Hinge actuator for a torque clutch

Abstract

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 path to the torque clutch; a lever having a main extension, which is connected to the actuating finger; a hinge bearing having a hinge axis, about which the lever can pivot; and a crossbar in force-transmitting contact with the lever, wherein the crossbar can be moved along the main extension between an ejection position and a push-in position, and wherein the crossbar can be pivoted by means of the lever for actuation. The hinge actuator is primarily characterized in that the hinge bearing is formed by a bridge and a convexly spherical protrusion around the hinge axis, such that only a point contact is formed between the convexly spherical protrusion and the bridge, wherein the convexly spherical protrusion rests in force-transmitting contact on the bridge. The hinge actuator presented here can be used in particularly narrow construction spaces and at the same time is less complex in terms of construction.

Description

TECHNICAL FIELD

[0001] The invention relates to a hinge actuator for a torque clutch, to a torque clutch with a rotational axis for a powertrain having such a hinge actuator, to a powertrain having such a torque clutch, and to a motor vehicle having such a powertrain. BACKGROUND

[0002] From the prior art, a pivoting lever actuator is also known. Thus, a pivoting lever actuator is already known from DE 10 2014 210 349 A1. In the pivoting lever actuator, a pivoting lever is pivotably supported via a bearing. To this end, the bearing has a surface which corresponds to the push-out lever.

[0003] From the prior art, hinge actuators for actuating torque clutches, for example friction clutches, for powertrains, for example motor vehicle powertrains, are known. Such a hinge actuator is shown, for example, in DE 10 2013 211 227 A1. Furthermore, such a hinge actuator is also shown, for example, in DE 10 2004 009 832 A1, for example in Figures 13 to 17 thereof. It is generally the case that the construction space available for the hinge actuator, in particular the construction space transverse to the main extension of the lever of the hinge actuator, is extremely limited. At the same time, cost pressure, in particular in the vehicle sector, is high, not only in terms of individual part costs but also in terms of installation costs. SUMMARY

[0004] On the basis thereof, it is an object of the present invention to at least partially overcome the disadvantages known from the prior art. The features according to the invention result from the present text and advantageous design embodiments are set out herein. The features according to the invention can be combined in all technically meaningful ways and methods, for which the explanations from the following description and the features from the figures can also be employed, which include supplementary design embodiments of the invention.

[0005] The invention relates to a hinge actuator for a torque clutch, having at least the following components:

[0006] at least one actuating finger for transferring an actuating path onto the torque clutch;

[0007] a lever having a main extension, which is connected to the actuating finger;

[0008] a hinge bearing having a hinge axis, about which the lever can pivot; and

[0009] - a crossbar which is in force-transmitting contact with the lever, wherein the crossbar is movable along a main extension between an ejection position and an injection position, and wherein the crossbar is pivotable by means of the lever for actuation.

[0010] The main feature of the hinge actuator is that the hinge bearing mechanism is formed by a bridge and a convexly spherical protrusion which bears against the bridge in a force-transmitting manner around the hinge axis.

[0011] The hinge actuator presented here is designed, for example, for a torque clutch, for example an axially compressible friction clutch. Alternatively, the hinge actuator is generally designed for transmitting axial forces, preferably by means of a central rotary shaft. The hinge actuator comprises at least one, preferably two actuating fingers, wherein, for example, when used in a torque clutch, the two actuating fingers act on the actuating bearing on the left and right of a rotary shaft, for example a transmission input shaft. The actuating fingers transmit an actuating path to the torque clutch. The actuating fingers are connected to a lever, for example formed in one piece, wherein the lever has a main extension. The main extension corresponds in a simplified model to the lever, wherein the real component of the lever, for example as a sheet metal component, does not necessarily have to have a symmetry with respect to the main extension and also does not necessarily have its greatest extension direction in the direction of the (central) axis of the main extension. The main extension is defined as the plane through which the hinge axis (see below) extends and in which the actuating faces of the actuating fingers are oriented tangentially. In the case of two actuating fingers, a central axis which extends centrally between the actuating fingers and preferably intersects the hinge axis perpendicularly extends in the plane of the main extension. It is advantageous for various applications to implement the lever cost-effectively and to save construction space, so that the lever as a sheet metal component with stiffening ribs and / or hemming is particularly advantageous in this respect. Just in this embodiment consisting of sheet metal, the main extension as a theoretical plane does not necessarily extend completely through the real component of the lever.

[0012] The lever is pivotably supported about a hinge axis by means of a hinge bearing, such that the lever thus describes a pivot about the hinge axis for exerting a manipulation path by means of the at least one manipulation finger. Furthermore, a crossbar is provided in the hinge actuator. The crossbar is in such force-transmitting contact with the lever that the lever is pivoted about the hinge axis by means of the crossbar along a main extent. The crossbar, which is preferably formed by a single or a plurality of, preferably two, bearing rollers for transmitting force to the lever with low friction, is movable between a pushed-out position and a pushed-in position. The crossbar together with the lever forms a ramp-like manipulation assembly. The manipulation assembly is formed, for example, by means of a lever ramp (rear side of the lever) on the side of the crossbar and a bearing rail at the side opposite the crossbar, for example at the base plate. The slope of the lever ramp and / or the bearing rail can be implemented arbitrarily for individual requirements. For a linearly driven crossbar, for example by means of a screw drive with a screw axis as linear motion axis, it is advantageous for the bearing rail to be implemented flat.

[0013] Via the manipulation finger, the lever gives no manipulation path or a minimum manipulation path, for example for a minimum required axial pretension, in the pushed-in position of the crossbar and a maximum manipulation path in the pushed-out position. It should be noted that the main extent moves together with the lever, so that from the perspective of the coordinate system moving together with the lever, the crossbar describes a circular or arcuate trajectory, for example at a constant height of the lever ramp. Nevertheless, the crossbar is particularly preferably moved along a fixed screw axis, wherein the screw axis is fixed relative to a fixed component, for example the base plate of the hinge actuator.

[0014] 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 comprises a driven (axially movable) screw nut or a driven (axially movable) screw, and the driving (rotating) screw or the driving (rotating) screw nut is driven by a rotating, preferably electric, drive machine. The screw axis is preferably in a pivot plane of the lever, the hinge axis is oriented normal relative to the pivot plane, and the center axis is in the pivot plane. The pivot axis is preferably fixed. Alternatively, the pivot axis is pivotable, for example about the hinge axis.

[0015] It is proposed here that the hinge bearing mechanism is formed by one, preferably only one, convexly spherical protrusion and the (counteracting) bridge. Here, the convexly spherical protrusion is a planar component which, viewed in cross section, forms a contact point with the bridge, wherein the contact point moves on the convexly spherical protrusion with the pivoting movement. In embodiments in which a pure rotational movement of the lever is desired, the convexly spherical protrusion forms an arcuate trajectory in cross section with a constant radius relative to the (theoretical) hinge axis. For example, a contact line is formed by means of the convexly spherical protrusion with the bridge, which, like the contact point, behaves in the pivoting movement of the lever.

[0016] In a preferred embodiment, the only convexly spherical protrusion is arranged centrally in the lever with respect to the main extension and / or the crossbar, centrally between the two control fingers, preferably with respect to the mentioned middle axis. In an embodiment, the convexly spherical protrusion is formed by a plate component, wherein the convexity of the protrusion is formed by means of shaping, preferably cold shaping. Thus, the (plane) normal of the contact point between the protrusion and the bridge (in the central cross section of the lever or a corresponding cross section in the case of a symmetrical lever) is oriented perpendicular to the main extension and perpendicular to the hinge axis. It should be noted that not only the convexly spherical protrusion is arranged on the lever side, but alternatively also the bridge, and the respective further counteracting part of the hinge bearing mechanism is fixed, for example with respect to the base plate of the hinge actuator.

[0017] Furthermore, it is proposed in a preferred embodiment of the hinge actuator that the convexly spherical protrusion is also convexly spherical about the main extension.

[0018] In said embodiment, the only contact point between the convexly spherical protrusion and the (counteracting) bridge is formed in a (technically realizable or meaningful budget) by the fact that the convexly spherical protrusion is curved not only about the hinge axis (for the pivoting movement about the hinge axis), but also about the middle axis in the main extension. Thus, the lever itself can be tilted about the main extension and thus installation tolerances can be compensated.

[0019] In an alternative embodiment, not the protrusion but the bridge is convexly spherical about the main extension, wherein as a result the (only) contact point between the protrusion and the bridge is formed again, so that the lever can be tilted about the middle axis (in the case of matching installation conditions or manufacturing tolerances).

[0020] Furthermore, it is proposed in a preferred embodiment of the hinge actuator that the convexly spherical protrusion is connected to the lever, preferably formed in one piece with the lever, and the bridge is a fixed component.

[0021] It is now proposed that the convexly spherical protrusion is connected with the lever and that the bridge is preferably a simple, particularly preferably planar component. Particularly preferably, the protrusion is formed in one piece with the lever, for example from a single plate, wherein the protrusion is preferably formed simultaneously with the shaping of the lever. The bridge then forms a fixing component which is connected, for example by means of mounting screws, with the base plate or directly with the fixing component. Alternatively, the bridge is connected with the lever, for example in one piece, and the protrusion is the fixing component.

[0022] Furthermore, it is proposed in a preferred embodiment of the hinge actuator that the bridge and / or the convexly spherical protrusion is implemented and / or attached softly, such that the hinge axis is displaceable by means of the movement of the crossbar along the main extent between the pushed-out position and the pushed-in position.

[0023] It is now proposed that the bridge and / or the convexly spherical protrusion is implemented and / or attached softly, such that a (elastic) energy store is formed and the hinge axis is elastically displaceable by means of the movement of the crossbar. Thereby, an additional (elastically limited) degree of freedom is realized beyond the rigidity of the lever itself. Said degree of freedom can be used for a specific spring characteristic curve of the reciprocating movement between the pushed-in position and the pushed-out position of the hinge actuator.

[0024] Particularly preferably, the bridge is implemented as a band which extends long in the direction of the hinge axis, which band is bendable under normal or designed handling forces and transverse forces transversely to said extent and away from the hinge axis, such that the displacement of the hinge axis is outside a negligible range, for example in the range of 0.1 mm to 0.3 mm [one-tenth to one-third of a millimeter]. In this implementation of the bridge, preferably the lever is implemented (almost) rigidly together with the convexly spherical protrusion ideally taking into account the maximum (desired) load according to the design.

[0025] Furthermore, it is proposed in a preferred embodiment of the hinge actuator that the lever is positionally fixed relative to the hinge bearing mechanism by means of a spring device.

[0026] In said embodiment, a spring device is preferably provided by means of which the lever is positionally pivotably fixed relative to the hinge bearing mechanism. The spring device is for example implemented as a leaf spring or leaf spring stack, wherein the spring stiffness is small with respect to the movement of the pivoting movement of the lever and large with respect to the displacement of the lever, for example along the hinge axis and / or the main extent. The spring device is preferably also implemented as soft for the pivoting movement around the center axis, in the case of which the convexly spherical protrusion and the bridge form only one contact point, for example by means of the convexity around the center axis of the protrusion.

[0027] Furthermore, it is proposed in a preferred embodiment of the hinge actuator that the lever and the bridge, and preferably the spring device according to the above-described embodiments, form a pre-mountable structural unit and are preferably connected to one another by means of rivets.

[0028] It is proposed here that the lever and the bridge, and preferably the spring device according to the above-described embodiments, together form a pre-mountable structural unit, particularly preferably the entire hinge actuator, preferably without the associated drive motor, together with the crossbar including the linear transmission mechanism and, for example, the base plate form a pre-mountable structural unit. Particularly preferably, the lever and the spring device are connected to one another by means of rivets, and the bridge is connected to the lever via the spring device by means of a mounting bolt, in addition to being in contact with the protrusion in a force-transmitting manner, wherein the bridge forms the stationary component here.

[0029] According to a further aspect, a torque clutch having an axis of rotation for a powertrain is proposed, having at least the following components:

[0030] - a hinge actuator according to one of the above-described embodiments;

[0031] - a torque plate, preferably an axially compressible friction plate, which is axially operable by means of the hinge actuator in order to transmit torque; and

[0032] - an operating bearing between the torque plate and the hinge actuator,

[0033] wherein the hinge actuator is provided with at least one, preferably two, operating fingers which act on the operating bearing.

[0034] In the following, the axial direction, the radial direction or the circumferential direction and the corresponding terms are used without further explicit indication, with reference to the axis of rotation. The ordinal numbers used in the above and below description serve merely for unambiguous distinguishability, unless explicitly indicated to the contrary, and do not represent an order or a priority of the components described. An ordinal number greater than one does not entail the mandatory presence of a further such component.

[0035] The torque clutch presented here is, for example, a friction clutch or a form-fit clutch, such as, for example, a dog clutch or a so-called wedge clutch. By means of the torque clutch, torque is detachably transmittable about the axis of rotation. The torque clutch is a switching element for a connection device for transmitting or for detaching the transmission of torque, wherein a torque lamella assumes the task. The torque lamella is axially manipulable by means of a hinge actuator, which is embodied as a friction lamella, for example, is axially compressible, wherein the manipulation force, if necessary via a lever spring conversion, is proportional to the maximum torque desired to be transmittable. The hinge actuator is arranged in such a way that the hinge actuator or its hinge axis, neglecting the spring stiffness, is fixed, for example, by means of mounting bolts on a stationary component, and the shaft, for example the transmission input shaft, to which the torque clutch is connected, extends between the two manipulation fingers in an embodiment with two manipulation fingers. At least one manipulation finger acts on a rotating bearing ring preferably via a manipulation bearing, and the rotating bearing ring guides the manipulation force from the rotating bearing ring onto the torque lamella. By means of the manipulation bearing, the torque of the manipulation finger, and thus of the hinge actuator, is relieved. In the pushed-in position of the crossbar, no manipulation path or only a (for the desired minimum pretension) minimum manipulation path is applied to the manipulation bearing, and in the pushed-out position, a maximum manipulation path is applied to the manipulation bearing.

[0036] For the detachable transmittability of torque, the torque clutch has an axially manipulable torque lamella, for example, an axially compressible friction lamella. In the friction lamella, at least two friction plates and at least one clutch disc are provided. In a simple embodiment, between a first friction plate, i.e. an axially movable pressure plate, and a second friction plate, i.e. an axially preferably fixed counter-pressure plate, a single clutch disc is provided, and between them, for the frictionally engaging torque transmission, a compression force can be applied by means of a compression force. The compression force is generated or (servo) supported by a hinge actuator, wherein the output manipulation force is usually converted into a compression force by means of a lever spring. Due to the compression force, a friction force is derived via the planar friction pair between the frictionally predetermined area of the clutch disc and the (respective) corresponding counter-friction area of the respective friction plate, which, multiplied by the average radius of the friction surface formed, results in the transmittable torque. Multiplying the number of friction pairs, for example, results in the transmittable (maximum) total torque of the friction clutch. In the uncompressed state of the friction lamella, no torque or only a small drag torque is transmittable. The friction clutch is, for example, embodied as a double clutch with two friction lamellas, wherein the respective counter-pressure plates are preferably formed by a common central plate.

[0037] The hinge actuator presented here can be installed in a particularly small construction space and with low tension, wherein at the same time, the hinge actuator is less complex to implement and can be simply installed. In a double clutch, for example, two (for example, twisted around the axis of rotation from one another) hinge actuators presented here are provided.

[0038] According to a further aspect, a powertrain is proposed, having at least one drive machine with a machine shaft, at least one drive wheel and a torque clutch according to the above-described embodiments, 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.

[0039] The powertrain proposed here comprises a torque clutch according to the above-described embodiments, for example a friction clutch, wherein by means of the actuating force or pressing force exerted on the torque lamella, for example the friction lamella, by the hinge actuator according to the above-described embodiments, the torque clutch is switchably, i.e. separably, enabled for torque transmission from the drive machine or its machine shaft to the at least one drive wheel, for example to the drive wheels in a motor vehicle. This by no means excludes a reverse torque transmission from the drive wheel to the machine shaft, for example for engine braking in a motor vehicle, in order to slow down the motor vehicle and / or for recovering brake 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 the at least one drive wheel in a torque-proof manner, at least indirectly, for example via a transmission.

[0040] The proposed torque clutch is particularly advantageous for powertrains in which, for the hinge actuator, little construction space is available and particularly high actuating forces are required. Particularly in the case of a biconvexity of the protrusion of the lever's hinge bearing around the central axis, despite the low construction space requirement, an almost tension-free installation of the hinge actuator is possible even with large installation tolerances and / or manufacturing tolerances.

[0041] According to a further aspect, a motor vehicle is proposed, having at least one drive wheel, which can be driven by means of a powertrain according to the above-described embodiments.

[0042] In a motor vehicle in particular, the construction space is particularly small due to the increasing number of components, and therefore it is particularly advantageous to use a powertrain with smaller construction dimensions. With the so-called down-sizing of the drive machines, which is desired at the same time as a reduction in the operating rotational speed, the intensity of the disturbing torque vibrations increases, and also the requirement for actuating forces increases with increasing torque or with a reduction in the torque clutch. Therefore, the challenge is proposed of providing sufficient actuating force by means of a hinge actuator while at the same time keeping the component costs low and the available construction space small.

[0043] The problem is exacerbated in passenger cars of the small car class according to the European classification. The equipment used in passenger cars of the small car class is not significantly reduced in relation to passenger cars of the larger vehicle classes. The construction space available in small cars is therefore significantly smaller. The proposed torque clutch is particularly advantageous for a powertrain in which the construction space available for the hinge actuator is small and a particularly high actuating force is preferably required. An almost tension-free mounting of the hinge actuator is possible even with large installation tolerances and / or manufacturing tolerances, especially in the case of a biconvexity of the protrusion of the lever's hinge bearing around the central axis, despite the low construction space requirement.

[0044] Passenger cars are assigned a vehicle class according to, for example, size, price, weight and power, wherein the definitions are continuously changing according to market requirements. In the US market, vehicles of the small car (Kleinwagen) and the smallest car (Kleinstwagen) class according to the European classification are assigned to the class of the subcompact car (Subcompact Car), while in the British market, this corresponds to the class of the supermini (Supermini) or the class of the city car (City Car). The Volkswagen up! or the Renault Twingo, for example, is a smallest car class. The Alfa Romeo MiTo, the Volkswagen Polo, the Ford Ka+ or the Renault Clio, for example, is a small car class. BRIEF DESCRIPTION OF DRAWINGS

[0045] The above invention is explained in detail below in the relevant technical background with reference to the relevant drawings showing preferred design solutions. The invention is not limited in any way by the purely schematic drawings, wherein it should be noted that the drawings are not to scale and are not suitable for defining the size proportions. The drawings show:

[0046] Figure 1 a side sectional view of the hinge actuator;

[0047] Figure 2 a perspective sectional view of the hinge actuator;

[0048] Figure 3 a sectional view of the hinge actuator from the side of the engine connection;

[0049] Figure 4 a perspective top view of the lever; and

[0050] Figure 5 a powertrain in a motor vehicle with a hinge actuator. DETAILED DESCRIPTION

[0051] In Figure 1A side sectional view of the hinge actuator 1 is shown in Fig. 1. The hinge actuator 1 has a lever 6 with a main extension 7. The lever has two operating fingers 3, 4 (see Fig. 2). Of the two operating fingers, the right-hand operating finger 4 is visible here. In the embodiment shown, the hinge actuator 1 is embodied with a base plate 26, on which there is at least one rolling track for each one of the support rollers 27 (shown here schematically in the foreground). The support rollers 27 shown are shown in detail in the pushed-in position 12 (on the right according to the drawing) for the implementation of the support and in the pushed-out position 11 as a broken circular line. Figure 4 ). Of the two operating fingers, the right-hand operating finger 4 is visible here. In the embodiment shown, the hinge actuator 1 is embodied with a base plate 26, on which there is at least one rolling track for each one of the support rollers 27 (shown here schematically in the foreground). The support rollers 27 shown are shown in detail in the pushed-in position 12 (on the right according to the drawing) for the implementation of the support and in the pushed-out position 11 as a broken circular line.

[0052] The support rollers 27 are an integral part of the crossbar 10. The crossbar can be moved along the main extension 7 by means of a screw drive 28 comprising a (rigid) screw 29 and a screw nut 30 (in the slide of the crossbar 10). Here, the screw drive 28 is embodied as a ball screw drive. The screw 29 has a motor connection 31 on the end side (on the right according to the drawing), on which a rotary, preferably electric, drive machine 21 can be connected. The translational movement of the crossbar 10 or of the support rollers 27, which is supported by a support rail 32, is introduced into the lever 6 by means of a lever rail 33, thereby causing a pivoting movement of the lever 6 or of the main extension 7 about the hinge axis 9. By this, a manipulation force 5 for the torque clutch 2, for example, having a high transmission ratio is generated. Here, the pivoting movement is ensured by means of a hinge bearing 8 formed by a convex, ball-like projection 13 and a counteracting bridge 14. The convexity of the projection 13, which is clearly visible in the sectional view, around the (theoretical) hinge axis 9 causes a defined pivotability, for example, around the drawn hinge axis 9. Here, the convex, ball-like projection 13 and the operating fingers 3, 4 are made in one piece with the lever 6, for example, from a common sheet metal part, for example, by means of cold forming. The bridge 14 is a separate component, which is fixed with a fixing component in the powertrain 18 of the motor vehicle 25, for example, a transmission housing, by means of a (here two) mounting bolt 34. In order to fix the position of the lever 6 relative to the bridge 14, a spring device 15 is connected with the lever 6 and with the bridge 14, wherein a rivet 16 is inserted here on the lever side and the mounting bolt 34 is used together on the bridge side.

[0053] In Figure 2 , a perspective sectional view of the hinge actuator 1 according to the embodiment of Figure 1 is shown. Here, it can be clearly seen how the lever 6 is positionally fixed with the bridge 14 (and the base plate 26) by means of the spring device 15.

[0054] In Figure 3 , a perspective sectional view of the hinge actuator 1 according to the embodiment of Figure 1 and Figure 2A cross-sectional view of the hinge actuator 1 according to the embodiment. Here, the convexity of the protrusion 13 around the (theoretically) compensating axis 35 can be clearly seen, such that only point contact is formed between the (double)convex spherical protrusion 13 and the bridge-like member 14. Therefore, the plane of the lever 6 or the main extension 7 can be flipped around the compensating axis 35. The (small) stopping force of the spring device 15 is resisted by the operating fingers 3, 4 (see... Figure 4 Conversely, in the ideal mounting configuration, the lever 6 is flipped relative to the ideal (or actual) hinge axis 9, so that even if the lever 6 is twisted and in contact, the lever 6 flips around the compensation axis 35, thereby releasing the torque of the lever 6. Thus, the hinge actuator 1 is not tensioned even under installation and / or manufacturing tolerances.

[0055] exist Figure 4 The diagram shows a perspective view of a lever 6 for the hinge actuator 1. The lever 6 has a left actuating finger 3 and a right actuating finger 4. By means of these actuating fingers, an actuating force 5 is applied to the torque plate 19 of the torque clutch 2. The left and right sides are selected here according to the diagram, and... Figures 1 to 3 This is generally described in the text. Additionally, there is a hole at which the spring device 15 is secured by a rivet 16 (see [link]). Figure 2 The position is fixed. The lever 6 has a (unique) central convex spherical protrusion 13 at the end opposite to the operating fingers 3 and 4.

[0056] exist Figure 5 The powertrain 18 is schematically shown from above (optionally located before the driver's compartment 36 and optionally in a transverse configuration, i.e., having an engine axis 37 transverse to the longitudinal axis 38 of the vehicle 25). The left drive wheel 23 and the right drive wheel 24 are here (optionally) driven by the powertrain 18. The powertrain 18 includes a drive motor 21 (shown here as a three-cylinder internal combustion engine) and a torque clutch 2 coupled to the drive motor 21 via a shaft 22. Torque can be separably transmitted about a rotation axis 17 or an equivalent engine axis 37 by means of the torque clutch 2. For separability, a torque plate 19 is provided, which is exemplarily implemented here as a friction plate having a pressure plate 39, a counter-pressure plate 40 connected to the shaft 22 by means of a clutch cover 41 in a torque-transmitting manner, and a friction disc 42 axially disposed between the pressure plate and the counter-pressure plate, the friction disc being connected to the drive wheels 23, 24 via a transmission (schematically shown in dashed lines) in a torque-transmitting manner. The operating force 5 of the hinge actuator 1 can be transmitted to the torque disc 19 of the torque clutch 2 via the lever spring 43 supported on the clutch cover 41 and the operating bearing 20, so that the torque disc 19 is separable (normally closed) or separable (normally open).

[0057] The hinge actuator presented here can be used in particularly narrow construction spaces and at the same time is less complex in its construction.

[0058] List of reference signs

[0059] 1 hinge actuator

[0060] 2 torque clutch

[0061] 3 left-hand operating finger

[0062] 4 right-hand operating finger

[0063] 5 operating force

[0064] 6 lever

[0065] 7 main extension

[0066] 8 hinge bearing

[0067] 9 hinge axis

[0068] 10 crossbar

[0069] 11 pushed-out position

[0070] 12 pushed-in position

[0071] 13 convex ball-shaped projection

[0072] 14 bridge

[0073] 15 spring device

[0074] 16 rivet

[0075] 17 axis of rotation

[0076] 18 power train

[0077] 19 torque plate

[0078] 20 operating bearing

[0079] 21 drive machine

[0080] 22 machine shaft

[0081] 23 left-hand drive wheel

[0082] 24 right-hand drive wheel

[0083] 25 motor vehicle

[0084] 26 base plate

[0085] 27 support roller

[0086] 28 screw drive

[0087] 29 screw

[0088] 30 screw nut

[0089] 31 engine connection

[0090] 32 support rail

[0091] 33 lever rail

[0092] 34 mounting bolt

[0093] 35 compensation axis

[0094] 36 driver's cabin

[0095] 37 engine axis

[0096] 38 longitudinal axis

[0097] 39 pressure plate

[0098] 40 counter-pressure plate

[0099] 41 clutch cover

[0100] 42 friction disc

[0101] 43 lever spring

Claims

1. A hinge actuator (1) for a torque clutch (2), said hinge actuator having at least the following components: - At least one control finger (3, 4) for transmitting the control path (5) to the torque clutch (2); - A lever (6) having a main extension (7), the lever being connected to the operating fingers (3, 4); - A hinge support mechanism (8) having a hinge axis (9), the lever (6) being pivotable about the hinge axis; and - A crossbar (10) that contacts the lever (6) in a force-transmitting manner, wherein the crossbar (10) is movable along the main extension (7) between an extended position (11) and an extended position (12), and wherein the lever (6) can be pivoted by means of the crossbar (10) for manipulation. Its features are, The hinge support mechanism (8) is formed by a bridge-shaped member (14) and a convex ball-shaped protrusion (13) surrounding the hinge axis (9), such that only point contact is formed between the convex ball-shaped protrusion (13) and the bridge-shaped member (14), wherein the convex ball-shaped protrusion (13) abuts against the bridge-shaped member (14) in a force-transmitting manner.

2. The hinge actuator (1) according to claim 1, wherein The convex spherical protrusion (13) is also convex spherically shaped around the main extension (7).

3. The hinge actuator (1) according to claim 1 or 2, wherein The convex spherical protrusion (13) is connected to the lever (6), and the bridge-shaped member (14) is a fixing member.

4. The hinge actuator (1) according to claim 1 or 2, wherein... The bridge-shaped member (14) and / or the convex spherical protrusion (13) are softly implemented and / or attached such that the hinge axis (9) can be displaced by means of the movement of the crossbar (10) along the main extension (7) between the push-out position (11) and the push-in position (12).

5. The hinge actuator (1) according to claim 1 or 2, wherein... The lever (6) is fixed in position relative to the hinge support mechanism (8) by means of a spring device (15).

6. The hinge actuator (1) according to claim 1 or 2, wherein The lever (6) and the bridge (14) form a pre-installable structural unit and are connected to each other by means of rivets (16).

7. A torque clutch (2) for a power transmission system (18) having a rotation axis (17), said torque clutch having at least the following components: -The hinge actuator (1) according to any one of the preceding claims; - Torque stack (19), the torque stack being axially manipulated by means of the hinge actuator (1) to transmit torque; and -The operating bearing (20) between the torque plate (19) and the hinge actuator (1), The hinge actuator (1) is provided with at least one actuating finger (3, 4) acting on the actuating bearing (20).

8. A power transmission system (18) comprising: The device comprises at least one drive motor (21) having a shaft (22), at least one drive wheel (23, 24), and a torque clutch (2) according to claim 7, wherein the shaft (22) is adjustablely connected to the at least one drive wheel (23, 24) by means of the torque clutch (2) in a manner that transmits torque.

9. A motor vehicle (25), comprising: At least one drive wheel (23, 24) is capable of being driven by means of the power transmission system (18) according to claim 8.

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