Hinge actuator for a torque clutch

Abstract

The present invention relates to a hinge actuator (1) for a torque clutch (2), having at least the following components: - at least one operating finger (3, 4) for transmitting an operating path (5) to the torque clutch (2); - a lever (6) having a main extension (7) connected to the operating finger (3, 4); - a hinge support (8) for pivotally supporting the lever (6); and - a crossbar (13) in contact with 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 operating path (5). The hinge actuator (1) is characterized in particular by the hinge support (8) comprising two support plates (21, 22) of the lever (6) and a mating circular support surface (70, 71), wherein the support plates (21, 22) extend along the main extension (7) away from the operating fingers (3, 4) and are pivotable on the respective mating support surfaces (70, 71). With the hinge actuator proposed herein, structural space can be saved and costs can be significantly reduced.

Description

Technical Field

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

[0002] Hinge actuators for operating torque clutches, such as those used in motor vehicles, are known from the prior art. These torque clutches are, for example, friction clutches used in powertrains. Such hinge actuators are shown, for example, in DE 10 2012 220 436 A1. A common problem is that the available structural space for the hinge actuator, especially the structural space transverse to the main extension of the hinge actuator, is extremely limited. However, cost pressures, particularly in the automotive industry, are high, not only in terms of component costs but also in terms of installation costs. Summary of the Invention

[0003] Starting from this point, the present invention aims to overcome, at least in part, the disadvantages known from the prior art. The features of the invention are derived in the independent claims, and advantageous designs are shown in the dependent claims. The features of the claims can be combined in any technically meaningful manner and method, which can also be considered from the description in the following specification and from the features in the drawings, including supplementary designs of the invention.

[0004] This invention relates to a hinge actuator for a torque clutch, comprising at least the following components:

[0005] - At least one control finger for transmitting the control path to the torque clutch;

[0006] - A lever with a main extension, the lever being connected to a control finger;

[0007] - A hinge support for pivotally supporting a lever; and

[0008] - A crossbar that contacts the lever in a force-transmitting manner, wherein the crossbar is movable along the main extension between a disengaged position and an engaged position, and wherein the lever is pivotable by means of the movement of the crossbar to transmit the manipulation path.

[0009] The hinge actuator is characterized in particular by the hinge support comprising two support plates of the lever and a mating circular support surface, wherein the support plates extend along the main extension away from the operating finger and are pivotable on the respective mating support surface.

[0010] Ordinal numbers used in the preceding and following descriptions, unless explicitly indicated otherwise, are used only for one-to-one distinguishability and do not describe the order or sequence of the mentioned components. Ordinal numbers greater than one do not necessarily imply the mandatory existence of another component of the same kind.

[0011] Furthermore, the terms used for spatial description can be arbitrarily chosen on the left and right sides and can also be used interchangeably (uniformly). They are only used for a good overview, especially regarding paired arrangements of components.

[0012] When axial, radial, or circumferential directions and their corresponding terms are used without explicit further explanation, reference is made below to the actuation axis of a hinge actuator (e.g., the rotation axis of a torque clutch that transmits torque about the rotation axis). Furthermore, reference to a hinge actuator refers to the main extension of a lever, wherein the lever is pivotable about a pivot axis of the hinged support, which is oriented transversely (ideally 90°) to the main extension. This pivot axis may be displaced and / or not centered on the supporting member during the pivoting motion of the lever, for example, not coinciding with the central axis of the bolt. The orientation of the actuation path can be approximately understood as a third spatial direction, wherein the actuation path is transverse (ideally 90°) to the pivot axis and variably transversely to the main extension during the pivoting motion of the lever by a pivot angle corresponding to the actuation path. Lever stiffness is derived from the deflection of the lever relative to the main extension in the direction of the actuation path, wherein the effective length of the lever is changed by means of the actuation of the crossbar, more precisely, shortened as the actuation path increases. This means that the effective length of the lever is greatest when the crossbar is in the engaged position and smallest when the crossbar is in the disengaged position. This is explained in more detail below. The lever has a construction extension (parallel to the pivot axis) between its main extension and its left and right sides. The operating path is arranged laterally relative to the construction surface. Lateral movement of the lever, i.e., movement to the left or right (with clearance where necessary), is prevented.

[0013] The hinge actuator proposed herein is designed, for example, for an axially operable torque clutch, such as an axially compressible friction clutch. Alternatively, the hinge actuator is generally designed to transmit axial force, preferably by means of a central shaft that rotates about its axis of rotation. The hinge actuator includes at least one, preferably two, actuating fingers, wherein the two actuating fingers (e.g., when used in a torque clutch) act on an actuating bearing. The actuating bearing is designed to transmit an actuating path, e.g., to the torque clutch. The actuating fingers are connected to a lever, preferably formed in one piece, wherein the actuating fingers are disposed in an extension of the main extension of the lever. The main extension corresponds to a lever in a simplified model, wherein the lever, for example as a real component of a sheet metal member, is not required to have symmetry about the main extension, nor is it required to have its maximum extension direction in the direction of its main extension (the centerline). The main extension and the pivot axis form a plane, and the actuating surface of the actuating fingers lies in said plane. A central axis extends in said plane of the main extension, which, in the case of two actuating fingers, extends centrally between the actuating fingers and preferably intersects the pivot axis perpendicularly. Advantageous for a variety of applications is that the lever is constructed cost-effectively and in a space-saving manner, making it particularly advantageous as a sheet metal member with reinforcing ribs and / or rolled edges. In this embodiment constructed of sheet metal, the theoretical plane of the main extension does not fully extend through the actual member of the lever.

[0014] The lever is pivotally supported about a pivot axis by means of a hinge support, such that the lever (about the pivot axis) pivots to describe the basic function of the lever by means of at least one actuating finger applying an actuating path. Furthermore, a crossbar is provided in the hinge actuator. The crossbar contacts the lever in such a force-transmitting manner that the lever pivots about the pivot axis by means of the crossbar's movement along the main extension. Preferably, the crossbar, formed by one or more, preferably two, support rollers for transmitting force to the lever with low friction, is movable between a disengaged position and an engaged position. The crossbar, together with the lever, forms a ramp-shaped actuating assembly. For example, the actuating assembly is formed by means of a lever ramp on the side of the crossbar (on the back side of the lever) and a support rail on the side opposite to the crossbar (e.g., at the base plate). The slope of the lever ramp and / or the support rail can be arbitrarily configured according to individual requirements. For a linearly driven crossbar (e.g., by means of a screw drive with a screw axis as the linear motion axis), it is advantageous that the support rail is configured flat.

[0015] It should be noted here that the hinge actuator is operated via a crossbar (as described above), wherein, for example, a rotating electric drive is connected to a screw drive, which causes relative movement of the ramp-shaped actuation assembly of the crossbar and forces at least one actuating finger to move along the actuation path by means of a ramp-shaped connection with a lever. In a preferred embodiment, the actuating force at the actuating finger, caused by the movement of the crossbar between the engaged and disengaged positions, is (approximately) constant throughout the actuation path due to the mounting configuration.

[0016] The lever provides no operating travel or only minimal operating travel (e.g., for minimal axial preload) in the engaged position of the crossbar, and provides maximum operating travel via the operating finger in the disengaged position of the crossbar. It is important to note that the main extension moves with the lever, thus, from the perspective of a coordinate system moving with the lever, the crossbar describes a circular or arcuate track with the slope of the lever ramp being, for example, constant. The crossbar still particularly preferably moves along a rigid screw axis, wherein the screw axis is fixed to a fixed component, such as the base plate of a hinge actuator.

[0017] The crossbar, as described above, is driven, for example, by a screw drive such as a ball screw drive with a screw axis, wherein the crossbar itself is configured as a slider comprising a driven (axially movable) screw nut or a driven (axially movable) screw, and the driven (rotating) screw or driven (rotating) screw nut is driven by a rotating, preferably electrically driven, mechanism. The screw axis is therefore preferably oriented 90° transverse to the pivot axis and at a relative ramp angle to the main extension of the lever.

[0018] It is now proposed that the hinge support includes two support plates of the lever and a mating circular support surface, preferably as a single additional support receiving portion.

[0019] The support tab extends within the extension of the lever to the hinge support. The support tab is preferably designed such that the lever stiffness is significantly reduced compared to previously known embodiments of the hinge actuator. In a particularly preferred embodiment, in the disengaged position of the lever, i.e., with the effective length of the lever shortened or the finger-side portion of the lever shortened, the lever stiffness, i.e., (at least approximately) the effective actuation stiffness of the hinge actuator, is between 1 kN / mm [one thousand Newtons per millimeter] and 2 kN / mm, for example, approximately 1.7 kN / mm. This allows customer requirements for relatively low lever stiffness to be met.

[0020] The mating circular support surface is formed, for example, by a metal plate, a rod-shaped component, or a single bolt. Each support tab has a support surface receiving portion (e.g., a bolt receiving portion) at the mating location, the support surface receiving portion having a mating shape such that a pivot axis is defined (and may wander if necessary) by the support surface and the mating support surface receiving portion. In a preferred embodiment, the support surface receiving portion is bathtub-shaped, i.e., formed by a central recess, two limiting edges, and a circular transition wall portion (of the support member) between them. In one embodiment, the support surface receiving portion is not precisely fitted to the support surface, so that different shapes of support surfaces can be used for (preferably always) the same support surface receiving portion.

[0021] Support tabs or support surface receptacles can be manufactured cost-effectively and can be individually matched to requirements, such as desired pivoting motion and / or the shape of the support surface, for example, in the case of a change in the diameter of the bolt forming the support surface. This reduces tooling costs. Furthermore, such support tabs can be manufactured with high precision using a simple mechanism, enabling high accuracy and / or low production costs.

[0022] Furthermore, in an advantageous embodiment of the hinge actuator, it is proposed that the lever, together with the operating finger, is the only spring element that determines the lever stiffness.

[0023] In this embodiment, no additional spring element is formed, which is conventionally designed, for example, to determine the lever stiffness. More precisely, the length of the lever or the lever itself, acting according to the position of the crossbar, forms a member, whose stiffness is simplified to be determined by the type of crossbar, such as a cantilever beam or a three-point supported beam. In the case of two operating fingers, torsion of the lever (e.g., around the main extension) may occur due to tolerances, for example, due to a difference of up to 0.2 mm [two-tenths of a millimeter] between the operating fingers along the direction of the operating path in the (fully) relaxed position and / or engaged position (minimum operating stroke). Thus, the first operating finger, in the case where the operating stroke is configured along the operating path, engages first individually or (compared to the second operating finger) in a force-transmitting manner, and the second operating finger follows.

[0024] In this implementation, the support plate is a particularly critical component because it (in the case of a beam with three supports) strongly influences or even decisively determines the lever stiffness and thus the effective stiffness of the hinge actuator.

[0025] Eliminating the separate (additional) spring element not only reduces costs but also saves structural space.

[0026] Furthermore, in an advantageous embodiment of the hinge actuator, it is proposed that two operating fingers are arranged laterally to the main extension of the lever with a finger spacing, and the hinge actuator has a maximum lateral dimension parallel to the finger spacing, wherein the maximum lateral dimension is less than 4 times the finger spacing, preferably less than 2.5 times.

[0027] In this embodiment, the width of the hinge actuator is significantly reduced compared to previously known embodiments. The finger pitch, i.e., the lateral dimension of the free space created between the two operating fingers, is determined, for example, by the size of the component to be operated with axial force, such as the shaft diameter in the case of the operating bearing of a torque clutch, and / or the required operating force. The maximum lateral dimension of the hinge actuator is the maximum extension between the left and right sides and / or the extension in which conventional hinge actuators have their maximum extension between the left and right sides, which has therefore so far determined the structural space. In a ratio just less than 4 times [four times], the lever is more rigid or can be manufactured more cost-effectively with a smaller sheet metal thickness. In a ratio less than 2.5 times, structural space can be significantly saved. In a particularly preferred embodiment, the ratio is, for example, 2.2 times the finger pitch. The maximum lateral dimension is then formed in the hinge support. The component determining the structural space is, for example, a fastening element for mounting the hinge actuator in a transmission of a motor vehicle.

[0028] Furthermore, in a preferred embodiment of the hinge actuator, it is proposed that the support tab, in terms of its cross-section, has a normal extending parallel to the support surface, and extends arcuately between the remaining lever and the support surface.

[0029] In the described embodiment of the hinge actuator, the support piece, as described above, is formed by a lever that is very flat in the region of the crossbar's movement path, more precisely, towards or away from the crossbar. The cross-section is thus situated in a plane in which the pivot axis is oriented normally (in ideal observation) relative to said plane. This cross-section describes an arcuate shape, preferably S-shaped, between the remaining lever and the hinge support. This allows for a soft engagement of the lever at the hinge support due to the extension of the support piece compared to a straight or shortest connection. Alternatively or additionally, structural space on the back side of the lever along the direction of the operating path can be saved by allowing the hinge support to be positioned deeper along the direction of the operating path, i.e., closer to the crossbar, when the support piece has an arcuate shape towards the crossbar. This structural space corresponds in various applications to the axial structural space in applications where torque is transmitted around a shaft about a rotation axis.

[0030] Furthermore, in an advantageous embodiment of the hinge actuator, the hinge support includes two bolts and two mating receiving elements, wherein the bolts respectively form a support surface, and wherein, for installation, the support tabs can be introduced into the receiving elements in the direction of the main extension.

[0031] In the described embodiment, the support surfaces are each formed by a bolt. The bolt is a cost-effective component with good wear resistance, which can be easily defined and / or easily achieved, for example, by means of hardness. Furthermore, the bolt can be easily installed, and the accommodating support portion can be simply and cost-effectively constructed, for example, as a hole. In a preferred embodiment, the bolt is constructed as in conventional embodiments of hinge actuators, allowing the use of tested components and / or components from established production lines or supply chains.

[0032] In at least the described embodiments, a support tab, for example generally in the direction of the main extension and / or generally toward the screw axis of the crossbar, may be introduced into the hinge support such that the support tab (by means of its corresponding bolt receptacle) is positioned behind the corresponding bolt (i.e., with respect to the movement path derived by the crossbar from the engaged position to the disengaged position), wherein preferably, the bolt has been installed. The lever is prevented from self-disassembly by means of the shape of at least one of the bolt receptacles and / or by an installation orientation deviating from the operating condition (i.e., the orientation of the lever between the engaged and disengaged positions), preferably by means of the previously described bathtub shape of the associated bolt receptacle.

[0033] Furthermore, in a preferred embodiment of the hinge actuator, the lever is laterally fixed by means of a hinge support, preferably by means of at least one of the bolts according to the embodiments described above.

[0034] In this embodiment, the lever is fixed laterally, i.e., to the left and right, without the need for additional components, by means of hinge supports. For example, lateral stops are formed to the right and / or left, for example by means of a shoulder of the support element and / or by means of the wall of the support element receiving portion. In a preferred embodiment, lateral fixation is formed by means of at least one of the bolts according to one of the above embodiments, preferably by means of two bolts. For this purpose, the bolt has, for example, at least one shoulder (diameter extension), preferably two shoulders, wherein preferably, the shoulders contact not only with the corresponding bolt receiving portion but also with the corresponding support element receiving portion in a force-transmitting manner (e.g., with a gap). Lateral fixation on both sides is particularly advantageous in embodiments of the lever that are flexible, especially (around the main extension) torsional flexible. With the embodiments presented herein, a simple construction and / or minimal structural space requirements can be achieved. It should be noted that the lever is preferably only elastically torsionable under the designed load.

[0035] Furthermore, in an advantageous embodiment of the hinge actuator, it is proposed that the lever comprises two partial levers, which are connected to each other in one piece by means of at least one lever bridge.

[0036] In this embodiment, the lever is divided into two partial levers, for example, associated with one of the two operating fingers. By providing two partial levers, which are preferably connected to each other in one piece by means of at least one lever bridge, a particularly small torsional stiffness (around the main extension) is achieved. This allows for large tolerances with respect to the operating surface of at least one operating finger, as angular deviations or misalignments of the two operating fingers with respect to the operating mating surfaces, such as the operating bearing of a torque clutch, can be compensated with small resistance. This (small) resistance is determined, for example, by (small) lateral forces in the hinge support and / or by (small) force differences at the two separate operating surfaces of the two operating fingers and / or at the crossbar, which preferably comprises two load-bearing rollers (on the left and right sides). In an embodiment with a bent support section, preferably, a single lever bridge is provided, which is positioned at a large distance from at least one operating finger (compared to the embodiment described below), such that a sufficiently small torsional stiffness is achieved in the operating finger while the lever stiffness is relatively large (due to the bent support section). In one embodiment with a support tab, two lever bridges are preferably provided, wherein the (first) lever bridge (compared to the previously mentioned embodiment with a single lever bridge) is located close to at least one operating finger, and the other (second) lever bridge is located close to the hinge support, such that although the lever stiffness (due to the support tab) is relatively small in the operating finger and in the hinge support, an excessively small torsional stiffness is not achieved.

[0037] According to another aspect, a torque clutch with a rotating axis for a powertrain is proposed, comprising at least the following components:

[0038] - A hinge actuator according to the embodiment described above;

[0039] - A torque assembly, preferably an axially compressible friction assembly, said torque assembly being axially actuated by means of a hinge actuator for adjustable torque transmission; and

[0040] - The control bearing between the torque group and the control finger of the hinge actuator

[0041] The hinge actuator's crossbar allows the control motion to be transmitted to the torque set via the control bearing.

[0042] The torque clutch proposed herein is, for example, a friction clutch or a form-fit clutch, such as a claw clutch or a so-called wedge clutch. With the aid of a torque clutch, torque can be transmitted separably around a rotational axis. The torque clutch is a switching element, for example, for transmitting or disengaging a torque-transmitting connection, wherein a torque set performs this task. The torque set is axially actuated by means of a hinge actuator, configured as a friction set, for example, axially compressible, wherein the actuating force applied by the hinge actuator, or the current actuating stroke derived from a position set between the disengaged and engaged positions of the crossbar, is proportional, if necessary, via a lever spring, to the desired maximum transmittable torque. The hinge actuator is configured such that the hinge actuator or its pivot axis (ignoring spring stiffness and the desired free movement if necessary for actuating the pivot axis) is fixed, for example, by means of mounting screws at a fixed component, and extends between the actuating fingers by means of a shaft connected to the torque clutch, such as a transmission input shaft (in embodiments with two actuating fingers). At least one actuating finger preferably acts on a rotating axial bearing ring via an actuating bearing, and the rotating axial bearing ring transmits the actuating force from the rotating axial bearing ring to the torque set. By means of the actuating bearing, the actuating finger, and thus the hinge actuator, is torque-selectable. In the engaged position of the crossbar, no actuating path or only a minimal actuating path (e.g., for the desired minimum preload) is applied to the actuating bearing, and in the disengaged position of the crossbar, the maximum actuating path (e.g., for the maximum pressure of the friction set) is applied to the actuating bearing.

[0043] A torque clutch has an axially operable torque set, such as an axially clampable friction set, for the (adjustable) separable transmissibility of torque. The adjustability of torque transmissibility also includes switching, i.e., disengagement and (full) engagement, as in a claw clutch, and in a friction clutch, steplessly (or, for example, incrementally due to manipulation) adjusting the maximum transmissible torque amount, for example, to eliminate torque excess. In a friction set, there are typically at least two friction plates and at least one clutch disc. In a simple embodiment, a single clutch disc is positioned between a first friction plate, i.e., an axially movable clamping plate, and a second friction plate, preferably an axially fixed counter-clamping plate, and clamped between them by means of a clamping force for torque transmission in a frictional engagement. This clamping force is generated or (servo-supported) by a hinge actuator, wherein the provided operating force is typically converted into a clamping force by means of a lever spring. Due to the clamping force, frictional force is generated between the pre-determined frictional engagement area of ​​the clutch disc and the corresponding engagement friction area of ​​the corresponding friction plate via the planar friction pairs. This frictional force, multiplied by the average radius of the formed friction surfaces, yields the transmittable torque. Multiplying this by the number of friction pairs roughly yields the maximum total transmittable torque of the friction clutch. In the unclamped state of the friction pairs, no torque or only a reliably small drag torque is transmittable. The friction clutch can be configured, for example, as a dual clutch with two friction pairs, wherein preferably, the corresponding counter-pressure plates are formed by a common central plate. It should be noted here that the hinge actuator is operated via a crossbar, wherein, for example, a rotating electric drive is connected to a screw drive, which causes the slider-like crossbar to move linearly and forces at least one operating finger to move along the operating path by means of a ramp-like connection with a lever. In a preferred embodiment, the operating force at the operating finger is (almost) constant along the entire operating path obtained by the movement of the crossbar between the engaged and disengaged positions.

[0044] The hinge actuator proposed herein can be installed in a particularly small structural space with low tension, while the hinge actuator is not complicated to construct and can be installed simply. In a dual clutch, for example, two of the hinge actuators proposed herein are provided (e.g., rotating about each other's axis of rotation).

[0045] According to another aspect, a powertrain is proposed having at least one drive machine with a machine shaft, at least one consumer, and a torque clutch according to the embodiment described above, wherein the machine shaft is adjustablely connected to at least one consumer by means of the torque clutch in a manner that transmits torque.

[0046] The powertrain proposed herein includes a torque clutch, such as a friction clutch, according to the embodiments described above. The torque clutch, by means of an operating force or clamping force applied to a torque set, such as a friction set, by means of a hinge actuator output according to the embodiments described above, allows torque to be transmitted from a drive machine or its machine shaft to at least one consumer, for example, to a drive wheel in a motor vehicle. This does not preclude the reverse torque transmission from the consumer to the machine shaft, for example, in a motor vehicle for the use of engine braking for vehicle deceleration and / or recovery of braking energy. The drive machine is, for example, an internal combustion engine and / or an electric drive machine. In one embodiment, the input side of the torque clutch is torque-fixedly connected to the machine shaft and the output side (at least indirectly, for example, via a transmission) is torque-fixedly connected to at least one consumer.

[0047] The torque clutch proposed herein is particularly advantageous for powertrains where there is limited structural space available for the hinge actuator, and preferably, high tolerances in at least one actuating finger are necessary or desirable for cost reasons. These tolerances can be at least partially compensated for by means of flexible support tabs without the need for additional spring elements.

[0048] According to another aspect, a motor vehicle is proposed having at least one propulsion wheel, which can be driven by means of a powertrain according to an embodiment described above.

[0049] Structural space is particularly limited in motor vehicles due to the increased number of components, making it especially advantageous to use a powertrain with a smaller structural size. This reduction in operating speed, along with the desired simplification of the drive mechanism, increases the intensity of torsional vibrations and also raises the requirements for steering force when torque increases or torque clutches decrease. Similar problems arise in so-called hybrid powertrains, where the electric drive mechanism is used more frequently or even forms the primary torque source, and the smallest possible internal combustion engine is used, which must engage and disengage from the powertrain significantly more frequently. Therefore, providing sufficient steering force with hinged actuators while maintaining low component costs and limited available structural space becomes a challenge.

[0050] The aforementioned problem becomes acute in passenger cars classified as small cars according to European classifications. The units used in small car class passenger cars are not significantly smaller than those in larger vehicle class passenger cars. Nevertheless, the available construction space is extremely limited in small cars. The powertrain proposed herein is particularly advantageous for motor vehicles where the available construction space for the hinge actuator is small, and where high tolerances in at least one control finger are necessary or desirable for cost reasons. These tolerances can be compensated at least partially by means of flexible support tabs without the need for additional spring elements.

[0051] Passenger cars are associated with vehicle classes based on factors such as size, price, weight, and power, and these definitions are constantly evolving according to market demand. In the US market, vehicles in the small and microcar classes correspond to the subcompact car class according to European classifications, while in the UK market they correspond to the submini or city car class. Examples of microcar classes are the Volkswagen up! or the Renault Twingo. Examples of small car classes 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. Mild hybrids are known examples such as the Audi A6 50 TFSI e or the BMW X2 xDrive25e. Attached Figure Description

[0052] The invention described above is further elaborated below with reference to the accompanying drawings, which illustrate preferred designs, within the relevant technical context. The invention is not limited in any way by the schematic diagrams, and it should be noted that the drawings are not to scale and are not suitable for defining size relationships. The drawings show:

[0053] Figure 1 A perspective view of the hinge actuator is shown.

[0054] Figure 2 Showing according to Figure 1 A sectional side view of the hinge actuator;

[0055] Figure 3 Showing according to Figure 1 A sectional rear view of the hinge actuator; and

[0056] Figure 4 A motor vehicle with a powertrain and hinge actuators is shown. Detailed Implementation

[0057] exist Figure 1 The figure shows a perspective view of the hinge actuator 1. The hinge actuator 1 here (optionally) has a base plate 38 on which a lever 6 having a main extension 7 is pivotally mounted about a pivot axis 39 defined by the hinge support 8 (see Figure 1). Figure 2 (Optionally pre-installed as a structural unit). The main extension 7 is defined between the pivot axis 39 and the operating surfaces 40, 41 of the operating fingers 3, 4 (see...). Figure 2 Here and elsewhere, on the left and on the right, only involves Figure 1 The view angle. Laterally to the main extension 7, the hinge actuator 1 has a maximum lateral dimension 42, which is defined as the maximum extension between the left and right sides at the hinge support 8. Crossbar 13 (or load-bearing roller 43, see...) Figure 2The linear motion of the lever 6 is introduced into the lever 6, thereby causing the lever 6 (or the main extension 7) to pivot about the pivot axis 39. The lever 6 provides no operating travel or provides minimal operating travel (e.g., for minimal required axial preload) in the (shown) engaged position 15 of the crossbar 13, and provides maximum operating travel in the (not shown) disengaged position 14 via operating fingers 3, 4 connected to the lever 6 and disposed in the extension of the main extension 7 of the lever 6 (see...). Figure 2 The left operating finger 3 and the right operating finger 4 are spaced apart from each other by a finger spacing 44 (the dimension of the free space between the operating fingers 3 and 4, for example, for the shaft). The lever 6 shown here comprises two partial levers 25 and 26. The left operating finger 3 and the left partial lever 25, and the right operating finger 4 and the right partial lever 26, are formed in a single-piece extension along the main extension 7. The two partial levers 25 and 26 are connected to each other in a single piece by means of a first lever bridge 27 and a second lever bridge 28. The first lever bridge 27 is positioned close to the operating fingers 3 and 4 along the direction of the main extension 7, and the second lever bridge 28 is positioned close to the hinge support 8, such that, despite the (desired) relatively small lever stiffness, an excessively small torsional stiffness is not achieved in the operating fingers 3 and 4 and in the hinge support 8.

[0058] The hinge support 8 includes a left-side receiving element 11 on the fastening side and a left-side bolt 9 with a bolt axis 20 in its (left-side) support receiving portion 16 (see [link]). Figure 2 Furthermore, on the lever side, the left-hand support piece 21 (according to the figures, on the left side of the screw drive 46) includes a mating left-hand bolt receiving portion 18. Correspondingly on the right side, the hinge support 8 includes a right-hand receiving element 12 on the fastening side and includes a right-hand bolt 10 with bolt axis 20 in its right-hand support receiving portion 17, and on the lever side includes a mating right-hand bolt receiving portion 19 at the right-hand support piece 22. In the illustrated (ideal) embodiment, the bolt axes 20 coincide with each other and (optionally) with the pivot axis 39. The support pieces 21, 22 extend along the main extension 7 away from the operating fingers 3, 4, and more precisely, (optionally) extend in an S-shape. The configuration of the bolt receiving portions 18, 19 is as follows: Figure 2 This will be further elaborated below. Furthermore, the bow-shaped member 45 and the crossbar 13, together with the bearing roller 43 and the screw drive 46 (or its bellows) having a screw axis 47, are described in detail below.

[0059] exist Figure 2 In China, according to Figure 1The hinge actuator 1 of the embodiment is shown here in a sectional side view. According to the view, the left bolt 9, together with the left support surface 70 (acting as a support member) and the left bolt receiving portion 18 engaging at the left support tab 21, is shown. Optionally, the right bolt 10, together with the right support surface 71 (acting as a support member) and the right bolt receiving portion 19 engaging at the right support tab 22, is similarly configured. Here, the left support tab 21 (S-shaped) is introduced into the hinge support member 8 approximately along the direction of the main extension 7, such that the left bolt receiving portion 18 at the left support tab 21 is located behind the left bolt 9 (i.e., regarding the operating path 5 of the lever 6). Furthermore, in this embodiment, the bolt axis 20 extends in accordance with the pivot axis 39 of the hinge actuator 1 (perpendicular to the drawing plane according to the view). A support receptacle 16 is formed in the left-hand receiving element 11, at which a bolt 9 is supported. The lever 6 is pivotally supported about a pivot axis 39 by means of the bolt receptacle 18, so that an operating force 50, or an operating stroke along the operating path 5, can be applied by means of the operating surface 40 shown here. The description of the left side of the hinge actuator 1 (optionally) also applies to its right side.

[0060] The crossbar 13 is positioned between a support rail 48 on the base plate 38 and a lever rail 49 on the rear side of the lever 6 (with respect to the operating surfaces 40, 41 of the operating fingers 3, 4). It is readily apparent that the crossbar 13 is in the engaged position 15 and the support rollers 43 roll on the support rail 48 and the lever rail 49, which is inclined to the support rail 48, as the crossbar 13 moves along the screw axis 47 toward the indicated disengaged position 14 by means of the screw drive 46. This causes the lever 6 or the main extension 7 to pivot about the pivot axis 39. This is, for example, for the torque clutch 2 (see...). Figure 4 The high gear ratio generates a driving force 50. The bow-shaped member 45 is (optionally) fixed to the base plate 38 by means of at least one round rivet 51, thereby fixing the crossbar 13 together with the screw drive 46. The bolt receiving portion 18 is precisely oriented by means of the locating pin 52 (visible on the left in the figure).

[0061] exist Figure 3 In the sectional rear view, it is shown according to Figure 1 and Figure 2The hinge actuator 1. Here, the section line extends discontinuously (vertical break line 65 in the left receiving element 11), such that the section plane in the left bolt 9 (on the right according to the view) is positioned further forward with respect to the drawing plane than the section plane in the right bolt 10. It is clearly visible here that the left bolt 9 is received in the left support receiving portion 16 and the right bolt 10 is received in the right support receiving portion 17. Furthermore, the left bolt 9 and the right bolt 10 have an inner shoulder 53 and an outer shoulder 54 respectively for laterally securing the lever 6 (via support tabs 21, 22), wherein the shoulders 53, 54 are shown only at the right bolt 9 in a partially representative manner. The respective bolts 9, 10 are laterally secured in conjunction with the corresponding receiving elements 11, 12 and the associated support tabs 21, 22. The inner shoulder 53 and the outer shoulder 54 (optionally) groove-shaped surround the corresponding support surfaces 70 and 71 of the bolts 9 and 10, wherein the support surfaces 70 and 71 contact the corresponding support member receiving portions 18 and 19 of the support tabs 21 and 22 in a force-transmitting manner. The positions of the support member receiving portions 16 and 17 relative to the bow-shaped member 45 are determined by means of the locating pin 52 and the protrusion 55 formed at the corresponding receiving element 11 and the cooperating protruding receiving portion 56 in the bow-shaped member 45. The relative position of the pivot axis 39 relative to the base plate 38 is here determined by means of the shims 68 and 69 between the corresponding receiving elements 11, 12 and the bow-shaped member 45. The dashed lines show the left mounting screw 23 in the left receiving element 11 and the right mounting screw 24 in the right receiving element 12, by means of which the hinge actuator 1 can be fastened in the use position, for example, as in Figure 4 In the torque clutch 2 shown in the figure. In one embodiment, the hinge actuator 1 can be pre-installed as a structural unit by means of mounting screws 23, 24.

[0062] exist Figure 4The powertrain 30 is shown from above in the schematic diagram (optionally located in front of the cab 57 and optionally in a transverse configuration, i.e., the engine axis 58 is transverse to the longitudinal axis 59 of the vehicle 37). The left drive wheel 35 and the right drive wheel 36 are here (optionally) driven by the powertrain 30. The powertrain 30 includes a drive machine 33 (shown here 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 disengaged about the rotation axis 29 or the corresponding engine axis 58 by means of the torque clutch 2. For disengagement, a torque assembly 31 is provided, which is exemplarily configured here as a friction assembly having a pressure plate 60, a counter-pressure plate 61 connected to the machine shaft 34 by means of a clutch cover 62 in a torque-transmitting manner, and a friction disc 63 axially disposed therebetween, which is connected to the drive wheels 35, 36 via a transmission (schematically indicated by dashed lines) in a torque-transmitting manner. The operating force 50 of the hinge actuator 1 can be transmitted to the torque group 31 of the torque clutch 2 via the lever spring 64 supported at the clutch cover 62 and the operating bearing 32, so that the torque group 31 can be disengaged (normally closed configuration) or closed (normally open configuration).

[0063] By using the hinge actuator proposed herein, structural space can be saved and costs can be significantly reduced at the same time.

[0064] Explanation of reference numerals in the attached figures

[0065] 1. Hinge actuator

[0066] 2 Torque Clutch

[0067] 3. Left-hand control finger

[0068] 4. Right-hand control fingers

[0069] 5. Manipulation Path

[0070] 6. Leverage

[0071] 7. Main Extension

[0072] 8. Hinge support components

[0073] 9. The bolt on the left

[0074] 10. The bolt on the right.

[0075] 11. Left-side receiving element

[0076] 12. Receiving element on the right

[0077] 13 Horizontal bar

[0078] 14. Separation position

[0079] 15. Joint position

[0080] 16. Left-side support housing

[0081] 17. Right-side support housing

[0082] 18. Left-side bolt housing

[0083] 19. Right-hand bolt housing

[0084] 20 bolt axis

[0085] 21. Left support plate

[0086] 22. Right-side support plate

[0087] 23. The mounting screw on the left.

[0088] 24. Right-hand mounting screws

[0089] 25. The left side of the lever

[0090] 26. The right-hand lever

[0091] 27 First Lever Bridge

[0092] 28 Second lever bridge

[0093] 29. Axis of rotation

[0094] 30 Powertrain

[0095] 31 Torque Group

[0096] 32. Manipulating bearings

[0097] 33 Drive Machine

[0098] 34 machine axes

[0099] 35. Left-hand propulsion wheel

[0100] 36. Right-hand propulsion wheel

[0101] 37 Motor vehicles

[0102] 38 substrate

[0103] 39 Pivot axis

[0104] 40 Left control panel

[0105] 41. Right-hand control panel

[0106] 42 Maximum lateral dimension

[0107] 43 Carrying Roller

[0108] 44 finger spacing

[0109] 45 Bow-shaped parts

[0110] 46. ​​Screw drive device

[0111] 47. Screw axis

[0112] 48 Support rails

[0113] 49 Lever Track

[0114] 50 Controlling force

[0115] 51 Round rivets

[0116] 52 Positioning Pins

[0117] 53 Internal shoulder

[0118] 54 External shoulder

[0119] 55 bulge

[0120] 56. Protruding receiving part

[0121] 57 Driver's Cab

[0122] 58 Engine shaft

[0123] 59. Vertical axis

[0124] 60 clamping plate

[0125] 61 Counter-pressure plate

[0126] 62 Clutch cover

[0127] 63 Friction disc

[0128] 64-bar spring

[0129] 65 Disconnected wire

[0130] 68. Left side pad

[0131] 69. The right-hand gasket

[0132] 70 Left-side support surface

[0133] 71. The support surface on the right.

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 hinge support (8) includes two spaced-apart support pieces (21, 22) of the lever (6) and a mating circular support surface (70, 71), wherein the support pieces (21, 22) extend along the main extension (7) away from the operating finger (3, 4) and are pivotable on the corresponding mating support surface (70, 71); wherein the lever (6) together with the operating finger (3, 4) is the only spring element that determines the lever stiffness.

2. The hinge actuator (1) according to claim 1. The support tabs (21, 22) have, in terms of their cross-section, normals extending parallel to the support surfaces (70, 71), and extend arcuately between the remaining levers (6) and the support surfaces (70, 71).

3. The hinge actuator (1) according to claim 1. The hinge support (8) includes two bolts (9, 10) and two mating receiving elements (11, 12), wherein the bolts (9, 10) form support surfaces (70, 71) respectively. For installation purposes, the support tabs (21, 22) can be introduced into the receiving element (11, 12) along the direction of the main extension (7).

4. The hinge actuator (1) according to any one of the preceding claims. The lever (6) is laterally fixed by means of the hinge support (8).

5. The hinge actuator (1) according to any one of claims 1 to 3 above. The lever (6) comprises two partial levers (25, 26) which are connected to each other in one piece by means of at least one lever bridge (27, 28).

6. 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) for adjustable torque transmission; and - The control bearing (32) between the torque group (31) and the control fingers (3, 4) of the hinge actuator (1). The manipulation path (5) can be transmitted to the torque group (31) via the crossbar (13) of the hinge actuator (1).

7. 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 6. 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).

8. A motor vehicle (37) having at least one propulsion wheel, the propulsion wheel being driveable by means of a powertrain (30) according to claim 7.

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