Torque transmission device with torsional vibration dampers

Abstract

The invention relates to a torque transmission device (1) for transmitting first drive torques about an axis of rotation (21) between a first connection element (16) assigned to the drive side of the torque transmission device (1) and a second connection element (17) assigned to the output side of the torque transmission device (1), the torque transmission device (1) having an input assembly (2) and the torque transmission device (1) having an output assembly (3) connected to the second connection element (17) on the output side, as well as having a first torsional vibration damper (4) and a second torsional vibration damper (6).

Description

Field of the invention

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

[0002] In motor vehicle drivetrains, the task of the torque transmission device is to transfer the torque generated by a prime mover to the transmission with as little vibration as possible. The torsional vibration dampers covered by the application belong to the class also known in technical terms as "reversed dampers." Such a torque transmission device for a hybrid vehicle is known from DE 10 2017 127 525 A1. Another torque transmission device is described in DE 10 2019 110 130 A1. Description of the invention

[0003] The object of the invention is to create a torque transmission device with a torsional vibration damper that can be manufactured and assembled easily and cost-effectively.

[0004] The problem is solved according to the subject matter of claim 1 of the present patent claims.

[0005] According to the invention, a torsional vibration damper designed as a “reversed damper” is combined with a pre-damper.

[0006] In common designs, the spring characteristic of the first torsional vibration damper is always superimposed by a basic friction. To effectively decouple the drivetrain when idling, pre-isolation with as little friction as possible is required. According to the invention, this task is achieved with the second torsional vibration damper, which acts as a pre-damper. The pre-damper is referred to below as the second torsional vibration damper. The second torsional vibration damper is connected in series with the main vibration damper in the chain of action, starting from the primary side and moving to the secondary side of the torque transmission device, and usually acts upstream of the first torsional vibration damper.

[0007] Hybrid transmissions pose new challenges for damper systems. A critical operating point is when the combustion engine is idling while the electric motor is off-load or charging with light load. Series, series-parallel, and power-split hybrid applications are particularly prone to idle rattle at these operating points. To further reduce fuel consumption, the belt drive side of the combustion engine is becoming increasingly lighter. This is especially true for hybrid vehicles, where the ancillary components are powered electrically rather than by the combustion engine. To restore balance in the drivetrain, the mass inertia on the other side of the crankshaft must also be reduced.

[0008] The power input of the torque transmission device or torsional vibration damper is often referred to as the primary side in technical terms, and the output of the torque transmission device or torsional vibration damper is referred to as the secondary side. The input is functionally assigned to a drive and is operatively connected to this. The output is functionally assigned to an output and is operatively connected to this. The drive consists of a prime mover or has this prime mover. The output can have a clutch, a converter and a gearbox or other transmission elements and is ultimately assigned to the driven vehicle wheels. During normal vehicle operation, the drive torques generated by the prime mover are present on the primary side, which means that the input is connected to the drive side. The secondary side is the output side of the torque transmission device. The input side means that the input or output is connected to the input or output.Towards the input. Output side means towards the output or output.

[0009] Functionally effective means that assemblies or components are operatively connected to one another via an operative connection. The operative connection is provided, for example, by a component, structural element, or an assembly composed of components and / or structural elements, through which drive torques are transmitted, for example. An operative connection is provided, for example, by a screw connection, a spring device, a slip or overload clutch, a flange, or otherwise by form fit, friction fit, force fit, or by a combination of at least two meshing elements.

[0010] In the known standard installations of torque transmission devices or torsional vibration dampers, the mass of the housing with the spring device is assigned to the primary side. The flange with the flange vanes engaging the spring device is assigned to the secondary side and is operatively connected to the output hub or a clutch plate. Deviating from this, in the reverse torque transmission devices or torsional vibration dampers according to the invention, the flange engaging the first spring device is assigned to the primary side and connected to a crankshaft of an internal combustion engine or to an electric motor, etc. Consequently, the flange interacting with the spring device, which was located in the secondary section of previous dampers, is now connected to the drive and is referred to below as the input flange. The housing is located in the secondary section.The mass of the housing and the first spring device that performs the function of the torsional vibration damper are no longer accommodated in the primary part, but in the secondary section.

[0011] The flange wings of the input flange each engage in a gap between two springs or spring assemblies of the first torsional vibration damper. This gap allows the respective flange wings of the input flange a pivoting range in each circumferential direction, known as the clearance angle. Within this pivoting range, the respective flange wings can pivot within the gap without contact with the springs of the spring assembly—meaning that the first torsional vibration damper is not effective in this operating state.

[0012] The pre-damper, which is referred to as the second damping device, acts within this clearance angle. The intermediate flange has a number of flange wings corresponding to the number of flange wings of the input flange. The flange wings of the intermediate flange are wider around the circumference than the flange wings of the input flange. Each flange wing of the intermediate flange also engages in the gap formed between the springs of the first spring device of the first vibration damper. However, it fills the width of the gap circumferentially completely without a clearance angle or almost completely with a very small clearance angle, so that each flange wing of the intermediate flange is supported in both circumferential directions by the springs of the first torsional vibration damper that close off the respective gap.

[0013] The torque transmission device is equipped with at least one slip clutch. The slip clutch creates a frictional connection between the intermediate flange and the housing on the secondary side due to static friction. The slip clutch(es) are designed for two operating states. One operating state ensures an axial force- and friction-locking static friction connection between the intermediate flange and the housing, in which the intermediate flange and the housing are held together by static friction, immobile relative to one another. In this operating state, the torques referred to as second drive torques act, e.g. during idling, until a breakaway torque is reached, after which, in a second operating state, the friction disc of the intermediate flange and the housing or a component supported on the housing can be pivoted against each other about the axis of rotation, rubbing against each other.The breakaway torque is the torque about the rotational axis at which static friction changes to sliding friction. The value of the breakaway torque is higher than the lowest value of the initial drive torque. Therefore, the static friction between the intermediate flange and the output assembly changes to sliding friction upon breakaway. In this case, the clutch's friction discs slip frictionally relative to a friction surface assigned to the housing. The adhesion underlying static friction is a state of rest in which the actual static friction force is always equal and opposite to the external forces acting on it, generated by the torques. Neither wear nor energy loss occurs. Adhesion is a combination of positive engagement due to roughness and molecular force engagement due to molecular forces of attraction, i.e., adhesion.Sliding friction occurs at the friction surfaces between the respective friction disc and the friction ring and / or the housing, which pivot relative to each other. The sliding friction force is lower than the static friction force. The breakaway torque is therefore the limiting torque around the rotational axis at which the static friction between components of the input assembly and the output assembly transitions to sliding friction, causing the input flange and the housing to pivot relative to each other.

[0014] The second drive torques are therefore smaller than the first drive torques. The breakaway torque represents a threshold value between the first and second drive torques and is the drive torque at which the static frictional engagement of the friction discs with the friction rings is released, and the friction surfaces of the friction discs and friction rings move relative to each other by pivoting around the rotational axis.

[0015] The friction surface of the intermediate flange is formed on a friction disc. Alternatively, according to a preferred variant, the intermediate flange has two friction discs, with each of the friction discs being assigned at least one friction surface that corresponds to one or more friction surfaces assigned to the housing. One embodiment of the invention provides that the two friction discs are connected to each other axially and rotationally fixed, i.e., rigidly, via connecting means. According to a preferred embodiment of the invention, the friction discs are riveted together using stepped bolts.

[0016] Both friction discs have circumferentially distributed first spring windows, in which the springs of the second spring device are supported in a first tangential or first circumferential direction. The input flange is arranged between the friction discs. The input flange is provided with second spring windows, in which the springs of the second spring device are supported in a direction opposite to the first direction.

[0017] When two friction discs are used, the input flange also features guideways designed as elongated holes. The connecting elements of the friction discs are each guided between two stops in the guideways. Each of the stops is formed by an inner contour of the guideway that limits the guideway in a circumferential direction. The clearance angle through which the input flange can pivot relative to the intermediate flange or the housing under the action of the second drive torque is predetermined by the distance between the stops in the respective guideway. As a result, the input flange can pivot between the friction discs against the action of the springs of the second spring device with either no friction or low friction. The pitch of the compression springs is designed such that the pre-damper ensures sufficient isolation of the excitations during idle and other low-load operating points.

[0018] After overcoming the clearance angle, the connecting elements are not yet in full contact with their respective guideways. The respective flange wing of the input flange first strikes one or more of the springs of the first spring device that define the gap and are preferably designed as arc springs, deforming them slightly. The springs of the second spring device are selected so that they do not lie in a block. If the second drive torques are exceeded, the respective flange wing of the input flange strikes the arc springs. The distance between the spacer bolts (connecting element) in the respective guideway is adjusted so that the connecting element and the guideway only reach a stop shortly after the flange wings of the input flange have begun to transmit the higher first drive torques. The intermediate flange is then pivotally carried by the input flange.

[0019] The spring forces of the springs or spring assemblies of the first spring assembly assigned to the main damper are higher than the spring forces of the springs or spring assemblies of the second spring assembly of the pre-damper. The first torsional vibration damper operates in a driving condition in which the first drive torques are applied to the torque transmission device.

[0020] The first torsional vibration damper preferably consists of a plurality of springs or spring assemblies distributed around the axis of rotation, which are preferably designed as cylindrically drawn or arcuately drawn or inserted coil springs. The springs of a spring assembly are preferably inserted concentrically into one another. The spring chamber is encapsulated by groove-shaped formations on the housing and / or on the cover of the housing and is sealed radially inwardly in the direction of the axis of rotation with one or more seals or friction linings. This is particularly the case when the spring chambers are filled with grease. Preferably, a plurality of springs are arranged distributed around the circumference of the housing around the axis of rotation. The flange wings of the input flange rest against one end of the springs after overcoming a clearance angle. The other end of the springs is supported on suitable support structures, preferably molded into the housing.The springs designed as compression springs can also be guided by means of plastic sliding shells.

[0021] The input is formed from a single component or assembly. The input is assigned to the primary side and comprises, for example, the input flange as a single part or an assembly with the input flange. The input is functionally connected to the first connecting element on the drive side. Connecting elements include, for example, screws, plates, or flywheels of combustion engines.

[0022] The output is formed from a single component or assembly. The output is preferably formed as an assembly consisting of the housing with the cover and the spring chamber. Alternatively, it may contain additional components and elements or may contain additional assemblies such as a centrifugal pendulum device. The output includes the output flange, which is preferably connected via a hub with a positive fit, e.g., a coupling pin, a pin of a transmission shaft, or another connecting element of the downstream drive train.

[0023] Radial is directed perpendicular to the rotational axis of the torque transmission device, meaning that any radial plane is perpendicularly traversed by the axially aligned rotational axis. The rotational axis is thus defined as axially aligned, regardless of its actual position in space. During operation, the torque transmission device rotates as a whole around the rotational axis. Furthermore, the input and output pivot relative to each other in both directions around the rotational axis against the resistance of the spring devices to dampen vibrations.

[0024] The intermediate flange is centered and axially positioned via one of the friction rings in or on the drive-side housing cover. A second friction ring is positioned on the transmission-side cover. A disc spring rests on the cover and the friction ring. This holds the flanges in a defined axial position. At the same time, a basic friction is generated that is not superimposed on the pre-damper characteristic curve, but only acts in the area of ​​the main damper characteristic curve. The level of friction can therefore be tailored to the requirements of other operating points. If no basic friction is required in the system, the use of a very weak disc spring is recommended to hold the pre-damper and the input flange axially in a defined position. Description of the characters

[0025] The invention is explained in more detail below using an exemplary embodiment in views not drawn to scale. - Fig. 1 shows a torque transmission device 1 in a longitudinal section along a rotation axis 21. - Fig. 2 shows the Fig. 1 shows the torque transmission device 1 in another further longitudinal section along the axis of rotation 21. - In Fig. 2a is the Fig. 2 framed detail Z shown enlarged. - Fig. 3 shows a section of the input assembly 2 of the torque transmission device 1. - Fig. Figure 4 shows a view of the input assembly 2, in which the second friction disc 27 is not visible, looking towards the flanges 8 and 43. - Fig. 5 shows a view of the torque transmission device 1, in which, however, the cover 13 has been omitted, from the direction of the primary side towards the secondary side.

[0026] Fig. 1 and Fig. 2 - The Fig. 1 and Fig. 2 shows a torque transmission device 1 for transmitting drive torque from a first connecting element 16 to a second connecting element 17, illustrated in a longitudinal section along the rotational axis 21. The first connecting element 16 is illustrated only symbolically. The second connecting element 17 is, for example, a gear shaft or a pin 28 for connection to a coupling (not illustrated). The torque transmission device 1 is provided with an input assembly 2 (in the primary section) assigned to the first connecting element 16 on the drive side and with an output assembly 3 (in the secondary section) assigned to the second connecting element 17 on the output side, as well as with a first torsional vibration damper 4 and a second torsional vibration damper 5.

[0027] The input assembly 2 is formed by an input flange 8, an intermediate flange 18, two friction discs 24 and 27, the second torsional vibration damper 5, and two slip clutches 44 and 45, and possibly a third slip clutch 46. The second torsional vibration damper 5 acts as a pre-damper to the first torsional vibration damper 4. The first torsional vibration damper 4 is connected by the flange wing 9 (see Fig. 2) of the input flange 8, by at least one first spring device 6 ( Fig. 1) and by a spring chamber 11 enclosed by the housing 10 of the output assembly 3. The input flange 8 of the primary section is fastened to the first connecting element 16 (not shown in detail) by means of several screws 29 distributed around the circumference of the rotation axis 21. Due to the nature of the illustration, only one of the screws 29 is visible. The first connecting element 16 is, for example, a connecting flange of an electric drive device or a flywheel of an internal combustion engine.

[0028] The output assembly 3 is formed from a housing 10, the first spring device 6, and an output flange 12. A spring chamber 11, in which first coil springs 32 and sliding shells 31 of the first spring device 6 are received, is delimited by a curvature 10b of a housing section 10a and by the cover 13 of the housing 10. The output flange 12 is connected to the housing section 10a of the housing 10 via a riveted connection 14 formed from several rivets 20. The housing section 10a and a cover 13 form the housing 10. The cover 13 and the housing section 10a are integrally connected to one another by a weld seam 30. The housing section 10a is designed as a multi-cranked circular disk, viewed in longitudinal section along the rotation axis 21, which has a through-opening with a radially inner edge 22. In its radially outer section, the housing section 10a has a groove-like curvature 10b.The axially opposite section of the cover 13 of the housing 10 is curved in a similar groove-like manner at this point, so that the axially and radially delimited spring chamber 11 is formed by the cover 13 and the housing section 10a at this point. The first spring device 6 is housed in the spring chamber 11, which in this case is formed by coil springs 32 and sliding shells 31. The coil spring 32 is supported at its end projecting into the image plane and not visible in the illustration on the housing 10 in a preloaded manner in the circumferential direction about the axis of rotation 21 or tangentially to the circumferential direction, just as at the spring end 33 visible in the drawing. Due to the illustration, only a first coil spring 32 of at least two coil springs of the second torsional vibration damper 4 is visible. Radially inward, the spring chamber 11 is protected and / or sealed by two friction rings 35 and 36.The friction ring 35 is axially clamped between the cover 13 and the input flange 8 under the action of a disc spring 37. The second friction ring 36 is axially supported between the input flange 8 and the housing section 10a. It is assumed that the spring chamber 11 is provided with lubricating grease (not shown).

[0029] The housing 10 or housing section 10a and the output flange 12 are connected to each other by several riveted joints 14 arranged circumferentially around the rotation axis 21. Only one of the riveted joints 14 is visible in the illustration.

[0030] The output flange 12 is operatively connected to the second connecting element 17, which is formed by a pin 28. The output flange 12 is a formed part made of sheet metal and has a one-piece hub 15 provided with internal teeth 26. The internal teeth 26 engage positively with external teeth 38 of the pin 28 to transmit the drive torque.

[0031] In a method not shown, the output assembly 3 is placed with the radially inner edge 22 onto the input assembly 2 in such a way that, upon placement, the output assembly is radially centered relative to the rotational axis 21 by one or more components 25. The component(s) 25 is / are preferably a circumferential annular disc(s) 39, which, on the annular section adjacent to the input flange 8, is provided with a plurality of second through holes 41 distributed around the circumference and aligned with the through holes 40. The screws 29 of the input flange 8 fastened to the first connecting element 16 extend through the through holes 40 and 41.

[0032] Fig. 2a - In Fig. Figure 2a shows, in particular, the details of the slip clutches 44, 45, and 46. The first slip clutch 44 is formed by the first friction disc 24 and the first friction ring 35 with the disc spring 37. The first friction disc 24 corresponds to the intermediate flange 18. The second slip clutch 45 is formed by the second friction disc 27 and the second friction ring 36. The third slip clutch 36 is formed between the friction disc 36 and the housing. The friction discs 24 and 27 are axially supported on one another via the spacer bolts 42 and are held at a distance at least equal to or greater than the axial thickness of the input flange 8 and are clamped between the friction rings 35 and 36 under the action of the disc spring 37. The disc spring 37 is supported axially on the cover 10c of the housing on one side and axially on the first friction ring 35 on the other side. The second friction ring 36 is axially supported on the housing portion 10a of the housing.The first friction disc 24 is provided with at least a first friction surface 24a. The second friction surface 35a is formed on the friction ring 35, wherein the first friction surface 24a and the second friction surface 35a form a first friction pairing, i.e. are in frictional engagement or frictional contact with one another. The second friction disc 27 has a first friction surface 27a and is in a first friction pairing with a second friction surface 36a of the friction ring 26. Alternatively or simultaneously, the friction ring 36 is provided with the third friction surface 36b, which is formed between the friction ring 36 and the housing 10, is in frictional contact with a friction surface 10d on the housing and forms a third friction pairing. Depending on the operating conditions, such as operating temperatures, all or some of the friction pairings react independently of one another as a slip clutch or one, two orthree of the slip clutches 44, 45, 46 react together as a multiple slip clutch.

[0033] Fig. 2 and Fig. 5 - The input flange 8 projects radially with a flange wing 9 between each two circumferentially adjacent coil springs 32 of the first spring device 6. The intermediate flange 18 projects radially with a flange wing 18a between each two circumferentially adjacent coil springs 32 of the first spring device 6.

[0034] Fig. 3 - Fig. 3 shows a section of the input assembly 2, which has an input flange 8 and the second torsional vibration damper 5. The input flange 8 is simplified without the hole pattern of the Fig. 1 and with only one flange wing 9. The second torsional vibration damper 5 is formed by the input flange 8, by the second spring device 7 and by the intermediate flange 18. Furthermore, the input assembly 2 can also be provided with shielding plates 19, which are connected to the input flange 8 with hollow rivet connections 23. The intermediate flange 18 has two friction disks 24 and 27. The first friction disk 24, which has a number of flange wings 18a corresponding to the number of flange wings 9 of the input flange 8, is arranged axially on a first flank 8a of the input flange 8 next to the input flange 8. The first friction surface 24a is formed on the first friction disk 24. The second friction disc 27 is arranged axially next to the input flange 8 on a second flank 8b of the input flange 8 facing away from the first flank 8a.The second friction surface 27a is formed on the second friction disc 27. The friction discs 24 and 27 are axially connected to one another by means of connecting elements designed as spacer bolts 42 and are held axially fixedly at a defined axial distance from one another. This distance is maintained by the axial length of the shaft 42a of the spacer bolt 42, to whose bolt shoulders 42b the friction discs 24 and 27 are attached and are each held firmly in place by means of a rivet head 42c of the spacer bolt 42.

[0035] To connect the friction discs 24 and 27, each of the spacer bolts 42 axially passes through a guide track 43 of the input flange 8. The respective Fig. 3 The guideway 43, which is only shown in half due to the way it is shown, is an elongated hole curved along a circumferential line running around the axis of rotation 21.

[0036] The second spring device 7 comprises helical springs 7a designed as compression springs. Each of the helical springs 7a is accommodated in a window-like spring receptacle 7b and supported in another spring receptacle of the input flange 8, not visible in the illustration.

[0037] Fig. 4 - The input flange 8 and the intermediate flange 18 can each pivot relative to one another by a defined second pivot angle beta around the rotation axis against the spring-elastic resistance of the second torsional vibration damper 5. The second torsional vibration damper 5 has the second spring device 7. The second spring device 7 is formed by second coil springs 7a distributed circumferentially around the rotation axis 21.

[0038] Fig. 3 and Fig. 5 - How Fig. 5, the respective flange wing 9 engages in the gap 34 formed between two spring ends 33. In this gap, the respective flange wing 9 of the input flange 8 is in a central position M without load. In this central position M, the respective flange wing 9 lies opposite the spring ends 33 of two circumferentially adjacent first coil springs 32 at a gap 34a, each without contact. Each gap 34a defines a clearance angle Beta, around which the flange wing 9 can be moved from the central position M without contact with a spring end 33 in one circumferential direction A or B (cf. Fig. 5) is pivotable about the rotation axis. The length of the guideway 43, measured on a circumferential path, is adjusted to the clearance angle Beta, taking into account the dimensions of the flanges 9 and 18a, around which the flanges 9 and 18a can freely pivot relative to each other. The respective flange wing 18a of the intermediate flange 18 also engages in the gap 34 and is supported by the spring ends 33, whose spring forces are overall greater than the spring forces of the springs 7a of the Fig. 3 shown second spring device 7. As can be seen Fig. 3, the spacer bolt 42 in the center position M is located circumferentially opposite a stop 43a defined by the end of the guide track 43. The travel of the respective spacer bolt 42 from the center position M to the stop 43a of the guide track 43 is designed slightly larger than the travel defined for the flange 9 by the clearance angle alpha, within which the flange wing 9 can be pivoted selectively in one or the other circumferential direction toward one of the spring ends 33 (cf. Fig. 5). If the respective flange wing 9 hits the springs 32, the helical spring 32 is initially compressed at continuously higher drive torques until the distance bolt 42 in the guideway 43 hits the stop 43a and the intermediate flange 18 with the input flange 8 is pivoted about the axis of rotation, thereby eliminating the static friction of the friction clutches and pivoting the friction discs 24 and 27 relative to the friction rings about the axis of rotation within a damping angle alpha. The damping angle alpha is Fig. 5 not drawn to scale and depends on the torques and spring characteristics of the coil springs 32. Reference symbol 1 torque transmission device 2 Input module 3 Output module 4 first torsional vibration damper 5 second torsional vibration damper 6 first spring device 7 second spring device 7a Coil spring of the second spring device 8 Input flange 8a first flank of the input flange 8b second flank of the input flange 9 Flange wing of the input flange 10 housings 10a Housing section 10b Curvature 10c Cover of the housing 10d Friction surface on the housing 11 Spring chamber 12 Output flange 13 Housing cover 14 riveted joint 15 Hub 16 first connection element 17 second connecting element 18 Intermediate flange 18a Flange wing of the intermediate flange 19 Shielding plate 20 rivets 21 axis of rotation 22 radial inner edge 23 Hollow rivet connection 24 first friction disc 24a first friction surface of the first friction disc 25 component 26 internal gearing 27 second friction disc 27a first friction surface of the second friction disc 28 cones 29 screws 30 Weld seam 31 sliding shell 32 first coil spring 33 first spring end of the first coil spring 34 Gap between the spring ends 34a gap 35 first friction ring 35a second friction surface of the first friction ring 36 second friction ring 36b third friction surface of the first friction ring 36a second friction surface of the second friction ring 37 Disc spring 38 external gearing 39 Ring disc 40 first through hole 41 second through hole 42 spacer bolts 42a Shaft of the spacer bolt 42b bolt heel 42c Rivet head of the spacer bolt 43 guideway 43a Stop in the guideway 44 first slip clutch 45 second slip clutch 46 third slip clutch A first circumferential direction Alpha first swivel angle B second circumferential direction Beta second swivel angle M middle position QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2017 127 525 A1

[0002] DE 10 2019 110 130 A1

[0002]

Claims

[1] Torque transmission device (1) for transmitting first drive torques about a rotational axis (21) between a first connection element (16) assigned to the drive side of the torque transmission device (1) and a second connection element (17) assigned to the output side of the torque transmission device (1), the torque transmission device (1) with an input assembly (2) and the torque transmission device (1) with an output assembly (3) connected to the second connection element (17) on the output side, and with a first torsional vibration damper (4) for transmitting the first drive torques, wherein - the input assembly (2) and the output assembly (3) can be pivoted against each other by a defined first pivot angle (Alpha) about the axis of rotation (21) against spring-elastic resistances of the first torsional vibration damper (4), - the inlet assembly (2) has an inlet flange (8) connected to the first connection element (16), - the input flange (8) is operatively connected to the output assembly (3) via the first torsional vibration damper (4) under load, transmitting first drive torques, - the first torsional vibration damper (4) is formed by a first spring device (6) received in a housing (10) of the output assembly (3), on which the input flange (8) under load transmits the first drive torques to the output assembly (3), - an intermediate flange (18) and the input flange (8) are in contact with a second spring assembly (7) of a second torsional vibration damper (5), which transmits second drive torques between the input assembly (2) and the intermediate flange (18), - at least one slip clutch (44, 45, 46) is formed between the intermediate flange (18) and the output assembly, - the intermediate flange (18) is operatively connected to the output assembly (3) via the slip clutch (44, 45, 46) until a breakaway torque of at least one slip clutch (44, 45, 46) is reached about the axis of rotation (21) by means of static friction and is rotationally fixed. [2] Torque transmission device according to claim 1, characterized by , that the second drive torques are transmitted via the second spring device (7) between the input flange (8) and the intermediate flange (18) until the first drive torques are reached. [3] Torque transmission device according to claim 1 or 2, characterized by, that the inlet flange (8) and the intermediate flange (18) are pivotable against spring-elastic resistances of the second torsional vibration damper (5) by a defined second pivot angle (Beta) about the axis of rotation (21), wherein the second pivot angle (Beta) is smaller than the pivot angle (Alpha) or corresponds at most to the smallest value of the first pivot angle (Alpha). [4] Torque transmission device according to claim 1 or 2, characterized by , that the largest value of the second drive torques is smaller than the smallest value of the breakaway torque and that the value of the breakaway torque is equal to or greater than the smallest value of the first drive torques but smaller than the largest value of the first drive torques. [5] Torque transmission device according to claim 1, characterized by, that until the breakaway torque is reached, a rotationally fixed connection between the input flange (8) and the output assembly is established via the intermediate flange (18) and via the at least one slip clutch (44, 45, 46), limited around the axis of rotation (21) by the breakaway torque and acting by static friction. [6] Torque transmission device according to claim 1, 2, 3 or 4, characterized by , that the second spring assembly (7) is formed by second coil springs (7a) distributed circumferentially around the axis of rotation (21). [7] Torque transmission device according to any one of the preceding claims 1 to 6, characterized by, that the slip clutch (44, 45) is formed by at least one friction pair consisting of at least one first friction surface (24a, 27a) and a friction disc (24, 27) with at least one second friction surface (35a, 36a) of a friction ring (35, 36) and / or a slip clutch (46) is formed by a friction pair consisting of at least one third friction surface (36b) of a friction ring (36) with at least one fourth friction surface (10d) of the housing (10), wherein the first friction surface (24a, 27a) is in frictional contact with the second friction surface (35a, 36a) and / or the third friction surface (36b) is in frictional contact with the fourth friction surface (10d). [8] Torque transmission device according to claim 7, characterized by , that the intermediate flange (18) has two friction discs (24, 27) that are rotationally fixed about the axis of rotation (21) and axially connected to each other, [9] Torque transmission device according to claim 8, characterized by, that a first friction disc (24) is arranged on a first flank (8a) of the inlet flange (8) and a second friction disc (27) is arranged on a second flank (8b) of the inlet flange (8) facing away from the first flank (8a), wherein each of the friction discs (24, 27) is provided with a first friction surface (24a, 27a), wherein the respective first friction surface (24a, 27a) is in frictional engagement with a second friction surface (35a, 36a). [10] Torque transmission device according to claim 8 or 9, characterized by , that the intermediate flange (18) is axially clamped by friction between two friction rings (35, 36) and / or the housing (10), wherein at least one of the friction rings (35, 36) is axially supported on the housing (10) and at least one of the friction rings (35, 36) is provided with at least the second friction surface (35a, 36a) and / or at least one of the friction rings (35, 36) is provided with the third friction surface (36b).

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