever.

[0011] The lever is pivotably supported about the hinge axis by means of a hinge support mechanism, so that the pivoting of the lever about the hinge axis for applying the actuating path by means of at least one actuating finger describes the basic function of the lever. In addition, a crossbar is provided in the hinge actuator. The crossbar is in such a force-transmitting contact with the lever that the lever pivots about the hinge axis by means of the movement of the crossbar along the main extension. The crossbar, which is preferably formed by a single or multiple, preferably two, support rollers for transmitting the force to the lever with low friction, is movable between an ejection position and an insertion position. The crossbar forms a ramp-shaped actuating assembly together with the lever. For example, the actuating assembly is formed by means of a lever ramp on the crossbar side (the rear side of the lever) and a support rail at the side opposite to the crossbar (for example, at the base plate). The slope of the lever ramp and / or the support rail can be arbitrarily implemented for individual requirements. For a linearly driven crossbar, for example, by means of a screw drive mechanism having a screw axis as the linear movement axis, it is advantageous to implement the support rail flatly.

[0012] Via the actuating finger, the lever provides no actuating path or a minimal actuating path (e.g. for a minimum required axial preload) in the pushed-in position of the crossbar, and a maximum actuating path in the pushed-out position. It should be noted that the main extension moves with the lever, so that from the perspective of a coordinate system moving with the lever, the crossbar describes a circular or arc-shaped path, for example with a constant slope of the lever ramp. Nevertheless, the crossbar particularly preferably moves along a fixed screw axis, wherein the screw axis is fixed relative to a fixed component, for example a base plate of a hinge actuator.

[0013] As described above, the crossbar is driven, for example, by a screw drive, for example a ball screw drive, with a screw axis, wherein the crossbar itself is implemented as a slide, which includes a driven (axially movable) screw nut or a driven (axially movable) screw, and the driven (rotating) screw or the driven (rotating) screw nut is driven by a rotating, preferably electric drive machine. The screw axis is preferably in the pivot plane of the lever, the hinge axis is oriented normally to the pivot plane, and the center axis is in the pivot plane. The pivot axis is preferably fixed. Alternatively, the pivot axis can be pivoted, for example, about the hinge axis.

[0014] It is now proposed that the joint actuator comprises an adjustment mechanism, by means of which the orientation of the joint axis of the joint support mechanism can be calibrated during installation. It is not excluded that the joint axis has already been calibrated (by means of the adjustment mechanism) before installation. The joint axis can thus be oriented during calibration so that the joint actuator or the lever can carry out a low-tension or even untensioned pivoting movement about the correspondingly calibrated joint axis during operation. In principle, the adjustment mechanism can be designed so that calibration can be carried out in each degree of freedom constrained by means of the joint support mechanism, wherein each of the degrees of freedom can preferably be adjusted by means of a separate adjustment device of the adjustment mechanism.

[0015] Furthermore, in an advantageous embodiment of the joint actuator it is provided that the adjusting mechanism enables an calibrated rotation of the joint axis about the main extension.

[0016] In the advantageous embodiment, preferably only the calibration rotation of the joint axis about the center axis can be calibrated by means of the adjustment mechanism. This means that the actuating finger can be tilted (orientated) by means of the adjustment mechanism, for example when used in a torque clutch, relative to the (ideally) normally oriented rotation axis of the torque clutch. In the embodiment in which the calibration rotation is adjustable by means of the adjustment mechanism as the only calibration possibility, the orientation is preferably calibrable along a single degree of freedom by means of a single adjustment device, for example by means of a mounting screw and a corresponding adjustment device, for example a washer (also called a washer) with a defined (axial) height of the screw.

[0017] Furthermore, in an advantageous embodiment of the joint actuator it is provided that the adjusting mechanism enables a calibrated displacement of the joint axis transversely to the main extension.

[0018] In this embodiment, the hinge axis is displaceable by means of an adjustment mechanism, more precisely transversely, for example normal to the main extension, for example parallel to the (ideally oriented) actuating force that can be applied by the actuating finger. By means of the displaceable position of the hinge axis (parallel) relative to the ideal hinge axis, the preload of the lever and / or the maximum pivotability about the hinge axis can be adjusted.

[0019] Furthermore, in an advantageous embodiment of the hinge actuator, it is proposed that the adjustment mechanism is arranged at at least one mounting bolt for fastening the hinge actuator, wherein, preferably, an adjustment bolt axially preloaded by the bolt forms a calibratable abutment for the mounting bolt in question, wherein, particularly preferably, a torsion stop is provided between the adjustment bolt and the mounting bolt in question.

[0020] It is proposed that the adjustment mechanism is arranged on a fixed component, for example a transmission cover in the powertrain of a motor vehicle, when at least one of the mounting bolts for fastening the hinge actuator is provided. For example, the adjustment mechanism is formed by the mounting bolt itself or an intermediate element, for example a disk as described above, but alternatively by a mounting bolt that can be selected according to the desired calibration direction. In a preferred embodiment, an adjustment bolt with axial prestressing of the bolt is formed between the mounting bolt and a base plate of a fastening device, for example a hinge actuator. With the aid of the adjustment bolt, an abutment for the mounting bolt is formed and the abutment (height) is adjustable, preferably steplessly (height), so that a calibration rotation (in the case of a single adjustment bolt) and / or a calibration displacement (in the case of two mounting bolts, for example, each with an adjustment bolt) can be achieved.

[0021] In a particularly preferred embodiment, a rotation lock is provided between the adjusting screw and the respective mounting screw, wherein the relative position between the adjusting screw and the respective mounting screw, which is adjusted once during installation, and thus the calibrated position of the hinge axis, is locked by means of the rotation lock. Such a rotation lock can be formed, for example, by a form fit, a material fit and / or a force fit, for example by means of a contour pattern, a locking plate, an adhesive bond (for example by means of an anaerobic locking adhesive), a caulking, locking particles, etc. Particularly preferably, the rotation lock is formed by means of a corresponding toothing, into which the mounting screw locks when the mounting screw reaches its end position. In order to suppress play in the axial direction of the screw and due to slight tilting in an embodiment of the adjusting screw with axial bolt prestressing, a prestressing energy store is preferably provided, for example by means of a wave spring arranged (approximately) coaxially with respect to the screw axis of the mounting screw or a wave spring plate superposed.

[0022] According to another aspect, a torque clutch having a rotation axis for a powertrain is provided, having at least the following components:

[0023] - a hinge actuator according to one of the above embodiments;

[0024] a torque plate pack, preferably an axially compressible friction plate pack, which can be axially manipulated by means of a hinge actuator for transmitting torque; and

[0025] - a steering bearing between the torque plate stack and the hinge actuator,

[0026] In this case, the joint actuator is provided with at least one, preferably two, actuating fingers which act on the actuating bearing.

[0027] In the following text, when the axial direction, radial direction or circumferential direction and the corresponding terms are used, reference is made to the mentioned rotation axis unless otherwise explicitly stated. Unless otherwise explicitly stated, the ordinal numbers used in the above description serve only for unambiguous distinguishability and do not indicate an order or priority of the components described. An ordinal number greater than one does not necessarily entail the mandatory presence of further such components.

[0028] The torque clutch proposed here is, for example, a friction clutch or a form-fitting clutch, such as, for example, a claw clutch or a so-called wedge clutch. With the help of the torque clutch, the torque can be transmitted separably around the rotation axis. The torque clutch is a switching element for transmitting or for separating a connection for torque transmission, wherein the torque plate stack is responsible for the task. The torque plate stack is axially actuable with the help of a hinge actuator, and is implemented as a friction plate stack, for example, which can be axially compressed, wherein then the actuating force that may be converted via a lever spring is proportional to the desired maximum torque that can be transmitted. The hinge actuator is arranged so that the hinge actuator or its hinge axis (ignoring the spring stiffness) is fixed, for example, fixed to a fixed part by means of a mounting screw, and the shaft connected by means of the torque clutch, for example, the transmission input shaft, extends between the actuating fingers in an embodiment with two actuating fingers. The actuating fingers act, preferably via an actuating bearing, on a rotating bearing ring, and the rotating bearing ring transmits the actuating force from the rotating bearing ring to the torque plate stack. With the help of the actuating bearing, the actuating fingers and thus the hinge actuator are freed from torque. In the retracted position of the crossbar, no actuation path or only a minimal actuation path (for the desired minimum preload) is exerted on the actuation bearing, and in the retracted position a maximum actuation path is exerted on the actuation bearing.

[0029] The torque clutch has an axially actuatable torque plate stack, for example an axially pressable friction plate stack for the separable transmittability of torque. In the friction plate stack, at least two friction plates and at least one clutch disk are provided. In a simple embodiment, a single clutch disk is provided between a first friction plate of an axially movable pressure plate and a second friction plate of a preferably axially fixed counter-pressure plate, and can be pressed between them for torque transmission with friction fit by means of a pressing force. The pressing force is generated or (servo) supported by a hinge actuator, wherein the output actuation force is usually converted into a pressing force by means of a lever spring. Due to the pressing force, a friction force is obtained via a surface friction pair between a region of the clutch disk predetermined for friction fit and (each) corresponding counter-friction region of each friction plate, which friction force is multiplied by the average radius of the friction surface formed to obtain a transmittable torque. Multiplied by the number of friction pairs, for example, the transmittable (maximum) total torque of the friction clutch is obtained. In the unpressed state of the friction plate stack, no torque can be transmitted or only a small permissible drag torque can be transmitted. The friction clutch is designed, for example, as a double clutch with two friction plate stacks, wherein the individual counterpressure plates are preferably formed by a common central disk.

[0030] The hinge actuator proposed here can be installed in a particularly small construction space and without tension, wherein at the same time, during installation, calibration can be particularly simple to implement. In a double clutch, for example, two hinge actuators proposed here (eg, twisted about a rotation axis relative to each other) are provided.

[0031] According to a further aspect, a drive train is proposed, comprising: at least one drive machine with a machine shaft, at least one drive wheel and a torque clutch according to the above-described embodiment, wherein the machine shaft is adjustably connected to the at least one drive wheel in a torque-transmitting manner by means of the torque clutch.

[0032] The drive train proposed here comprises a torque clutch, for example a friction clutch, according to the above-described embodiments, wherein the torque clutch can be switched, i.e. disengaged, by means of an actuating force or a pressing force exerted on a torque plate stack, for example a friction plate stack, by an articulated actuator according to the above-described embodiments to transfer torque from a drive machine or its machine shaft to at least one drive wheel, for example a drive wheel in a motor vehicle. This by no means excludes a reverse torque transfer from the drive wheel to the machine shaft, in a motor vehicle, for example for engine braking to decelerate the motor vehicle and / or for recovering 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 to at least one drive wheel in a torque-proof manner (at least indirectly, for example via a transmission).

[0033] The proposed torque clutch is particularly advantageous for use in drive trains in which the available construction space for the hinge actuator is small and preferably particularly high actuating forces are required. The hinge actuator proposed here can be installed in a particularly small construction space and without tension, and at the same time, during installation, calibration can be carried out particularly easily.

[0034] According to a further aspect, a motor vehicle is proposed, having at least one drive wheel which is drivable by means of a drive train according to the above-described embodiment.

[0035] Especially in motor vehicles, the installation space is particularly small due to the increasing number of components, and it is therefore particularly advantageous to use a drive train with smaller construction dimensions. With the desired so-called downsizing of the drive machine while reducing the operating speed at the same time, the intensity of disturbing torque vibrations increases, and the requirements for actuating forces also increase with increasing torques or torque clutch reductions. Therefore, the challenge is to provide sufficient actuating forces with the aid of a hinge actuator while having simultaneously low component costs and little available construction space.

[0036] The problem is exacerbated in passenger cars of the small car class according to the European classification. The devices used in passenger cars of the small car class are not significantly reduced compared to passenger cars of the larger vehicle class. Therefore, the available construction space in small cars is significantly smaller. The proposed torque clutch is particularly advantageous for use in drive trains in which the available construction space for the hinge actuator is small and preferably particularly high actuating forces are required. The hinge actuator proposed here can be installed in a particularly small construction space and without tension, and at the same time, calibration can be carried out particularly easily during installation.

[0037] Passenger cars are assigned to vehicle classes according to, for example, size, price, weight and power, wherein the definitions are constantly changing according to market requirements. In the US market, vehicles according to the classes "Small Car" and "Smallest Car" of the European classification are assigned to the class "Subcopact Car", and in the UK market this corresponds to the class "Supermini" or the class "City Car". Examples of the smallest car class are the Volkswagen up! or the Renault Twingo. Examples of the small car class are the Alfa Romeo MiTo, the Volkswagen Polo, the Ford Ka+ or the Renault Clio. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] The above invention is explained in detail below with reference to the relevant drawings showing preferred designs against the relevant technical background. The invention is not limited in any way by the purely schematic drawings, wherein it should be pointed out that the embodiments shown in the drawings are not dimensionally accurate and are not suitable for defining dimensional ratios. The drawings show:

[0039] Figure 1 showing a hinge actuator in a perspective view;

[0040] Figure 2 The hinge actuator is shown in side view;

[0041] Figure 3 The hinge actuator is shown in a top view;

[0042] Figure 4 The hinge actuator is shown in a rear view with two adjustment bolts; and

[0043] Figure 5 A motor vehicle is shown having a powertrain and a hinge actuator. DETAILED DESCRIPTION

[0044] exist Figure 1 The hinge actuator 1 is shown in a three-dimensional view in FIG. Here (optionally), the hinge actuator 1 has a base plate 30 on which there is a main extension 7 (see FIG. Figure 2) is pre-mounted pivotably about the hinge axis 9 (optionally) as a structural unit, here (optionally) by means of a mounting screw 16 on the left (according to the illustration) and a mounting screw 17 on the right (according to the illustration). Left and right here and in other cases only refer to Figure 1 . The hinge axis 9 can be adjusted in the structural unit (and during installation) by means of the adjusting mechanism 13. In the embodiment of the hinge actuator 1, the adjusting mechanism 13 is formed by means of the (single, here left) adjusting screw 18 at the left mounting screw 16, so that a calibrated rotation of the hinge axis 9 about the main extension 7 of the lever 6 is achieved. For this purpose, the hinge support 8 or the left part of the hinge support 8 can be displaced along the screw axis by means of the left mounting screw 16 in cooperation with the adjusting screw 18 and the preload energy storage 31. The preload energy storage 31 is designed as a wave spring plate pack and the screw is arranged axially between the component with the left part of the hinge support 8 and the base plate 30. In order to avoid uncontrolled rotation of the hinge axis 9 or reverse rotation of the hinge axis 9, a rotation protection device 20 is provided here (optionally) between the left mounting screw 16 and the adjusting screw 18, and the rotation protection device is optionally designed as a locking toothing.

[0045] exist Figure 2 The side view shows the Figure 1A hinge actuator 1 is provided, wherein the main extension 7 of the lever 6 is parallel to the plane of the paper and the hinge axis 9 is oriented perpendicular to the plane of the paper. The lever 6 is pivotably connected to a base plate 30 by means of mounting screws 16, 17. In the view, a lever track 32 of the lever 6 is shown in dashed lines (blocked edges). The lever track 32 describes the part of the lever 6 at which (at least one, preferably two) supporting rollers 33 of the crossbar 10 roll in the push-out position 11 and in the push-in position 12. Corresponding to the lever track 32 of the lever 6, the base plate 30 has a fixed supporting rail 34, wherein the supporting rail 34 is (optionally) oriented parallel to the screw 35. The supporting rail 34 and the lever track 32 together with the supporting roller 33 of the crossbar 10 form a kinematic assembly, which converts the screw axial movement of the supporting roller 33 into a pivoting movement of the actuating fingers 3, 4, wherein the force conversion is preferably achieved by means of a path shortening from the path of the crossbar 10 to the path of the actuating fingers 3, 4. The spindle drive 36 comprises a spindle 35 (shown here with a dotted line as a shielded edge) and a spindle nut 37, wherein the slide of the crossbar 10 is described here as a spindle nut 37. The slide is preferably designed in one piece with the spindle nut thread. The spindle drive 36 has a motor connection 38 at the end, to which an electric motor (optionally) can be connected. The support roller 33 is shown in dashed lines in the push-out position 11 (on the left side of the illustration; the current position of the lever 6, wherein the support roller 33 is partially shielded) and in the push-out position 12 by means of long dashed lines (on the right side; the lever 6 is then tilted upwards about the pivot axis). Therefore, the actuating force 5 is applied to the torque plate stack 23 via the actuating fingers 3, 4 depending on the pivot position of the lever 6, i.e., depending on the position 11, 12 of the support roller 33.

[0046] exist Figure 3 The top view shows the Figure 1 and Figure 2 The hinge actuator 1 of FIG. 1 is shown in FIG. 1 , wherein the heads of the mounting bolts 16 and 17 are observed. Here, the right operating finger 3 and the left operating finger 4 can be clearly seen (according to FIG. 1 ). Figure 1 ). It can also be clearly seen that the (left-hand) adjusting screw 18 is secured against uncontrolled adjustment by means of a rotation securing device 20 designed as a toothing.

[0047] exist Figure 4 An alternative embodiment of a hinge actuator 1 is shown in FIG. 1 , wherein the embodiment shown is purely for the sake of overview. Figures 1 to 3 The diagram in is basically the same as that in Figures 1 to 3Compared to the embodiment of the present invention, the hinge axis 9 can be calibrated here by means of the (previously described) left adjusting screw 18 and the additional (optionally identical) right adjusting screw 19. If only one of the adjusting screws 18 is calibrated or the two adjusting screws 18, 19 are calibrated in opposite directions or at different heights relative to the base plate 30, the hinge axis 9 is twisted about a parallel line of the main extension 7, i.e., the calibration rotation 14 (about the central axis 39) is carried out. The central axis 39 is shown here in a simplified manner perpendicular to the paper plane, but is preferably parallel to the main extension 7 (see Figure 2 If the two adjusting screws 18 , 19 are adjusted identically, a calibration displacement 15 is produced. The preload energy store 31 is preferably designed both for the calibration rotation 14 and for the calibration displacement 15 relative to the clearance-free area.

[0048] exist Figure 5 2 shows a drive train 22 from above in a schematic illustration (optionally in front of a driver's cabin 40 and optionally in a transverse arrangement, i.e. with an engine axis 41 transverse to a longitudinal axis 42 of a motor vehicle 29). A left drive wheel 27 and a right drive wheel 28 are here (optionally) driven by the drive train 22. The drive train 22 comprises a drive machine 25 (shown here as a three-cylinder internal combustion engine) and a torque clutch 2 coupled to the drive machine 25 via a machine shaft 26. The torque can be transmitted about the rotation axis 21 or the coincident engine axis 41 by means of the torque clutch 2 in a releasable manner. For the releasability, a torque plate stack 23 is provided, which is designed here as a friction plate stack by way of example, and which has a pressure plate 43, a counter-pressure plate 44 connected to the machine shaft 26 in a torque-transmitting manner by means of a clutch cover 45, and a friction disk 46 arranged axially between the pressure plate and the counter-pressure plate and connected to the drive wheels 27, 28 in a torque-transmitting manner via a transmission (schematically indicated by dashed lines). The actuating force 5 of the hinge actuator 1 can be transmitted to the torque plate stack 23 of the torque clutch 2 via the lever spring 47 supported on the clutch cover 45 and the actuating bearing 24 so that the torque plate stack 23 can be separated (normally closed configuration) or closed (normally open configuration).

[0049] The hinge actuator proposed here can be used in particularly confined installation spaces and can at the same time be installed simply and without tension.

[0050] Reference numerals list

[0051] 1 Hinge Actuator

[0052] 2 Torque Clutch

[0053] 3 Left control finger

[0054] 4 Right control finger

[0055] 5. Control

[0056] 6 Leverage

[0057] 7 Main Extension

[0058] 8 Hinge support mechanism

[0059] 9 Hinge axis

[0060] 10 Crossbar

[0061] 11 Push-out position

[0062] 12 Push-in position

[0063] 13 Adjustment mechanism

[0064] 14 Calibration rotation

[0065] 15 Calibration Shift

[0066] 16 Left mounting bolt

[0067] 17 Right mounting bolt

[0068] 18 Left adjusting bolt

[0069] 19 Right adjusting bolt

[0070] 20 Torsion lock

[0071] 21 Rotation axis

[0072] 22 Powertrain

[0073] 23 Torque plate stack

[0074] 24 Manipulator bearing

[0075] 25 Drive Machine

[0076] 26 Machine Axles

[0077] 27 Left drive wheel

[0078] 28 Right drive wheel

[0079] 29 Motor Vehicles

[0080] 30 substrate

[0081] 31 Preload accumulator

[0082] 32 Lever Track

[0083] 33 Support roller

[0084] 34 Support rail

[0085] 35 Screw

[0086] 36 Screw drive mechanism

[0087] 37 Screw nut

[0088] 38 Engine connection terminal

[0089] 39 Central Axis

[0090] 40 Driver's cabin

[0091] 41 Engine axis

[0092] 42 Vertical axis

[0093] 43 Platen

[0094] 44 Back pressure plate

[0095] 45 Clutch cover

[0096] 46 Friction disc

[0097] 47 Lever Spring

Claims

1. A hinge actuator (1) for a torque clutch (2), the hinge actuator having at least the following components: - at least one actuating finger (3, 4) for transmitting an actuating path (5) to the torque clutch (2); - a lever (6) having a main extension (7), said lever being connected to said operating finger (3, 4); - a hinge support (8) having a hinge axis (9) about which the lever (6) can be pivoted; and - a crossbar (10) in force-transmitting contact with the lever (6), wherein: The crossbar (10) is movable along the main extension (7) of the lever (6) between an extended position (11) and an inserted position (12), and the lever (6) can be pivoted for actuation by means of the crossbar (10), It is characterized in that The hinge support mechanism (8) also comprises an adjustment mechanism (13), by means of which the position of the hinge axis (9) can be calibrated during installation; the adjustment mechanism (13) can realize a calibrated rotation (14) of the hinge axis (9) around the main extension (7).

2. The hinge actuator (1) according to claim 1, wherein: The adjustment mechanism (13) enables a calibrated displacement (15) of the hinge axis (9) transversely to the main extension (7).

3. The hinge actuator (1) according to any one of the preceding claims, wherein: The adjustment mechanism (13) is arranged at at least one mounting bolt (16, 17) for fastening the hinge actuator (1).

4. The hinge actuator (1) according to claim 3, wherein: An adjuster screw (18, 19) which is preloaded in the axial direction of the screw is used to produce an adjustable contact for the respective mounting screw (16, 17).

5. The hinge actuator (1) according to claim 4, wherein: A rotation locking device (20) is provided between the adjusting screw (18) and the mounting screw (16) in question.

6. A torque clutch (2) having a rotation axis (21) for a powertrain (22), the torque clutch having at least the following components: - A hinge actuator (1) according to any one of the preceding claims; - a torque plate stack (23); and - a steering bearing (24) between the torque plate stack (23) and the hinge actuator (1), in, The hinge actuator (1) is provided with at least one steering finger (3, 4) acting on the steering bearing (24).

7. The torque clutch (2) according to claim 6, wherein: The torque plate stack (23) is an axially compressible friction plate stack which can be axially actuated by means of the joint actuator (1) for transmitting a torque.

8. A power transmission system (22) comprising: At least one drive machine (25) having a machine shaft (26), at least one drive wheel (27, 28) and a torque clutch (2) according to claim 6, wherein: The machine shaft (26) is adjustably connected to the at least one drive wheel (27, 28) in a torque-transmitting manner by means of the torque clutch (2).

9. A motor vehicle (29) comprising: At least one drive wheel (27, 28) which can be driven by means of the drive train (22) according to claim 8.

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