Torque transmission device and overload clutch of torque transmission device

Abstract

The invention relates to a torque transmission device (1, 61, 70, 71) for transmitting a drive torque between a first connecting element (16) and a second connecting element (17), in which a torsional vibration damper (4) is functionally arranged between an input (2) and an output (3), the overload clutch (50, 60) is arranged functionally between the torsional vibration damper (4) and the output flange (12), and wherein the overload clutch (50, 60) is connected to the output flange (12, 68, 69) and at least one housing section (10a) of the housing (10), which housing section is connected to the housing (10), is clamped in the overload clutch (50, 60) in a frictional manner.

Description

Field of the Invention

[0001] The present invention relates to a torque transmission device according to the preamble of claim 1. Background Art

[0002] In the drive train of a motor vehicle, the task of a torque transmission device is to transmit the torque generated by a drive device to a transmission with as little vibration as possible. The torque transmission device according to the subject matter of the present application corresponds to the following type, i.e., an overload clutch is arranged between a torsional vibration damper and a driven flange on the secondary side of the torque transmission device. Such a torque transmission device is disclosed by DE 10 2020 122185A1 and DE 10 2020 129 170A1. Summary of the Invention

[0003] The object of the present invention is to provide a torque transmission device that can be manufactured and installed simply and at low cost, and that has a torsional vibration damper and an overload clutch.

[0004] This object is achieved by the subject matter of the claims.

[0005] The overload clutch is also referred to as a torque limiter in technical terms. The torque limiter involved is a friction clutch in which different friction pairs are pressed against each other in a force-transmitting manner until a defined starting frictional torque. The torque limiter can prevent damage caused by high and sudden torque peaks in the overload clutch and in the drive train. The torque limiter operates according to the principle of a slip friction clutch in such a way that, after the starting frictional torque is reached, the input part and the output part of the overload clutch are disengaged from each other in a frictional engagement and pivot or rotate relative to each other about the axis of rotation by friction control. The input part of the overload clutch according to the present invention is formed by the housing of the torsional vibration damper or more precisely by a section of the housing, where the housing is a component of the secondary side of the torque transmission device. The output part of the overload clutch is the driven flange.

[0006] The input part of the torque transmission device is also commonly referred to as the primary side in technical terms and the output part of the torque transmission device is called the secondary side. The input part functionally belongs to the drive part and is operatively connected thereto, and the output part functionally belongs to the driven part and is operatively connected thereto. The drive part consists of or has the drive device. The driven part can have a clutch and a transmission or other transmission elements and is ultimately equipped with driven wheels. During normal driving operation of the vehicle, a driving torque generated by the drive device is applied on the primary side, i.e., the input part is connected to the drive side. The secondary side is the driven side of the torque transmission device and has transmission elements via which the torque is further transmitted from the torque transmission device to the transmission elements on the driven side. The input side refers to the direction towards the input part or the drive part. The output side refers to the direction towards the output part or the driven part.

[0007] Functionally acting means that components or elements are functionally connected to each other via an acting connection. The acting connection is provided, for example, by elements, structural elements or components formed by elements and / or structural elements. The acting connection is provided, for example, via threaded parts, spring devices or overload clutches, flanges, or elements that engage with each other by form-fitting or force transmission connections.

[0008] The torsional vibration damper basically consists of an input flange, a spring device and the part of the housing connected to the driven flange. The spring device is functionally arranged between the input part and the output part, i.e., between the input flange and the housing, such that the spring device forms a vibration-reducing acting connection between the input part and the output part. Here, the input flange is supported on the spring device via flange wings and the housing is supported on the spring device via a support structure for the spring of the spring device such that they can be torsionally supported relative to each other in a limited manner about the rotational axis of the torque transmission device against the spring action / spring force of the spring device.

[0009] The spring device preferably consists of a plurality of springs or spring groups distributed around the rotational axis. The springs or spring groups are preferably embodied as cylindrical tension springs or arc-shaped tension springs or inserted helical springs. The springs of the spring group are preferably inserted concentrically into each other. The spring chamber is encapsulated by a groove-shaped structure on the housing and / or on the cover of the housing, and optionally, the spring chamber is sealed radially inwards in the direction of the rotational axis by one or more seals or friction linings. This is especially the case when the spring chamber is filled with grease. Preferably, a plurality of springs are arranged distributed in the housing on the circumference around the rotational axis. The flange wings of the input flange abut against one end of the spring. The spring is supported at the other end on a suitable support structure, preferably formed into the housing. In addition, the spring can also be guided by means of a sliding shell made of plastic or sheet metal.

[0010] Here, the input part is formed by an element or by a component. According to the invention, the input part belongs to the primary side, and the input part has, for example, an input flange as a single part or a pulse sensor having an input flange and a sensing unit fixed thereto as a component. The input part is functionally connected to a first connecting element on the drive side. The connecting element is, for example, a bolt, a plate or a flywheel of an internal combustion engine.

[0011] The output part is configured as a component. Here, according to the invention, the output part as a component consists of a housing including a cover and formed by a spring chamber, and alternatively can also contain other elements and structural elements. According to the invention, the output part also includes a driven flange and an overload clutch.

[0012] According to the subject matter of the invention, the overload clutch forms an active connection between the torsional vibration damper and the driven flange, i.e. between the housing or more precisely between housing sections of the housing. The driven flange is preferably connected in a form-fitting manner via a sleeve to a connecting element of the subsequent drive train, for example a pin of a clutch, a pin of a transmission shaft or a differently designed component.

[0013] The axially extending rotational axis is passed through radially transversely to the rotational axis of the torque transmission device, i.e. any radial plane is perpendicularly passed through by the axially extending rotational axis. The rotational axis extends axially in any number of axial planes intersecting the rotational axis. During driving operation, the torque transmission device rotates about the rotational axis, and in addition, the input part and the output part are pivoted relative to each other for vibration reduction.

[0014] In contrast to the known standard mountings of torque transmission devices or torsional vibration dampers known to date, in which the mass of the housing containing the spring belongs to the primary side, i.e. is fixed to the primary side, the flange including the flange wings belongs to the primary side and is operatively connected to the driven flange. In other words, in the torque transmission device or torsional vibration damper according to the invention, the flange belongs to the primary side and the housing is located in the secondary part. Therefore, the flange that interacts with the spring device (which was arranged in the secondary part of the damper in previous solutions) is now the input flange and is connected to the drive, for example to the crankshaft of an internal combustion engine or to an electric motor or the like. As a result, the mass of the housing and the spring device that performs the function of the torsional vibration damper are no longer connected to the primary part, but are accommodated in the secondary part.

[0015] The overload clutch comprises at least two axial supports, at least one friction lining, at least one preload element and at least one friction surface. The axial supports are configured in the shape of an annular disk and are configured in a curved manner in the cross-sectional configuration. The axial supports are axially opposite to each other at the annular gap. At least one of the axial supports is fixed to the driven flange. Alternatively, two axial supports are fixed to the driven flange. Alternatively, one of the axial supports is configured in one piece with the driven flange and with the same material.

[0016] The housing section which is a component of the overload clutch and is in a disc-shaped structure has at least one friction surface, preferably two friction surfaces. The two friction surfaces are axially separated from each other. The friction surface is used for friction contact with another friction partner, for example, for contact with a friction lining. The friction lining is a lining made of paper, fabric, metal material, plastic, or a combination of the above materials or mechanically or chemically coated. The friction lining is constructed, fixed or coated on the friction lining carrier in a form-fitting or materially connected manner or on the friction disk as in the design of the present invention. The friction lining constructed of paper is preferably used in dry applications, that is, not used in applications lubricated with grease or with an oil pool.

[0017] One or more friction linings, friction surfaces, and preloading elements are arranged axially in an annular gap between axial supports concentrically relative to each other and relative to the axis of rotation and are preloaded relative to each other. Here, each friction lining is held on one of the axial supports or the preloading element of the overload clutch in a frictionally connected, force-transmitting connected, or form-fitting connected manner relative to the driven flange. The friction lining is preloaded axially relative to the friction surface of the housing section.

[0018] A design of the present invention provides that the axial support and the driven flange are connected to each other by means of at least one riveted connection, preferably by means of a plurality of riveted connections distributed on the circumference around the axis of rotation. The riveted connection can be manufactured simply and at low cost.

[0019] Another design of the present invention is that the axial supports directly abut against each other in the surface section where the axial supports are connected to the driven flange. Here, one of the axial supports abuts against one side of the driven flange at the rear, preferably on the side of the driven flange facing the input flange. In the region of the connection fixing part, an annular gap is formed between the axial supports so that other components of the overload clutch are installed in the annular gap. By this measure, the axial structural space can be kept very small. Alternatively, it is provided that one of the axial supports is formed by an annular section of the driven flange that is integrally formed with the driven flange. By this measure, the number of individual components of the overload fastening part is reduced.

[0020] A design of the present invention lies in the overload clutch of the torque transmission device, wherein the preloading element is formed by one or more axially acting compression springs, preferably by disc springs, and is preferably supported at one of the axial supports.

[0021] The following design of the present invention is also conceivable, wherein the sleeve is provided with an internal tooth part or an insert provided with an internal tooth part is inserted into the sleeve, and the driven flange corresponds to the second connecting element in a form-fitting manner via the internal tooth part and transmits the driving torque. The tooth part is preferably introduced into the sleeve or the insert by a forming process. Advantageously, an insert is used so that, for example, the wall thickness of the housing can be kept very low and thus advantageously affects its deformation ability, mass, and material distribution. In addition, the form-fitting connection between the sleeve and the connecting element can be advantageously designed by the larger wall thickness at the insert and the teeth of the tooth part so as to transmit a high torque. The insert can be selectively held in the sleeve by a press fit, form fit, and by a material connection part or by a combination of the foregoing methods. The form-fitting connection between the sleeve and the connecting element is preferably formed by a tooth part, for example, by a spline or a fine tooth groove connection part. The sleeve and the insert and their tooth parts are preferably manufactured by deformation or cold forming. Description of the Drawings

[0022] The present invention will be described in detail below based on a plurality of embodiments which are not shown to scale.

[0023] Figure 1 The torque transmission device 1 for transmitting a driving torque from the first connecting element 16 to the second connecting element 17 is shown in a longitudinal section along the rotational axis 21.

[0024] Figure 2 It is shown enlarged Figure 1 detail Z marked therein.

[0025] Figure 3 Another embodiment of the torque transmission device 61 for transmitting a driving torque from the first connecting element 16 to the second connecting element 17 is shown in a longitudinal section along the rotational axis 21.

[0026] Figure 4 It is shown enlarged Figure 3 detail X marked therein.

[0027] Figure 5 Another embodiment of the torque transmission device 70 for transmitting a driving torque from the first connecting element 16 to the second connecting element 17 is shown in a longitudinal section along the rotational axis 21, and

[0028] Figure 6 Another embodiment of the torque transmission device 71 for transmitting a driving torque from the first connecting element 16 to the second connecting element 17 is shown in a longitudinal section along the rotational axis 21. DETAILED DESCRIPTION

[0029] Figure 1 、 Figure 3 、 Figure 5 and Figure 6 : The torque transmission devices 1 and 61 shown by Figure 1 and Figure 3 are constructed substantially identically. The difference lies only in the details of their overload clutches 50 and 60. The torque transmission devices 61, 70 and 71 shown by Figure 3 、 Figure 5 and Figure 6 are constructed substantially identically. The difference lies only in the design of their driven flanges 68 and 69 and the geometry of the axial support 67.

[0030] The torque transmission devices 1, 61, 70, 71 are provided with an input section 2 (in the primary part) with the first connecting element 16 on the drive side, an output section 3 (in the secondary part) with the second connecting element 17 on the driven side, and a torsional vibration damper 4. The input section 2 on the primary side is formed by the input flange 8 of the torsional vibration damper 4.

[0031] The input flange 8 of the primary section is fixed to a first connecting element 16, not shown in detail, by means of a plurality of bolts 29 distributed circumferentially about the axis of rotation 21. Since it is shown in a schematic manner, only one of the bolts 29 can be seen. The first connecting element 16 is, for example, a connecting flange of an electric drive device or a flywheel of an internal combustion engine. The input flange 8 abuts against the respective spring device 7 with a flange wing 9 acting on the spring device 7 on the input side, that is, the input flange 8 has a number of flange wings 9 corresponding to the number of spring devices 7. Since in the Figure 1 , Figure 3 , Figure 5 and Figure 6 schematic manner, only one spring device can be seen. The input flange 8 abuts with the flange wings 9 respectively against the spring ends of the coil springs 32, which spring ends point in the opposite direction to the spring ends on which the coil springs 32 are supported on the housing 10. The assembly 5 of the input section 2 in the primary section is formed by the input flange 8 and a sensing ring 33 of a sensing unit, not shown further, which is connected to the input flange 8. The sensing ring 33 is connected to the input flange 8 by means of a riveted connection 34.

[0032] The torsional vibration damper 4 comprises an input flange 8, a spring device 7 and at least a housing 10.

[0033] A housing section 10a and a cover 13 form the housing 10. The cover 13 and the housing section 10a are materially connected to each other at the radially outer edge 23 by means of a welded joint 30. The housing section 10a is configured as an annular disk bent in a longitudinal section along the axis of rotation 21. The housing section 10a has a rib 10b with a groove-like configuration in its radially outer section. The axially opposite sections of the cover 13 of the housing 10 bulge similarly in a groove-like manner at this location, such that an axially and radially bounded spring chamber 11 is formed by the cover 13 and the housing section 10 at this location.

[0034] A spring device 7 is installed in the spring chamber 11, which spring device is formed in this case by a coil spring 32 and a sliding shell 31. The coil spring 32 is supported at the housing 10 at its end that extends into the schematic illustration and is not visible in the schematic illustration, circumferentially about the axis of rotation 21 or tangentially to the circumferential direction. Based on the schematic illustration, only one of the at least two spring devices 7 of the torsional vibration damper 4 can be seen. Radially inside the spring chamber, a ring 35, preferably a friction ring, is axially clamped between the cover 13 and the input flange 8 under the action of a disc spring 37.

[0035] Figure 1: In a method, not shown, the component 6 of the output part 3 is placed on the input part 2 such that the component is centered relative to the axis of rotation 21 when the radial inner edge 54 of one of the axial support parts 42, 43 is placed radially on one or more members 25. The one or more members 25 are preferably the guide sections 40 on the radial outside of the annular disk 39, which is provided with a plurality of through holes 41 distributed in the circumferential direction, and the bolts of the input flange 8 fixed to the first connecting element 16 engage through the through holes. The annular disk 39 is bent such that the annular disk bridges the axial spacing between the input flange 8 and the driven flange 12.

[0036] The component 6 of the output part 3 in the secondary part is provided with a housing 10, at least one spring chamber 11 for accommodating the spring device 7, and a driven flange 12 connected to the housing section 10a of the housing 10. The housing 10 and the driven flange 12 are operatively connected to each other by an overload clutch 50. The overload clutch 50 is connected to the driven flange 12, and the edge of the annular disk of the housing section 10a of the housing 10 is clamped in the overload clutch 50 in a frictionally connected manner. The driven flange 12 is operatively connected to the second connecting element 17, which is formed by a pin 28. The driven flange 12 is a formed part made of sheet metal and integrally has a sleeve 15, which is provided with an internal tooth section 26. The internal tooth section 26 engages in a form-fitting manner in the external tooth section 38 of the pin 28 to transmit the driving torque. Another ring 36 is tightly clamped axially between the annular disk 39 and the driven flange 12.

[0037] Figure 2 : The overload clutch 50 at least includes two axial support parts 42, 43, friction linings 44, 45, a preloading element 46, and friction surfaces 47, 49. The axial support parts 42, 43 are fixed axially opposite each other on the driven flange 12 at an annular gap 48. The friction surfaces 47, 49 are formed on the housing section 10a. The friction linings 44, 45, the friction surfaces 47, 49, and the preloading element 46 are arranged axially in the annular gap 48 between the axial support parts 42, 43 and are preloaded axially relative to each other. The friction linings 44, 45 are held relative to the driven flange 12 and are preloaded in a frictionally connected manner relative to one of the friction surfaces 47, 49 by means of the preloading element 46.

[0038] The axial support portions 42, 43 and the driven flange 12 are connected to each other by means of a plurality of riveted connection portions 14, and only one of them can be seen due to the way it is shown. That is, the overload clutch 50 is fixed to the driven flange 12 by means of the riveted connection portions. The axial support portions 42 and 43 are provided with flat fixing sections 56 and 57 for this purpose. The axial support portions 42, 43 are directly abutted against each other with the fixing sections 56, 57 respectively, wherein the axial support portion 42 abuts against one side 58 of the driven flange 12 at the rear side here. The first friction lining 44 is pre-tensioned in a frictionally connected manner relative to the first friction surface 47 constructed on the housing section 10a, and the second friction lining 45 is pre-tensioned in a frictionally connected manner in the axial direction towards the first friction lining 44 relative to the second friction surface 49 facing away from the first friction surface 47. The pre-tensioning element 46 is pre-tensioned relative to the first friction lining 44 while being axially supported on the first axial support portion 42. The second friction lining 45 is axially supported on the second axial support portion 43. The pre-tensioning element 46 is formed by a compression spring 59 that acts as a disc spring in the axial direction. The compression spring 59 is axially supported on the first axial support portion 42. The friction lining 44 is fixed to or screwed onto the friction disc 51, wherein the pre-tensioning element 46 is pre-tensioned relative to the side of the friction disc 51 that faces away from the friction lining 44 in the axial direction. The friction lining 44 is materially connected to the friction disc 51. The friction lining 45 is fixed to the axial support portion 43 or alternatively inserted between the axial support portion 43 and the housing section 10a.

[0039] Figure 3 : The assembly 6 of the output portion 3 in the secondary part is provided with a housing 10, at least one spring chamber 11 for accommodating a spring device 7, and a driven flange 12 connected to the housing section 10a of the housing 10. The housing 10 and the driven flange 12 are operatively connected to each other by means of an overload clutch 60. The overload clutch 60 is connected to the driven flange 12, and the annular disc-shaped edge of the housing section 10a of the housing 10 is clamped in the overload clutch 60 in a frictionally connected manner. The driven flange 12 is operatively connected to a second connecting element 17, which is formed by a pin 28. The driven flange 12 is a formed part made of sheet metal and integrally has a sleeve 15, and the sleeve is provided with an internal tooth portion 26. The internal tooth portion 26 engages in a form-fitting manner with the external tooth portion 38 of the pin 28 to transmit the driving torque. Another ring 36 is tightly clamped axially between the input flange 8 and the housing section 10a.

[0040] Figure 4: The overload clutch 60 comprises at least two axial support portions 42, 43, friction linings 62, 63, a preloading element 46, and friction surfaces 47, 49. The axial support portions 42, 43 are fixed to the driven flange 12 axially opposite each other at an annular gap 48. The friction surfaces 47, 49 are formed at the housing section 10a. The friction linings 62, 63, the friction surfaces 47, 49, and the preloading element 46 are arranged axially between the axial support portions 42, 43 in the annular gap 48 and are preloaded axially relative to each other. The friction linings 62, 63 are held relative to the driven flange 12 and are preloaded in a frictionally connected manner relative to one of the friction surfaces 47, 49 by means of the preloading element 46. The friction linings 62, 63 are friction rings which have a friction surface on the surface or are provided with a friction surface.

[0041] The axial support portions 42, 43 and the driven flange 12 are connected to each other by means of a plurality of riveted joints 14, only one of which can be seen due to the way it is shown. That is, the overload clutch 60 is fixed to the driven flange 12 by means of the riveted joints. For this purpose, the axial support portions 42, 43 are provided with flat fixing sections 56 and 57. The axial support portions 42, 43 are directly abutted against each other with the fixing sections 56, 57 respectively, wherein the axial support portion 42 abuts against one side 58 of the driven flange 12 at the rear side here. The first friction lining 62 is preloaded in a frictionally connected manner relative to the first friction surface 47 formed on the housing section 10a, and the second friction lining 63 is preloaded in a frictionally connected manner in the axial direction towards the first friction lining 62 relative to the second friction surface 49 which is opposite to the first friction surface 62. The preloading element 46 is preloaded relative to the first friction lining 62 axially supported on the first axial support portion 42. The second friction lining 63 is axially supported at the second axial support portion 43. The preloading element 46 is formed by a compression spring 59 which acts as a disc spring axially. The compression spring 59 is axially supported at the first axial support portion 42. The friction lining 62 is fixed to a friction disc 64 made of sheet metal in a form-fitting manner, wherein the preloading element 46 is preloaded relative to the side of the friction disc 64 which is axially opposite to the friction lining 62. The form-fitting connection between the friction disc 64 and the friction lining 62 is provided by axial projections 65, wherein each projection engages into a recess 66 of the first friction lining 62 respectively. The friction lining 63 is fixed to the axial support portion 43 or alternatively is placed between the axial support portion 43 and the housing section 10a.

[0042] Figure 5 and Figure 6: The torque transmission devices 70 and 71 are constructed substantially identically. The only difference lies in their driven flanges 68 or 69 (which belong to the torque transmission device 71). The assembly 6 of the output part 3 in the secondary part is provided with a housing 10, at least one spring chamber 11 for accommodating the spring device 7, and a driven flange 68 or 69 connected to the housing section 10a of the housing 10. The housing 10 and the driven flange 68 or 69 are operatively connected to each other via an overload clutch 60. The overload clutch 60 is connected to the driven flange 68 or 69, and the annular disk-shaped edge of the housing section 10a of the housing 10 is clamped in the overload clutch 60 in a frictionally connected manner. The driven flange 68 or 69 is operatively connected to a second connecting element 17, which is formed by a pin 28.

[0043] In the overload clutch 60, the corresponding driven flange 68 or 69 forms one of the axial support parts 68 or 69, that is, the corresponding axial support part 68 or 69 is simultaneously the corresponding driven flange 68 or 69. The overload clutch 60 is formed by at least two axial support parts 67 and 68 or 69, friction linings 62, 63, a preloading element 46, and friction surfaces 47, 49. The axial support parts 67 and 68 or 69 are fixed axially relative to each other at the corresponding driven flange 68 or 69 at an annular gap 48. The friction surfaces 47, 49 are configured on the housing section 10a. The friction linings 62, 63, the friction surfaces 47, 49, and the preloading element 46 are arranged axially in the annular gap 48 between the axial support parts 68, 69 and are preloaded axially relative to each other. The friction linings 62, 63 are held relative to the driven flange 68 or 69 and are preloaded relative to one of the friction surfaces 47, 49 in a frictionally connected manner by means of the preloading element 46.

[0044] The axial support part 67 and the corresponding driven flange 68 or 69 are connected to each other by means of a plurality of riveted joints 14, and only one of them can be seen due to the way it is shown. That is, the overload clutch 60 is fixed to the driven flange 68 or 69 by means of the riveted joint 14. The axial support part 67 is provided with a flat fixing section 56 for this purpose, and the corresponding driven flange 68 or 69 has a flat fixing section 57. The axial support part 67 and the corresponding driven flange 68 or 69 are directly abutted against each other with the fixing sections 56, 57 respectively, wherein the axial support part 67 abuts against one side 58 of the driven flange 68 or 69 at the rear side here. The first friction lining 62 is pre-tensioned in a frictionally connected manner relative to the first friction surface 47 constructed on the housing section 10a, and the second friction lining 63 is pre-tensioned in a frictionally connected manner in the axial direction towards the first friction lining 62 relative to the second friction surface 49 facing away from the first friction surface 62. The pre-tensioning element 46 is pre-tensioned relative to the first friction lining 62 while being axially supported on the first axial support part 67. The second friction lining 63 is axially supported at the second axial support part 43. The pre-tensioning element 46 is formed by a compression spring 59 that acts as a disc spring in the axial direction. The compression spring 59 is axially supported on the first axial support part 67. The friction lining 62 is fixed to the friction disc 64 in a form-fitting manner, wherein the pre-tensioning element 46 is pre-tensioned relative to the side of the friction disc 64 facing away from the friction lining 62 in the axial direction. The form-fitting connection between the friction disc 64 and the friction lining 62 is provided by axial protrusions 65, wherein each protrusion engages into a recess 66 respectively. The friction lining 63 is fixed to the axial support part 68 or alternatively placed between the axial support part or the axial flange 68 and the housing section 10a.

[0045] In a method not shown, the assembly 6 of the output part 3 is placed on the input part 2 such that the assembly is centered relative to the rotational axis 21 when the hollow cylindrical section 55 extending axially in the direction towards the input flange 8 is placed radially on one or more components 25. The hollow cylindrical section 55 is connected to the fixing section 56 of the axial support part 67 radially inside and is integrally constructed therewith. The one or more components 25 are preferably the radially outer guiding sections 40 of the annular disc 39, and the annular disc is provided with a plurality of through holes 41 distributed in the circumferential direction, and the bolts 29 of the input flange 8 fixed to the first connecting element 16 pass through the through holes and engage. The annular disc 39 is bent such that the annular disc bridges the axial spacing between the input flange 8 and the driven flange 68 or 69.

[0046] Figure 5:The driven flange 68 is a formed part made of sheet metal and has integrally a sleeve 73 oriented in the direction of the input flange 8, into which the insert 27 is inserted with its internal teeth 26. The internal teeth 26 engage form - fit with the external teeth 38 of the pin 28 for transmitting the driving torque. Another ring 36 is clamped tightly axially between the input flange 8 and the housing section 10a.

[0047] Figure 6 :The driven flange 69 has a disk 76 made of sheet metal, on which a sleeve 74 oriented in the direction of the input flange 8 is fixed form - fit. The sleeve is provided with teeth on the outside and is clamped form - fit with the tooth configuration 75 of the disk 76. The sleeve 74 is provided with internal teeth 26, which engage form - fit with the external teeth 38 of the pin 28 for transmitting the driving torque. Another ring 36 is clamped tightly axially between the input flange 8 and the housing section 10a.

[0048] List of Reference Signs

[0049] 1 Torque transmission device

[0050] 2 Input section

[0051] 3 Output section

[0052] 4 Torsional vibration damper

[0053] 5 Components of the input section

[0054] 6 Components of the output section

[0055] 7 Spring device

[0056] 8 Input flange

[0057] 9 Flange wing of the input flange 10 Housing

[0058] 10a Housing section

[0059] 10b Bulge

[0060] 11 Spring chamber

[0061] 12 Driven flange

[0062] 13 Cover of the housing

[0063] 14 Riveted connection

[0064] 15 Sleeve

[0065] 16 First connecting element

[0066] 17 Second connecting element

[0067] 18 First through - hole

[0068] 19 Second through-hole

[0069] 20 Unassigned

[0070] 21 Axis of rotation

[0071] 22 Unassigned

[0072] 23 Radial outer edge

[0073] 24 Unassigned

[0074] 25 Component

[0075] 26 Internal tooth part

[0076] 27 Insert

[0077] 28 Pin

[0078] 29 Bolt

[0079] 30 Welding part

[0080] 31 Sliding housing

[0081] 32 Helical spring

[0082] 33 Sensing ring

[0083] 34 Riveted connection part

[0084] 35 Ring

[0085] 36 Ring

[0086] 37 Disc spring

[0087] 38 External tooth part

[0088] 39 Annular disc

[0089] 40 Guide section

[0090] 41 Through-hole

[0091] 42 Axial support part

[0092] 43 Axial support part

[0093] 44 Friction lining

[0094] 45 Friction lining

[0095] 46 Preloading element

[0096] 47 First friction surface

[0097] 48 Annular gap

[0098] 49 Second friction surface

[0099] 50 Overload clutch 51 Friction disc

[0100] 52 - 53 - 54 Inner edge of the axial support

[0101] 55 Section of the axial support

[0102] 56 Fixed section

[0103] 57 Fixed section

[0104] 58 One side of the driven flange

[0105] 59 Compression spring

[0106] 60 Overload clutch

[0107] 61 Torque transmission device

[0108] 62 Friction lining

[0109] 63 Friction lining

[0110] 64 Friction disc

[0111] 65 Bump

[0112] 66 Recess

[0113] 67 Axial support

[0114] 68 Driven flange

[0115] 68a Axial support

[0116] 69 Driven flange

[0117] 69a Axial support

[0118] 70 Torque transmission device

[0119] 71 Torque transmission device

[0120] 72 Axial support

[0121] 73 Sleeve

[0122] 74 Sleeve

[0123] 75 Tooth configuration

[0124] 76 Disc

Claims

1. A torque transmission device (1, 61, 70, 71), the torque transmission device being used for transmitting a driving torque between a first connecting element (16) of the torque transmission device (1, 61, 70, 71) and a second connecting element (17) of the torque transmission device (1, 61, 70, 71), the torque transmission device (1, 61, 70, 71) having an input part (2) provided with the first connecting element (16) on the drive side, and the torque transmission device (1, 61, 70, 71) having an output part (3) provided with the second connecting element (17) on the driven side, the torque transmission device having a torsional vibration damper (4) and an overload clutch (50, 60), wherein: the torsional vibration damper (4) is functionally arranged between the input part (2) and the output part (3) and has at least one spring device (7), wherein the input part (2) and the output part (3) are pivotable relative to each other in a limited manner about the rotation axis (21) of the torque transmission device (1, 61, 70, 71) against the action of the spring device (7), the output part (3) is functionally provided with a driven flange (12) which is operatively connected to the second connecting element (17), wherein the overload clutch (50, 60) is arranged in a functionally effective manner between the torsional vibration damper (4) and the output flange (12), It is characterized in that the input part (2) has at least one input flange (8) which is operatively connected to the first connecting element (16) and which bears against the spring device (7) on the input side of the spring device (7), The output part (6) is provided with a housing (10), at least one spring chamber (11) for accommodating the spring device (7) and a driven flange (12, 68, 69) operatively connected to the housing (10), wherein the driven flange (12, 68, 69) is operatively connected to the second connecting element (17), the spring chamber (11) is at least partially enclosed by the housing (10) and a cover (13) of the housing (10) which is fixed to the housing (10), the spring device (7) is accommodated in the spring chamber (11) and is supported on the driven side on the housing (10), - wherein the overload clutch (50, 60) is connected to the output flange (12, 68, 69) and at least one housing section (10a) of the housing (10) connected to the housing (10) is clamped in the overload clutch (50, 60) in a frictionally connected manner.

2. The torque transmission device (1, 61, 70, 71) according to claim 1, characterized in that The overload clutch (50, 60) comprises at least two axial supports (42, 43), at least one friction lining (44, 45, 62, 63), at least one preload element (46) and at least one friction surface (47, 49), wherein: - the axial supports (42, 43, 67, 68a, 69a) are connected to the driven flanges (12, 68, 69) axially opposite to each other at the annular gap (48), - the at least one friction surface (47, 49) is formed on the housing section (10a), - the at least one friction lining (44, 45, 62, 63), the at least one friction surface (47, 49) and the preload element (46) are arranged in an annular gap (48) between the axial supports (42, 43, 67, 68a, 69a) and are axially preloaded against one another, The at least one friction lining (44, 45, 62, 63) is held relative to the driven flange (12) and is preloaded relative to at least one friction surface (47, 49) in a frictionally connected manner by means of the preload element (46).

3. The torque transmission device (1, 61, 70, 71) according to claim 2, characterized in that At least one axial support (42, 43, 67) and the driven flange (12, 68, 69) are connected to one another by means of at least one riveted connection (14).

4. The torque transmission device (1, 61) according to claim 3, characterized in that The axial supports (42, 43, 68a, 69a) bear directly against one another and an axial support (42, 43, 68a, 69a) bears against one side (58) of the output flange (12, 68, 69) at the rear.

5. The torque transmission device (70, 71) according to claim 1 or 2, characterized in that One of the axial supports (68a, 69a) is formed by an annular section of the driven flange (68, 69) formed on the driven flange (68, 69) and is connected to the driven flange (68, 69) in a one-piece manner by means of a uniform material.

6. The torque transmission device (1, 61, 70, 71) according to claim 1, 2, 3 or 4, characterized in that A first friction lining (44, 62) is preloaded in a frictionally connected manner relative to a first friction surface (47) constructed on the housing section (10a), and a second friction lining (45, 63) is preloaded in an axial direction in a direction toward the first friction lining (44, 62) relative to a second friction surface (49), the second friction surface facing away from the first friction surface (47), wherein the preload element (46) is axially supported on a first axial support portion (42, 67) of the axial support portion (42, 43, 67, 68a, 69a) to be preloaded relative to the first friction lining (44, 62), and the second friction lining (45, 63) is axially supported on a second axial support portion (43, 68a, 69a) of the axial support portion (42, 43, 67, 68a, 69a).

7. The overload clutch (50, 60) of the torque transmission device (1, 61, 70, 71) according to claim 2, characterized in that: The preload element (46) is formed by at least one axially acting compression spring (59).

8. The overload clutch (50, 60) according to claim 7, characterized in that: The compression spring (59) is axially supported at a first axial support portion (42, 67) of the axial support portions (42, 43, 67, 68a, 69a).

9. The overload clutch (50, 60) according to claim 2, characterized in that: At least one friction lining (44) of the friction linings (44, 45, 62, 63) is held on a friction disk (51), wherein the preload element (46) is preloaded relative to a side of the friction disk (51) facing away from the friction lining (44) in the axial direction.

10. The overload clutch (50, 60) according to claim 8, characterized in that At least one friction lining (62) of the friction linings (44, 45, 62, 63) is held on the friction disk (51) in a form-fitting manner.

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