Hinge actuator for a torque clutch

Abstract

The invention relates to a 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 path (5) to the torque clutch (2); a lever (6) having a main extension (7), which is connected to the actuating finger (3, 4); a hinge bearing (8) for pivotably bearing the lever (6); and a crossbar (13) which is in force-transmitting contact with the lever (6), wherein the crossbar (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 movement of the crossbar (13), the lever (6) can be pivoted in order to transmit the actuating path (5). The hinge actuator (1) is characterized, inter alia, in that the lever (6), together with the actuating finger (3, 4), is the only spring element which determines the lever stiffness of the lever (6). By means of the hinge actuator presented here, it is possible to save construction space and at the same time to significantly reduce costs.

Description

TECHNICAL FIELD

[0001] The invention relates to a hinge actuator for a torque clutch, to a torque clutch 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, hinge actuators are known for actuating a torque clutch, for example for a motor vehicle, for example a friction clutch for a powertrain. Such a hinge actuator is shown, for example, in DE 10 2012 220 436 A1. The problem often arises that the construction space available for the hinge actuator, in particular the construction space transverse to the main extension of the hinge actuator, is extremely limited. At the same time, however, cost pressure, in particular in the automotive industry, is high, not only in terms of part costs but also in terms of installation costs. SUMMARY

[0003] Against this background, the invention is based on the object of at least partially overcoming the disadvantages known from the prior art. The features according to the invention emerge in the independent claims, advantageous design embodiments thereof being shown in the dependent claims. The features of the claims can be combined in any technically meaningful manner and method, it being possible for this to also take into account the explanations from the following description and the features from the drawings, including supplementary design embodiments of the invention.

[0004] The invention relates to a hinge actuator for a torque clutch, 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, which lever is connected to the actuating finger;

[0007] a hinge bearing for pivotably bearing the lever; and

[0008] a crossbar in force-transmitting contact with the lever, wherein the crossbar is movable along the main extension between a disengaged position and an engaged position, and wherein, by means of the movement of the crossbar, the lever is pivotable for transmitting the actuating path.

[0009] The hinge actuator is particularly characterized in that the lever, together with the actuating finger, is the only spring element which determines the lever stiffness of the lever.

[0010] The ordinal numbers used in the preceding and following description are used only for a one-to-one distinguishability and do not describe an order or sequence of the components mentioned, unless expressly indicated otherwise. Ordinal numbers greater than one do not necessarily entail that there are several components of the same kind.

[0011] Furthermore, the terms left and right for the spatial description are arbitrarily chosen and can also be used (uniformly) interchangeably. They serve only for a good overview, especially with regard to a paired arrangement of components.

[0012] When using the axial direction, radial direction or circumferential direction and the corresponding terms without expressly stating otherwise, reference is made in the following to the actuation axis of the hinge actuator (for example the rotation axis of the torque clutch which transmits torque about said rotation axis). Furthermore, reference is made to the main extension of the lever in connection with the hinge actuator, wherein the lever can be pivoted about a pivot axis of the articulated bearing, which is oriented transversely (in the ideal case 90°) to the main extension. Said pivot axis can be displaceable during the pivoting movement of the lever and / or not in the center of the component being supported, for example not in line with the central axis of the bolt. The orientation of the actuation path can be understood approximately as a third spatial direction, wherein the actuation path is oriented transversely (in the ideal case 90°) to the pivot axis and during the pivoting movement of the lever is oriented transversely to the main extension in a manner variable corresponding to the pivoting angle of the actuation path. The lever stiffness results from the bending of the lever with a deflection of the lever in the direction of the actuation path relative to the main extension, wherein the effective length of the lever is changed by means of the actuation of the crossbar, more precisely shortened in the case of an actuation path increase. This means that the effective length of the lever is greatest when the crossbar is in the engagement position and the effective length of the lever is smallest when the crossbar is in the disengagement position. This is explained in more detail further below. The lever has a construction extension (parallel to the pivot axis) between the left and right in addition to its main extension. The actuation path is arranged transversely relative to said construction face. A lateral movement of the lever, i.e. a movement to the left or to the right (if necessary with play) is prevented.

[0013] The hinge actuator presented here is designed, for example, for an axially operable 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 shaft which rotates about its axis of rotation. The hinge actuator comprises at least one, preferably two, operating fingers, wherein the two operating fingers, for example when used in a torque clutch, act on an operating bearing. The operating bearing is designed for transmitting an operating path, for example onto the torque clutch. The operating fingers are connected to a lever, preferably in one piece, wherein the operating fingers are arranged in an elongation of the main extension of the lever. The main extension corresponds, in a simplified model, to the lever, wherein the actual 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 to have its greatest extension direction in the direction of the center line of its main extension. The main extension and the pivot axis form a plane, and the operating face of the operating fingers lies in said plane. The center axis runs in said plane of the main extension, said center axis running centrally between the operating fingers in the case of two operating fingers and preferably intersecting the pivot axis perpendicularly. It is advantageous for various applications for the lever to be constructed cost- suitably and space-savingly, so that the lever is particularly advantageous in this respect as a sheet metal component with reinforcing ribs and / or crimping. Just in this embodiment consisting of sheet metal, the theoretical plane of the main extension does not run completely through the actual component of the lever.

[0014] The lever is pivotably supported about the pivot axis by means of a hinge bearing, so that the lever is thus pivoted (about the pivot axis) to describe an operating path by means of the at least one operating finger. Furthermore, a crossbar is provided in said hinge actuator. The crossbar is in contact with the lever in such a way that the lever is pivoted about the pivot axis by means of the crossbar along the movement of the main extension. The crossbar, preferably formed by a single or a plurality of, preferably two, carrier rollers for low-friction transmission of forces to the lever, can be moved between a disengaged position and an engaged position. The crossbar together with the lever forms a ramp-like operating assembly. For example, the operating assembly is formed by means of a lever ramp on the side of the crossbar (on the back side of the lever) and a bearing track at the side opposite the crossbar, for example at the base plate. The slope of the lever ramp and / or of the bearing track can be arbitrarily composed for individual requirements. For a crossbar which is driven linearly, for example by means of a screw drive with a screw axis as linear movement axis, it is advantageous for the bearing track to be composed flat.

[0015] At this point it is noted that the hinge actuator manipulates via a crossbar (as described above), wherein for example a rotating electric drive machine is connected to a screw drive, which electric drive machine causes a relative movement of the ramp-like manipulation assembly of the crossbar and forces a movement of the at least one manipulation finger along the manipulation path by means of the ramp-like connection to the lever. In a preferred embodiment the manipulation force (caused by the movement of the crossbar between the engagement position and the disengagement position at the manipulation finger) is (approximately) constant over the entire manipulation path (due to the installation situation).

[0016] The lever provides no manipulation stroke or a minimum manipulation stroke in the engagement position of the crossbar (for example for a minimum required axial pretension) and provides a maximum manipulation stroke via the manipulation finger in the disengagement position of the crossbar. It is noted that the main extension moves with the lever, so that from the point of view of the coordinate system moving with the lever the crossbar describes a circular or arcuate path in the case of a constant slope of the lever ramp, for example. The crossbar is still preferably moved along a rigid screw axis, wherein the screw axis is fixed to a fixed component, for example a base plate of the hinge actuator.

[0017] The crossbar is driven as already described above for example by a screw drive, for example a ball screw drive, with a screw axis, wherein the crossbar itself then consists of a slider, which includes 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 thus preferably oriented at 90° transversely to the pivot axis and at a relative ramp angle with respect to the main extension of the lever.

[0018] It is proposed here that no additional spring element is formed which determines the lever stiffness of the lever. The lever stiffness of the lever is the determined magnitude of the stiffness of the hinge actuator which acts in the actuation. The influence of other stiffnesses, for example the stiffness in the connection between the hinge bearing or a separate component, is much smaller, preferably negligible, in relation to this. Rather, the length of the lever or the lever itself, which acts depending on the position of the crossbar, forms a component which determines the lever stiffness simply depending on the type of the crossbar, for example a cantilever beam. In a preferred embodiment, at least one actuation finger is part of the crossbar and thus has the lever stiffness partially. In another embodiment, the lever is almost ideally stiff (in consideration of the applied load) apart from the at least one actuation finger, i.e. its bending deformation is negligible, and the lever stiffness is determined exclusively by the at least one actuation finger. In yet another embodiment, the at least one actuation finger is almost ideally stiff (in consideration of the applied load). In embodiments with a lever (or at least a part of the lever) as a spring element, the (bearing-side) part of the lever is only negligibly deformed between the hinge bearing and the crossbar, and only the (finger-side) part of the lever forms a spring element between the crossbar and the actuation finger (more precisely between the crossbar and the actuation face of the actuation finger), i.e. depending on the type of a cantilever beam. In another embodiment, the (bearing-side) part of the lever has the lever stiffness partially between the crossbar and the hinge actuator, so that the spring element corresponds to a 3-point supported crossbar, wherein the hinge bearing and the actuation face of the actuation finger correspond to the two supports and the crossbar corresponds to the test head, similar to a three-point bending test.

[0019] In the case of two actuation fingers, a twisting of the lever (for example around the main extension) can occur due to tolerances, for example up to 0.2 mm [two tenths of a millimeter] in the direction of the actuation path between the actuation fingers in the (fully) relaxed position and / or in the engaged position (minimum actuation stroke). The first actuation finger then engages in a force-transmitting manner first alone or (compared to the second actuation finger) more strongly along the actuation path and the second actuation finger follows subsequently.

[0020] By eliminating the separate (additional) spring element, not only costs can be reduced, but also construction space can be saved.

[0021] Furthermore, in one advantageous embodiment of the hinge actuator, the two actuation fingers are arranged transversely to the main extension of the lever at a finger spacing, and the hinge actuator has a maximum transverse dimension parallel to the finger spacing, wherein the maximum transverse dimension is less than 4 times the finger spacing, preferably less than 2.5 times.

[0022] In this embodiment, the width of the hinge actuator is significantly reduced compared to previously known embodiments. The finger spacing, i.e. the lateral dimension of the free space generated between two actuating fingers, is determined, for example, by the dimensions of the components to be actuated with axial force, for example by the shaft diameter in the case of an actuating bearing of a torque clutch, and / or by the actuating force required. The maximum lateral dimension of the hinge actuator is the maximum extension between the left and right side and / or the extension in which the conventional hinge actuator has its maximum extension between the left and right side, which has thus hitherto determined the construction space. In a ratio of just less than 4 times [four times], the lever is more rigid or can be made with a smaller sheet thickness of metal and thus more cost- advantageously. In a ratio of less than 2.5 times, the construction space can be significantly saved. In one particularly preferred embodiment, the ratio is, for example, 2.2 times the finger spacing. The maximum lateral dimension is then formed in the hinge bearing. The component determining the construction space is then, for example, a fastening element for mounting the hinge actuator, for example in a transmission of a motor vehicle.

[0023] Furthermore, in one preferred embodiment of the hinge actuator, it is proposed that the hinge actuator has two pegs with a peg axis and each one mating peg receptacle, wherein the peg receptacles are formed in a bearing section of the lever which is preferably angled at 90° with respect to the main extension and the peg axis, wherein preferably in the disengaged position the lever stiffness of the lever lies between 4 kN / mm and 5 kN / mm.

[0024] In this embodiment, the peg accommodation is formed in an angled bearing section of the lever, for example in a (preferably cold) formed tab. Preferably, the angled bearing section is arranged laterally outside the lever. The respective peg extends through the cooperating peg accommodation. The peg is in turn accommodated in a corresponding bearing accommodation and is indirectly or directly mountable by means of the bearing accommodation (together with the entire hinge actuator). In one embodiment, the peg is rotationally fixed. In one embodiment, the peg is supported such that it rotates together in the pivoting movement of the lever. In one embodiment, a joint movement of the peg is permitted, but not necessary. In one preferred embodiment, the peg axis (then of both pegs in unison) corresponds to the pivot axis of the lever. In one embodiment, the pivot axis is oriented parallel to the peg axis (then of both pegs in unison or parallel). In yet another embodiment, the pivot axis is obliquely oriented relative to at least one peg axis. The position of the pivot axis is determined by the shape of the respective pair of peg accommodations and (bearing) outer faces of the pegs, such that, for example, in a unison embodiment of said pair, the pivot axis coincides with the peg axis. If one of the shapes of the pair deviates from the concentricity and / or the peg axes of the two pegs do not coincide, the pivot axis deviates from the peg axis. For example, the pivot axis is then not fixed via the pivot axis of the lever, but migrates. In one preferred embodiment, this migration movement of the pivot axis is within the permissible tolerances and can be approximately described as fixed, i.e. within technical considerations.

[0025] In one preferred embodiment, a relatively high lever stiffness is achieved, preferably due to the stiffening effect by means of the formed tab with peg accommodation. In one particularly preferred embodiment, in the detached position of the crossbar, i.e. when the effective length of the lever is shortened or when the part of the lever on the finger side is shortened, the lever stiffness of the lever, i.e. the (at least approximately) manipulation-effective stiffness of the hinge actuator, is between 4 kN / mm [four thousand Newton per millimeter] and 5 kN / mm, for example approximately 4.5 kN / mm. By this, the customer requirement for a relatively high lever stiffness is met.

[0026] Furthermore, in one advantageous embodiment of the hinge actuator, it is proposed that the hinge bearing has two pegs with a peg axis and each one cooperating peg accommodation, wherein the peg accommodations are formed by bearing tabs of the lever, respectively, wherein the bearing tabs extend away from the manipulation finger along the main extension, wherein preferably in the detached position, the lever stiffness of the lever is between 1 kN / mm and 2 kN / mm.

[0027] In this embodiment, the same and different things apply as in the previously mentioned embodiments of the hinge support as to the peg and its support accommodation and as to the resulting pivot axis. In contrast to the embodiment with angled support sections, here the peg accommodation is formed by a support tab which extends in the lever's extension to the hinge support. In one embodiment, the support tab, for example substantially in the direction of the main extension and / or substantially in the direction of the screw axis of the crossbar, can be introduced into the hinge support such that the peg accommodation of the respective support tab is arranged behind the respective peg (i.e. with respect to the handling path resulting from the movement of the crossbar from the engagement position up to the disengagement position), wherein preferably the peg is already installed. The lever is prevented from automatic disassembly by means of the shape of at least one of the peg accommodations and / or the installation orientation deviating from the operating situation (i.e. the orientation of the lever between the engagement position and the disengagement position).

[0028] The support tab is preferably designed such that the lever stiffness of the lever is reduced compared to the embodiment with angled support sections. In one particularly preferred embodiment, the lever stiffness of the lever, i.e. the (at least almost) handling-effective stiffness of the hinge actuator, is between 1 kN / mm [one thousand Newton per millimeter] and 2 kN / mm, for example approximately 1.7 kN / mm, in the disengagement position, i.e. when the effective length of the lever is shortened or when the part of the lever pointing towards the side is shortened. By this, the customer requirements for a relatively small lever stiffness are met.

[0029] Furthermore, it is proposed in one advantageous embodiment of the hinge actuator that the support tab extends between the remaining lever and the peg in an arcuate, preferably S-shaped, manner with respect to a cross section with the peg axis as a normal.

[0030] In the described embodiment of the hinge actuator, the support tab already described above is shaped by the lever being very flat in the area of the movement path of the crossbar, more precisely towards or away from the crossbar. The cross section is thus in a plane with respect to which the peg axis is (in ideal observation) oriented normally. The cross section describes an arcuate, preferably S-shaped, shape between the remaining lever and the hinge support. By this, a soft engagement of the lever at the hinge support is achieved due to the elongation of the support tab compared to a straight or shortest connection. Alternatively or additionally, a construction space on the back side of the lever in the direction of the handling path can be saved in that, with the arcuate shape of the support tab towards the crossbar, the hinge support can be arranged more deeply, i.e. closer to the crossbar, in the direction of the handling path. The construction space corresponds in various applications to an axial construction space in applications in shafts which transmit torque about a rotational axis.

[0031] Furthermore, it is proposed in one preferred embodiment of the hinge actuator that the lever is laterally fixed by means of the hinge bearing, preferably by means of at least one of the pegs according to the embodiments described above.

[0032] In this embodiment, the lever is laterally, i.e. to the left and to the right, fixed by means of the hinge bearing without additional components. For example, lateral stops are formed to the right and / or to the left, for example by means of a shoulder of the bearing element and / or by means of a wall of the bearing receptacle. In one preferred embodiment, the lateral fixing is formed by means of at least one of the pegs according to one of the embodiments described above, preferably by means of two pegs. For this, the pegs have, for example, at least one shoulder (diameter expansion), preferably two shoulders, wherein preferably the shoulders are in force-transmitting contact, for example with play, with the respective peg receptacle and with the respective bearing receptacle. In another embodiment, at least one of the pegs is fixed by means of a screw, preferably a mounting screw, wherein the screw extends through or into a mating slot or hole of the associated screw. The lateral fixing on both sides is particularly advantageous in a flexible, in particular torsionally flexible, embodiment of the lever around the main extension. By means of the embodiments proposed here, a simple construction and / or a small space requirement can be achieved. It is pointed out that the lever is preferably only elastically torsionable in a design-compliant load.

[0033] Furthermore, it is proposed in one 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.

[0034] In this embodiment, the lever is divided into two partial levers, for example associated with each of the two actuating fingers. By providing two partial levers, which are connected to one another only by means of at least one lever bridge, preferably in one piece, a particularly small (around the main extension) torsional stiffness is achieved. By this, a large tolerance with respect to the actuating surfaces of the at least one actuating finger is allowed, since angular deviations or misalignments of the actuating surfaces of the two actuating fingers with respect to the mating surfaces to be actuated, for example the actuating bearings of a torque clutch, can be compensated with small resistance. This (small) resistance is determined, for example, by (small) transverse forces in the hinge bearings and / or (small) force differences at the two separate actuating surfaces of the two actuating fingers and / or at the crossbar, which preferably (on the left and on the right) comprises two carrier rollers. In one embodiment with a bent support section, preferably, a single lever bridge is provided, which is arranged at a large distance from the at least one actuating finger (compared to the embodiments described below), so that a sufficiently small torsional stiffness is achieved in the actuating finger, while the lever stiffness is relatively large (due to the bent support section). In one embodiment with a support tab, preferably, two lever bridges are provided, wherein the (first) lever bridge (compared to the previously mentioned embodiment with a single lever bridge) is arranged close to the at least one actuating finger, and the further (second) lever bridge is arranged close to the hinge bearing, so that in the actuating finger and in the hinge bearing, despite the relatively small lever stiffness (due to the support tab), a too small torsional stiffness is not achieved.

[0035] According to another aspect, a torque clutch with a rotational axis for a powertrain is proposed, having at least the following components:

[0036] - a hinge actuator according to the embodiments described above;

[0037] - a torque group, preferably an axially compressible friction group, which is axially actuable by means of the hinge actuator, for the adjustable transmission of torque; and

[0038] - an actuating bearing between the torque group and the actuating finger of the hinge actuator,

[0039] whereby, by means of the crossbar of the hinge actuator, an actuating movement can be transmitted via the actuating bearing onto the torque group.

[0040] 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 can be transmitted detachably about an axis of rotation. The torque clutch is a switching element, for example, for transmitting or detaching the transmission of torque, wherein a torque group takes on the task. The torque group is axially manipulable by means of a hinge actuator, is configured, for example, axially compressible as a friction group, wherein the manipulation force applied by the hinge actuator or the current manipulation stroke resulting from the position set between the disengaged position and the engaged position of the crossbar, if necessary via a lever spring drive, is proportional to the desired maximum torque that can be transmitted. The hinge actuator is arranged in such a way that the hinge actuator or its pivot axis (under the condition of neglecting the spring stiffness and in the case of a desired play movement of the manipulation pivot axis, if necessary) is fixed, for example, by means of a mounting screw at a fixed component, and the shaft, for example the transmission input shaft, to which the torque clutch is connected, stretches between the manipulation fingers (in embodiments with two manipulation fingers). At least one manipulation finger acts on a rotating axial bearing ring via a manipulation bearing and the rotating axial bearing ring conducts the manipulation force from the rotating axial bearing ring onto the torque group. By means of the manipulation bearing, the manipulation finger and thus the hinge actuator are torque-selective. In the engaged position of the crossbar, no manipulation path or only a minimum manipulation path (for example for a desired minimum pretensioning) is applied to the manipulation bearing, and in the disengaged position of the crossbar, a maximum manipulation path (for example for a maximum compression of the friction group) is applied to the manipulation bearing.

[0041] The torque clutch has an axially operable torque group for the (adjustably) detachable torque transferability, for example an axially compressible friction group. The adjustability of the torque transferability also includes here the switching, i.e. the detachment and the (complete) connection, as in a dog clutch, as well as the stepless (or for example incrementally due to the actuation) adjustment of the maximum transferable torque quantity in a friction clutch, for example for the elimination of torque surpluses. In a friction group, usually at least two friction plates and at least one clutch disc are provided. In a simple embodiment, the only clutch disc is arranged between a first friction plate, i.e. an axially movable compression plate, and a second friction plate, preferably an axially fastened counter-plate, and can be compressed between them for the frictionally engaging torque transfer by means of a compression force. The compression force is generated or (servo-) supported by a hinge actuator, wherein the provided actuation force is usually converted into a compression force by means of a lever spring. Due to the compression force, a friction force is achieved between a frictionally predetermined area of the clutch disc and the (respective) mating friction area of the respective friction plate via the planar friction pair, which, multiplied by the average radius of the friction surface formed, results in the transferable torque. Multiplying this by the number of friction pairs, the (maximum) total torque transferable by the friction clutch is approximately achieved. In the uncompressed state of the friction group, no torque or only a reliably small drag torque is transferable. The friction clutch is for example constructed as a dual clutch with two friction groups, wherein preferably the respective counter-plate is formed by a common central plate. It is noted here that the hinge actuator is actuated via a crossbar, wherein for example a rotary electric drive machine is connected to a screw drive, which linearly moves a slider-like crossbar and forces at least one actuation finger along an actuation path by means of a ramp-like connection to the lever. In a preferred embodiment, the actuation force at the actuation finger is (almost) constant over the entire actuation path resulting from the movement of the crossbar between the engagement position and the detachment position.

[0042] The hinge actuator presented here can be installed with particularly small installation space and low tension, wherein at the same time the hinge actuator is less complex to construct and can be simply installed. In a dual clutch, for example two (for example rotating around a rotation axis relative to each other) of the hinge actuators presented here are provided.

[0043] According to another aspect, a powertrain is presented 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 adjustably connected to the at least one consumer in a torque transferable manner by means of the torque clutch.

[0044] The powertrain presented here comprises a torque clutch according to the embodiments described above, for example a friction clutch, wherein the torque clutch switchably, i.e. releasably, enables the transmission of torque from a drive machine or its machine shaft to at least one consumer, for example to a propulsion wheel in a motor vehicle, by means of a manipulation force or a compression force applied to the torque group, for example the friction group, by the hinge actuator output according to the embodiments described above. This in no way excludes the opposite torque transmission from the consumer to the machine shaft, for example in a motor vehicle in order to use the engine brake for motor vehicle deceleration and / or to recover 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 in a torque- fixed manner to the machine shaft and the output side is connected in a torque-fixed manner, at least indirectly, for example via a transmission, to at least one consumer.

[0045] The torque clutch presented here is particularly advantageous for a powertrain in which the structural space available for the hinge actuator is small and, preferably, high tolerances in at least one manipulation finger are necessary or desired for cost reasons. The tolerances can be compensated without high resistance by the low torsional stiffness in the hinge actuator presented here.

[0046] According to a further aspect, a motor vehicle is presented having at least one propulsion wheel, which can be driven by means of a powertrain according to the embodiments described above.

[0047] The structural space is particularly small in motor vehicles due to the increasing number of components, so that it is particularly advantageous to use a powertrain of small structural size. By means of the desired so-called down- sizing of the drive machine at reduced operating rotational speeds, the strength of the disturbing torsional vibrations is increased and the requirement for the manipulation force is also increased when the torque is increased or the torque clutch is reduced. Similar problems arise in so-called hybridization, in which electric drive machines are used more and more frequently or even form the main torque source and a small internal combustion engine is used, which must, however, be connected to the powertrain significantly more frequently and disconnected again. It is therefore a challenge to provide sufficient manipulation force by means of the hinge actuator while the part costs are low and the available structural space is small.

[0048] The problem becomes acute in cars of the small car class according to the European classification. The powerpacks used in cars of the small car class are not significantly smaller in relation to larger vehicle classes of cars. Nonetheless, the construction space available is extremely small in small cars. The powerpack presented here is particularly advantageous for motor vehicles in which the construction space available for the hinge actuator is small and high tolerances in at least one control finger are necessary or desirable for cost reasons. The tolerances can be compensated without high resistance by the low torsional stiffness in the hinge actuator presented here.

[0049] Cars are associated with vehicle classes according to, for example, size, price, weight and power, wherein the definitions continue to change according to market requirements. In the US market, vehicles of the small car and micro car class correspond to the sub-compact class according to the European classification, while in the British market they correspond to the supermini class or the city car class. Examples of the micro 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. Known hybrid vehicles are the BMW 330e or the Toyota Yaris Hybrid. As light hybrids, for example, the Audi A6 50TFSI e or the BMW X2 xDrive25e are known. BRIEF DESCRIPTION OF DRAWINGS

[0050] The invention described above is explained in detail below in the relevant technical context with reference to the attached drawings, which show a preferred design. The invention is not limited in any way by the drawings, wherein it is noted that the drawings are not to scale and are not suitable for defining size relationships. Shown in the drawings are:

[0051] Figure 1 Perspective view of a hinge actuator with angled bearing sections;

[0052] Figure 2 Side view of a hinge actuator according to Figure 1 ;

[0053] Figure 3 Perspective cut view of a hinge actuator according to Figure 1 ;

[0054] Figure 4 Perspective view of a hinge actuator with bearing tabs;

[0055] Figure 5 Side view of a hinge actuator according to Figure 4 ;

[0056] Figure 6 Perspective view of a hinge actuator according to Figure 4cross-sectional rear view of a hinge actuator according to

[0057] Figure 7 showing a perspective cross-sectional view of a hinge actuator according to Figure 4 ; and

[0058] Figure 8 showing a powertrain with a hinge actuator in a motor vehicle. DETAILED DESCRIPTION

[0059] A perspective view of a hinge actuator 1 is shown in Figure 1 . The hinge actuator 1 has here (optionally) a base plate 38 on which a lever 6 (optionally pre-mounted as a structural unit) with a main extension 7 (see Figure 2 ) is pivotably mounted about a pivot axis 39 defined by a hinge support 8 here (optionally) by means of a mounting screw 23 on the left (according to the view) and a mounting screw 24 on the right (according to the view). The main extension 7 defines (see Figure 2 ) between the pivot axis 39 and a levering face 40, 41 of a levering finger 3, 4. Left and right here and elsewhere relate only to the view angle of Figure 1 . Transversely to the main extension 7, the hinge actuator 1 has a maximum lateral dimension 42 defined as the maximum extension in the hinge support 8 between the left and right of the base plate 38. A linear movement of the crossbar 13 (or of a carrier roller 43) is introduced into the lever 6 so as to cause a pivoting of the lever 6 (or of the main extension 7) about the pivot axis 39. The lever 6 outputs no or a minimum levering stroke (for example for a minimum required axial pretension) in the (shown) engagement position 15 of the crossbar 13 and outputs a maximum levering stroke in the (not shown) disengagement position 14 via the (here two) levering fingers 3, 4 connected to the lever 6 and provided in the prolongation of the main extension 7 of the lever 6. The left levering finger 3 and the right levering finger 4 are provided spaced apart from one another by a finger spacing 44 (a dimension between the levering fingers 3, 4, for example a free space for a shaft). The lever 6 comprises two partial levers 25, 26 in the embodiment shown here. The left levering finger 3 and the right levering finger 4 are formed in one-piece prolongations along the main extension 7. The partial levers 25, 26 are connected to one another in one piece by means of a (here only) lever bridge 27. The (only) lever bridge 27 is provided in the prolongation of the main extension 7 (relative to the view according to Figures 4 to 7the lever side. The hinge bearing 8 comprises on the fixed side a left-sided receiving element 1 1 in which the left-sided peg 9 is supported on the fixed side and a right-sided receiving element 12 in which the right-sided peg 10 is supported on the right side (see Figure 2 ). In the shown embodiment, congruence of the peg axis 20 and the pivot axis 39 is derived. Furthermore, the bow 45 and the crossbar 13 are visible together with the carrying rollers 43 and the screw drive 46 (or its bellows) having a screw axis 47, which is explained in detail below.

[0060] In Figure 2 a side view of the hinge actuator 1 according to Figure 1 is shown. The crossbar 13 is arranged between its (here paired) bearing roller tracks 48 on the base plate 38 and the lever tracks 49 on the back side of the lever 6 (with respect to the actuation faces 40, 41 of the actuation fingers 3, 4). It is well visible here that the crossbar 13 is in the engagement position 15 and that the carrying rollers 43 roll on the bearing roller tracks 48 and the lever tracks 49, which are oriented obliquely to the bearing roller tracks 48, when moved along the screw axis 47 by means of the screw drive 46 towards the indicated disengagement position 14. By this, a pivoting of the lever 6 or the main extension 7 about the pivot axis 39 is induced. By this, a high transmission ratio of the actuation force 50 along the actuation path 5 for the torque clutch 2 (see Figure 8 ) is generated. Furthermore, in this embodiment, the peg axis 20 is congruent with the pivot axis 39 of the hinge actuator 1 (according to the view perpendicular to the drawing plane). The bow 45 is here (optionally) fixed on the base plate 38 by means of at least one round rivet 51 so that the crossbar 13 together with the screw drive 46 is fixed. The right-sided peg receiving section 19 is precisely oriented by means of a positioning pin 52 (here visible to the right in the figure), as explained with respect to the embodiment according to Figures 4 to 7 .

[0061] In Figure 3 a sectional view of the hinge actuator 1 according to Figure 1 is shown. The carrying rollers 43 of the hinge actuator 1 are visible here, which roll on the bearing roller tracks 48 and the cooperating lever tracks 49 (see Figure 2) is supported and moved between an engagement position 15 (shown here) and a disengagement position 14. Here, the lever bridge 27 is positioned along the main extension 7 between the engagement position 14 and the disengagement position 15. In this embodiment, a relatively high lever stiffness is achieved due to the stiffening effect achieved by means of the webbing with the left bolt receptacle 18 and the right bolt receptacle 19.

[0062] In Figure 4 a perspective view of an alternative embodiment of the hinge actuator 1 is shown. In this regard, reference is made to the previous explanations regarding the function of the hinge actuator 1 and only the differences are emphasized. The maximum lateral dimension 42 is here in the hinge bearing 8, which is here, however, determined by the receiving elements 11, 12. In this embodiment, the hinge bearing 8 comprises on the fixed side a left bolt 9 with a bolt axis 20 and on the lever side a left bolt receptacle 18 at a left bearing web 21 (according to the view on the left of the screw drive 46) in engagement. Correspondingly on the right side, the hinge bearing 8 has on the fixed side a right bolt 10 with a bolt axis 20 and on the lever side a right bolt receptacle 19 at a right bearing web 22. In the shown (ideal) embodiment, the bolt axes 20 coincide with each other and (optionally) with the pivot axis 39. The bearing webs 21, 22 extend along the main extension 7 away from the operating fingers 3, 4, more precisely here (optionally) S-shaped. The configuration of the bolt receptacles 18, 19 is further elaborated in Figure 5 . Here again, the left operating finger 3 and the right operating finger 4 are formed in one piece in the prolongation of the main extension 7 of the lever 6. The two partial levers 25, 26 are connected to each other in one piece by means of a first lever bridge 27 and a second lever bridge 28. The first lever bridge 27 (compared to the embodiment described above with the only lever bridge 27) is arranged in the direction of the main extension 7 close to the operating fingers 3, 4, and the second lever bridge 28 is arranged close to the hinge bearing 8, so that in the operating fingers 3, 4 and in the hinge bearing 8, despite the (sought) relatively small lever stiffness (due to the bearing webs 21, 22), an excessively small torsional stiffness is not achieved.

[0063] In Figure 5 , the hinge actuator 1 according to the alternative embodiment in Figure 4 is shown here in a side view similar to the view of the hinge actuator 1 in Figure 2 . Reference is made in this regard to the explanations of the hinge actuator 1 in Figure 4 and Figure 2The left-hand side of the hinge actuator 1 is described. According to the view, in this side view, the left-hand bolt 9 is shown together with the cooperating left-hand bolt receptacle 18 at the left-hand support tab 21, wherein (optionally) the right-hand bolt 10 and the cooperating right-hand bolt receptacle 19 at the right-hand support tab 22 are identically constituted. Here, the left-hand support tab 21 is introducible (S-shaped) into the hinge support 8 approximately in the direction of the main extension 7, so that the left-hand bolt receptacle 18 at the left-hand support tab 21 is arranged behind the left-hand bolt 9 (i.e. with respect to the lever 6 operating path 5). Furthermore, in this embodiment, the bolt axis 20 runs congruently with the pivot axis 39 of the hinge actuator 8 (according to the view perpendicular to the drawing plane). The arc 45 is (optionally) fixed on the base plate 38 by means of at least one circular rivet 51, and the left-hand receptacle element 1 1 is oriented with respect to the arc 45 and the base plate 38 by means of a positioning pin 52. In the left-hand receptacle element 1 1, the (left-hand) support receptacle 16 is formed, at which the (left-hand) bolt 9 is supported. By means of the (left-hand) bolt receptacle 18, the lever 6 is pivotably supported about the pivot axis 39 in order to exert an operating force 50 by means of the (here shown left-hand) operating face 40 or an operating stroke along the operating path 5. The left-hand description of the hinge actuator 1 (optionally) applies equally to the right-hand side thereof.

[0064] In Figure 6 , a hinge actuator 1 according to Figure 4 is shown in a cutaway rear view. Here, the cutaway line runs discontinuously (vertical discontinuous line 65 in the left-hand receptacle element 1 1 ), so that the cut plane in the left-hand bolt 9 (according to the view on the right-hand side) is arranged more forward with respect to the drawing plane than the cut plane in the right-hand bolt 10. It is well visible here that the left-hand bolt 9 is accommodated in the left-hand support receptacle 16, and the right-hand bolt 10 is accommodated in the right-hand support receptacle 17. Furthermore, the left-hand bolt 9 and the right-hand bolt 10 have an inner shoulder 53 and an outer shoulder 54, respectively, in order to laterally secure the lever 6 (via the support tabs 21, 22), wherein the shoulders 53, 54 at the right-hand bolt 9 are shown only in part, representative of the whole. The relevant bolt 9, 10 is laterally fastened in cooperation with the relevant receptacle element 1 1, 12 and the associated support tab 21, 22. The inner shoulder 53 and the outer shoulder 54 (optionally) enclose the respective support face of the bolt 9, 10 in a slot-like manner, wherein the support face is in force-transmitting contact with the respective support receptacle 18, 19 of the support tab 21, 22. The position of the support receptacle 16, 17 with respect to the arc 45 is fixed by means of the positioning pin 52 and a cooperating lug 55 formed at the respective receptacle element 1 1 and a cooperating lug receptacle 56 in the arc 45.

[0065] In Figure 7 , a hinge actuator 1 according to Figure 4Cross-sectional view of the hinge actuator 1. Here reference is made to the similar view in Figure 3

[0066] In Figure 8 the power unit 30 is shown in a schematic view from above (optionally in front of the cab 57 and optionally in a transverse arrangement, i.e. the engine axis 58 is transverse to the longitudinal axis 59 of the motor vehicle 37). The left-hand propulsion wheel 35 and the right-hand propulsion wheel 36 are here (optionally) driven by the power unit 30. The power unit 30 comprises a drive machine 33 (here shown as a three-cylinder internal combustion engine) and a torque clutch 2 coupled to the drive machine 33 via a machine shaft 34. Torque can be transmitted around the axis of rotation 29 or the uniform motor axis 58 by means of the torque clutch 2 in a detachable manner. For the detachability, a torque group 31 is provided, which is here exemplarily constituted as a friction group with a pressure plate 60, a counter-pressure plate 61 connected to the machine shaft 34 in a torque-transmitting manner by means of a clutch cover 62 and a friction disc 63 axially arranged therebetween, which is connected to the propulsion wheels 35, 36 in a torque-transmitting manner via a transmission (indicated schematically by a dashed line). The actuating force 50 of the hinge actuator 1 is here transmittable to the torque group 31 of the torque clutch 2 via a lever spring 64 supported at the clutch cover 62 and an actuating bearing 32, so that the torque group 31 can be detached (configuration with constant closure) or can be closed (configuration with constant opening).

[0067] By means of the hinge actuator presented here, it is possible to save construction space and at the same time to significantly reduce costs.

[0068] Legend of the figures

[0069] 1 hinge actuator

[0070] 2 torque clutch

[0071] 3 left-hand actuating finger

[0072] 4 right-hand actuating finger

[0073] 5 actuating path

[0074] 6 lever

[0075] 7 main extension

[0076] 8 hinge bearing

[0077] 9 left-hand peg

[0078] 10 right-hand peg

[0079] 11 left-hand receiving element

[0080] 12 right-hand receiving element ​

[0081] 13 Horizontal bar

[0082] 14. Separation position

[0083] 15. Joint position

[0084] 16. Support accommodating part on the left side

[0085] 17. Right-side support housing

[0086] 18. Left-side plug housing

[0087] 19. Right-side plug housing

[0088] 20 bolt axis

[0089] 21. Support plate on the left side

[0090] 22. Support plate on the right side

[0091] 23. Mounting screws on the left side

[0092] 24. Mounting screws on the right side

[0093] 25. The lever on the left side

[0094] 26. The lever on the right side

[0095] 27 First Lever Bridge

[0096] 28 Second lever bridge

[0097] 29. Axis of rotation

[0098] 30 Powertrain

[0099] 31 Torque Group

[0100] 32. Manipulating bearings

[0101] 33 Drive Machine

[0102] 34 machine axes

[0103] 35. Left-side propulsion wheel

[0104] 36. Right-side propulsion wheel

[0105] 37 Motor vehicles

[0106] 38 substrate

[0107] 39 Pivot axis

[0108] 40. Left-side control panel

[0109] 41. Right-side control panel

[0110] 42 maximum lateral dimension

[0111] 43 carrier roller

[0112] 44 finger spacing

[0113] 45 bow

[0114] 46 screw drive

[0115] 47 screw axis

[0116] 48 support rail

[0117] 49 lever rail

[0118] 50 actuating force

[0119] 51 round rivet

[0120] 52 positioning pin

[0121] 53 inner shoulder

[0122] 54 outer shoulder

[0123] 55 protrusion

[0124] 56 protrusion receptacle

[0125] 57 cab

[0126] 58 engine axis

[0127] 59 longitudinal axis

[0128] 60 pressure plate

[0129] 61 counter-pressure plate

[0130] 62 clutch cover

[0131] 63 friction plate

[0132] 64 lever spring

[0133] 65 break line

[0134] 66 left support section

[0135] 67 right support section

Claims

1. A hinge actuator (1) for a torque clutch (2), comprising 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) connected to the operating fingers (3, 4); - Hinge support (8) for pivotally supporting the lever (6). and - A crossbar (13) that contacts the lever (6) in a force-transmitting manner, wherein the crossbar (13) is movable along the main extension (7) between a disengaged position (14) and an engaged position (15), and wherein the lever (6) is pivotable by means of the movement of the crossbar (13) to transmit the manipulation path (5). Its features are, The lever (6), together with the operating fingers (3, 4), is the only spring element that determines the lever stiffness of the lever (6). The hinge support (8) has two bolts (9, 10) with bolt axes (20) and a mating bolt receptacle (18, 19), wherein the bolt receptacles (18, 19) are formed in support sections (66, 67) of the lever (6) at an angle relative to the main extension (7) and the bolt axes (20), or the bolt receptacles (18, 19) are formed by support tabs (21, 22) of the lever (6), wherein the support tabs (21, 22) extend along the main extension (7) away from the operating fingers (3, 4).

2. The hinge actuator (1) according to claim 1. Two of the operating fingers (3, 4) are set with a finger spacing (44) transverse to the main extension (7) of the lever (6), and the hinge actuator (1) has a maximum lateral dimension (42) parallel to the finger spacing (44), wherein the maximum lateral dimension (42) is less than 4 times the finger spacing (44).

3. The hinge actuator (1) according to claim 1 or 2. When the bolt receiving portions (18, 19) are formed in the support sections (66, 67) of the lever (6) at angles relative to the main extension (7) and the bolt axis (20), respectively, In the separated position (14), the lever stiffness of the lever (6) is between 4 kN / mm and 5 kN / mm.

4. The hinge actuator (1) according to claim 1 or 2. When the bolt receiving portions (18, 19) are respectively formed by the support pieces (21, 22) of the lever (6), In the separated position (14), the lever stiffness of the lever (6) is between 1 kN / mm and 2 kN / mm.

5. The hinge actuator (1) according to claim 4, wherein The support tabs (21, 22) extend arcuately between the remaining levers (6) and the bolts (9, 10) about the cross section with the bolt axis (20) as the normal.

6. The hinge actuator (1) according to claim 1, 2 or 5. The lever (6) is laterally fixed by means of the hinge support (8).

7. The hinge actuator (1) according to claim 1, 2 or 5. The lever (6) therein comprises two partial levers (25, 26) which are connected one piece to each other by means of at least one lever bridge (27, 28).

8. A torque clutch (2) for a powertrain (30) having a rotating shaft (29), comprising at least the following components: - The hinge actuator (1) according to any one of the preceding claims; - Torque set (31), which can be axially manipulated by means of the hinge actuator (1) to adjustably transmit torque; and - The control bearing (32) between the torque group (31) and the control fingers (3, 4) of the hinge actuator (1). The control path (5) can be transmitted to the torque group (31) via the control bearing (32) by means of the crossbar (13) of the hinge actuator (1).

9. A powertrain (30) having at least one drive machine (33) with a machine shaft (34), at least one consumer, and a torque clutch (2) according to claim 8. The machine shaft (34) is adjustablely connected to the at least one consumer in a torque-transmitting manner by means of the torque clutch (2).

10. A motor vehicle (37) having at least one propulsion wheel (35, 36) capable of being driven by means of a powertrain (30) according to claim 9.

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