WO2014063881A1

WO2014063881A1 - Torsional vibration damper arrangement

Info

Publication number: WO2014063881A1
Application number: PCT/EP2013/069738
Authority: WO
Inventors: Daniel Eckhardt; Patrick Rediger; Matthias Kram; Christoph Sasse
Original assignee: Zf Friedrichshafen Ag
Priority date: 2012-10-22
Filing date: 2013-09-23
Publication date: 2014-05-01
Also published as: DE102012219194A1

Abstract

A torsional vibration damper arrangement (100) for a drivetrain, wherein the torsional vibration damper arrangement (100) is designed to transmit a rotational movement from an input (110) of the torsional vibration damper arrangement (100) to an output (120) of the torsional vibration damper arrangement (100), comprises a first torsional vibration damper (130), an absorber arrangement (140) and a second torsional vibration damper (150), wherein the first torsional vibration damper (130) is arranged radially outside the second torsional vibration damper (150), wherein the absorber arrangement (140) and the first torsional vibration damper (150) at least partially overlap one another radially, wherein the torsional vibration damper arrangement (100) is designed to transmit the rotational movement from the input of the torsional vibration damper arrangement (100) initially to the first torsional vibration damper (130) and subsequently to the second torsional vibration damper (150) and/or the absorber arrangement (140), and wherein the first torsional vibration damper (130) is designed such that the rotational movement is transmitted from the first torsional vibration damper (130), at a side of said torsional vibration damper (130) which faces toward the input (110) of the torsional vibration damper arrangement (100), to the second torsional vibration damper (150) and/or the absorber arrangement (140).

Description

Torsionsschwinqunqsdämpferanordnunq

Exemplary embodiments relate to a torsional vibration damper arrangement for a drive train, as may be used, for example, in the context of a motor vehicle and in particular in the area of a passenger car.

In many fields of technology, but especially in vehicle construction, the technical challenge arises that a rotational movement torsional or torsional vibrations are superimposed, which should be suppressed or attenuated as possible, before the rotational movement is forwarded to other components.

Corresponding torsional vibrations may, for example, result from a drive unit of a motor vehicle due to operational reasons, for example if it is an internal combustion engine. Such a design does not have a uniform torque development, but rather has an at least partially dependent on the number of cylinders and their arrangement dependent on torque development.

Within the scope of a drive train of such a motor vehicle, torsional vibration damper arrangements are used which operate, for example, according to the two-damper-converter principle (ZDW). In these, a speed-adaptive absorber is often arranged between two dampers on the so-called intermediate mass of the same. A Tilger differs here from other Torsionsschwingungsdämp- by the fact that in this the rotational movement does not run through corresponding energy-storing elements, but these are only stimulated to appropriate oscillations or other movements.

Regardless of the exact design of the vehicle here is generally only a limited space available. In vehicles with a front-transverse drive train, in which therefore the at least not insignificant parts of the drive train are installed transversely to its direction of travel in the front region of the vehicle, here is a special focus on an axially slidable as possible arrangement. Depending on the concrete implementation, it may be advisable in this case to arrange the absorber masses used in a speed-adaptive absorber as far as possible radially outward, in order to increase the effect of this oscillation reduction unit.

DE 10 2008 057 648 A1 relates to a power transmission device, in particular for power transmission between a prime mover and an output, in which a speed-adaptive absorber is arranged between two series-connected dampers. DE 10 2009 024 743 A1 relates to a hydrodynamic Namely torque converter, in which a speed-adaptive absorber between the piston and spring is integrated. Finally, WO 201/110146 A1 relates to a damper unit and a power transmission device having such a damper unit, in which a speed-adaptive damper is implemented between two springs.

In the implementations described in these documents, not least axial space is given away by the arrangements of the individual components, which may be disadvantageous, for example, in the previously mentioned front-transverse drive trains. In these, both the engine, as well as the starting element and possibly the integrated behind the starting element gear transversely to the direction of travel of the motor vehicle in its front area is implemented. This arrangement of a drive train, which is also very popular with small cars, poses particular challenges to the axial installation space.

Therefore, there is a need to provide a torsional vibration damper arrangement for a powertrain that improves a trade-off between damping capability and axial space.

This requirement is borne by a torsional vibration damper arrangement according to claim 1.

An embodiment of a torsional vibration damper assembly for a powertrain, such as a motor vehicle, wherein the torsional vibration damper assembly is configured to transmit rotational motion from an input of the torsional damper assembly to an output thereof includes a first torsional vibration damper, a damper assembly, and a second torsional vibration damper. The first torsional vibration damper is in this case arranged radially outside the second torsional vibration damper, wherein the Tilgeranordnung and the first torsional vibration damper overlap each other radially at least partially. The torsional vibration damper assembly is configured to transmit rotational motion from the input of the torsional vibration damper assembly first to the first torsional vibration damper and then to the second torsional vibration damper and / or damper assembly, wherein the first torsional vibration damper is configured such that rotational movement from the first torsional vibration damper is transmitted to the second torsional vibration damper and / or the Tilgeranordnung at one of the input of the torsional vibration damper facing side of the first torsional vibration damper.

One embodiment of a torsional vibration damper arrangement is based on the finding that a compromise between the damping capability of the torsional vibration damper arrangement on the one hand and the axial installation space of another. on the one hand can be improved by, on the one hand, the Tilgeranordnung and the first torsional vibration damper overlap each other at least partially radially. The first torsional vibration damper is in this case the one which is coupled to the input of the Torsionsschwingungsdämpferanordnung and thus damps a torsional vibration included in the rotational movement before the damped rotational movement is transmitted to the second torsional vibration damper and / or the Tilgeranordnung. On the other hand, the axial construction space is positively influenced by the fact that the first torsional vibration damper is just designed so that the rotational movement is transmitted to the input of the torsional vibration damper assembly side facing the first torsional vibration damper to the subsequent components.

Optionally, in a torsional vibration damper arrangement according to an exemplary embodiment, the first torsional vibration damper may be arranged on a side of the absorber arrangement facing away from the input of the torsional vibration damper arrangement. As a result, it may possibly be possible to use a space available radially within the first torsional vibration damper for other components, for example a turbine wheel of a hydrodynamic starting element.

Optionally, in such a torsional vibration damper according to one embodiment, the rotational movement of an axial direction may be radially further inwardly from the input of the torsional vibration damper assembly to the first torsional vibration damper as the rotational motion is transmitted from the first torsional vibration damper to the second torsional vibration damper and / or the absorber assembly. This may possibly make it possible to guide the rotational movement to the first torsional vibration damper in a region which is less attractive for other components of a corresponding torsional vibration damper arrangement or a corresponding starting element. In addition, such a transmission can also be implemented to save space in terms of the axial space used.

Optionally, in a torsional vibration damper assembly according to an embodiment, the rotational movement from the input of the Torsionsschwingungs- damper assembly to the first torsional vibration damper on a side facing the input of the torsional vibration damper assembly side of the first torsional vibration damper. This makes it possible to additionally save axial construction space by both the input as well as the second torsional vibration and / or Tilgeranordnung are coupled to the first torsional vibration damper on the input side facing the same. A guide of the rotational movement on a side facing away from the input side of the first torsional vibration damper can thus be optionally saved. Optionally, in a torsional vibration damper assembly according to an embodiment, the first torsional vibration damper may comprise at least one spring element coupled between an input member and an output member of the first torsional vibration damper. Here, the spring element may comprise a coil spring, a bow spring and / or a barrel spring. This makes it possible to make the first torsional vibration damper compact in such a way that the rotational movement is transmitted from the input component via the at least one spring element and the Ausgansbauteil. The at least one spring element thus serves as an energy store, in which the energy contained in the torsional vibration is temporarily stored at least temporarily.

Optionally, in a torsional vibration damper according to an embodiment, the input member and the output member of the first torsional vibration damper may abut on a common side eccentric to the at least one spring member therewith. Due to the eccentric system on the common side, this may possibly make it possible to reduce a mass of the input component. In addition or as an alternative to this, the axial construction of the torsional vibration damper arrangement can, if appropriate, be further reduced.

Optionally, in such a torsional vibration damper assembly according to an embodiment, the common side may be the side of the first torsional vibration damper facing the input of the torsional vibration damper assembly. In this way, it may possibly be possible, just in the case of an arrangement of the first torsional vibration damper on the side of the absorber arrangement facing away from the input of the torsional vibration damper arrangement, to likewise save axial installation space.

Optionally, in a torsional vibration damper arrangement according to an exemplary embodiment, the at least one spring element may be at least partially open radially on the outside. In this way, it may possibly be possible to make the at least one spring element larger and thus possibly to improve the damping effect. Thus, it may be possible, for example, to insert or insert a spring element, as mentioned above, with a larger diameter, which extends radially further outwards. This also makes it possible, if necessary, to use the available space more efficiently and thus save axial space. Optionally, according to one embodiment, a torsional vibration damper arrangement may be coupled to a turbine wheel of a hydrodynamic starting element, wherein the at least one spring element of the first torsional vibration damper is arranged at least partially radially outside of the turbine wheel along an axial direction of the torsional vibration damper arrangement. This may possibly make it possible to reduce the axial construction of the torsional vibration damper arrangement or of the hydrodynamic starting element. in that the turbine wheel is arranged at least partially radially inside the first torsional vibration damper.

Optionally, in such a torsional vibration damper assembly according to an embodiment, the turbine shell may comprise a turbine shell and a plurality of vanes, the turbine shell having a plurality of recesses and the plurality of vanes each having at least one protrusion, the protrusions and the recesses of the turbine shell being formed in that the projections can be introduced into the recesses from a blade side of the turbine shell so that the projections do not protrude substantially beyond a side of the turbine shell facing away from the blade side. The blades can then be materially connected to the turbine shell, so for example soldered or verschwe eats. This makes it possible to save axial space by the blades close substantially flat with the turbine shell. The side facing away from the blade side is hereby typically facing the torsional vibration damper arrangement, that is to say, for example, the first torsional vibration damper, the second torsional vibration damper and / or the absorber arrangement. In this way, if necessary, a distance of the turbine shell from a corresponding component of the torsional vibration damper arrangement can be reduced and thus the axial installation space can be further reduced. A frictional or frictional connection comes about through static friction, a cohesive connection by molecular or atomic interactions and forces and a positive connection by a geometric connection of the respective connection partners. The static friction thus generally requires a normal force component between the two connection partners.

Optionally, in the case of a torsional vibration damper arrangement according to one exemplary embodiment, the input of the torsional vibration damper arrangement can be connected via a spline to an input of the first torsional vibration damper. For example, the connector may include a riveted to the input or welded bent metal sheet. This may make it possible, if necessary, to further simplify the construction with structurally simple means, for example by saving expensive components such as spacers or spacer rivets. Of course, however, in other embodiments, such can be used.

Optionally, in a torsional vibration damper assembly according to one embodiment, the absorber assembly may comprise at least one absorber mass carrier and at least one absorber mass, the absorber mass carrier being configured to be exposed to rotational movement, and wherein the absorber mass carrier and the at least one absorber mass are configured to surround the at least one absorber mass to be guided so that this superimposed during a rotary motion torsional vibration component is deflected from a rest position. Optionally, with such a Torsionsschwingungsdämpferanordnung according to an embodiment of the second torsional vibration damper comprise at least one spring element which is in contact with the absorber mass carrier as the input of the second torsional vibration damper. As a result, it may possibly be possible to save components of a corresponding torsional vibration damper arrangement and thus also to save axial space as necessary by omitting corresponding connecting elements.

Optionally, in a torsional vibration damper assembly according to an embodiment of the second torsional vibration damper having a hub disc which is in contact with the at least one spring element and is coupled as an output of the second torsional vibration damper with the output of the torsional vibration damper assembly. Alternatively, the second torsional vibration damper may comprise at least one cover plate, which is in contact with the at least one spring element and is coupled as an output of the second torsional vibration damper to the output of the Torsionsschwingungsdämpferanordnung. In this case, a hub disc is typically arranged centrally, that is to say centrally with respect to the at least one spring element, while the at least one cover plate is arranged offset axially relative to the at least one spring element. By both constructions, a compact and therefore axial construction saving space implementation of a Torsionsschwingungsdämpferanordnung can be made possible. A cover plate can thus also serve, for example, for axial guidance of the spring element or elements.

In a torsional vibration damper assembly according to an embodiment, the input of the torsional vibration damper assembly may include or be coupled to an output of a friction clutch, wherein the friction clutch is configured to transfer the rotational motion to the torsional vibration damper assembly. Alternatively or additionally, the output of the torsional vibration damper arrangement may also be coupled to or comprise an output hub. Thus, in the first case, for example, be formed by a friction surface support, such as a piston of the friction clutch. Alternatively or additionally, the input may also include a connection structure with which the torsional vibration damper assembly is coupled to the friction clutch. For example, the input may also be a riveted connection or another corresponding connection. By both design measures, it may possibly be possible again to save axial space.

A frictional contact is in this case when two objects, so for example, the respective receiving element and the sliding surface frictionally contact each other, so that between them a force in the case of a relative movement perpendicular to a contact surface between them. Here, a speed difference, so for example, a slip exist. However, in addition to such a frictional contact, a frictional contact also includes a frictional contact. conclusive or non-positive connection between the objects in question, in which a corresponding speed difference or slip substantially does not occur.

Adjacent are two objects, between which no further object of the same type is arranged. Immediately adjacent are corresponding objects when they are adjacent, that is, for example, in contact with each other. A mechanical coupling of two components comprises both direct and indirect coupling. Under an integrally formed component is understood as one which is made exactly from a contiguous piece of material. The term "integral" may therefore be used synonymously with the terms "integral" or "one-piece".

Despite the word component "direction", the individual "directions" in the present case may not necessarily be a direction in the mathematical sense of a vector, but a line along which the corresponding movement takes place. Such a line can be straight but also bent. Abgrenzenzenzen here are directions that actually describe directions along a line, such as the direction of movement. Thus, for example, a first direction may be opposite to a second direction, but both run or be directed along a line also designated as a direction.

For example, a component may have n-fold rotational symmetry, where n is a natural number greater than or equal to 2. An n-fold rotational symmetry is present when the component in question, for example, about a rotational or symmetry axis by (360 n) is rotatable and thereby essentially in terms of form passes into itself, so with a corresponding rotation substantially to itself in the mathematical sense is shown. By contrast, in the case of a complete rotation-symmetrical design of a component in any rotation about any angle about the axis of rotation or symmetry, the component essentially transits itself in terms of its shape, so it is essentially mapped onto itself in a mathematical sense. Both an n-fold rotational symmetry as well as a complete rotational symmetry is referred to here as rotational symmetry.

Hereinafter, embodiments will be described and explained in more detail with reference to the accompanying drawings.

1 shows a schematic representation of a torsional vibration damper arrangement according to an embodiment; 2 shows a cross-sectional view through a hydrodynamic starting element with a torsional vibration damper arrangement according to an exemplary embodiment;

3 shows a cross-sectional view through a hydrodynamic starting element with a torsional vibration damper arrangement according to an embodiment, in which the turbine wheel is connected by means of a ZDW circuit;

4 shows a hydrodynamic starting element with a torsional vibration damper arrangement according to an exemplary embodiment, in which the turbine wheel is arranged in the form of a double TTD circuit;

5 shows a cross-sectional view through a hydrodynamic starting element with a torsional vibration damper arrangement according to an embodiment, in which the absorber arrangement comprises a common absorber mass carrier, which also serves as an output component of a first torsional vibration damper and as input component of a two torsional vibration damper;

6 shows a cross-sectional representation through a hydrodynamic starting element with a torsional vibration damper arrangement according to an exemplary embodiment, in which the spring elements of the first torsional vibration damper are at least partially open radially on the outside;

7 shows a cross-sectional view through a hydrodynamic starting element with a torsional vibration damper arrangement according to an exemplary embodiment, in which the input of the first torsional vibration damper is connected by means of splines; and

FIG. 8 shows a schematic representation of a drive train with a torsional vibration damper arrangement according to one exemplary embodiment.

In the following description of the accompanying drawings, like reference characters designate like or similar components. Further, summary reference numbers are used for components and objects that occur multiple times in one embodiment or in one representation, but are described together in terms of one or more features. Components or objects which are described by the same or in a combination of reference numerals may have the same, but possibly also different, characteristics with respect to individual, several or all features, for example their dimensions. results from the description unless something else explicitly or implicitly results from the description.

As has already been explained, there is a need in many applications in mechanical engineering and vehicle construction to remove torsional vibrations, which are also referred to as torsional vibrations, from a rotational movement, or at least to damp them, before they are passed on to further components. An example here are powertrains of motor vehicles in which due to the internal combustion engines used often corresponding torsional vibrations are coupled into the drive train. In order to increase the ride comfort of the corresponding vehicle, they are removed from the rotational movement, but at least reduced.

Conventionally, for example, two-damper transducers (ZDW) are used, in which, for example, speed-adaptive absorbers (DAT) are arranged between two dampers. In other words, such a speed-adaptive damper is conventionally formed as part of the intermediate mass.

In many vehicles and corresponding applications here the available space is limited. Especially in vehicles with a front-transverse drive train, in which so essential parts of the drive train are arranged in the front region of the vehicle and installed transversely to the direction of travel, there is a special attention to an axially slidable as possible arrangement. However, it may be advisable to increase the effect of such a vibration reduction unit to arrange the absorber masses of such a speed-adaptive absorber as far as possible radially au Shen.

In conventional designs, the output portion of the outer torsional vibration damper is often located between the vibration reduction unit and the turbine of a corresponding torque converter. This has the consequence that the circuit is designed correspondingly smaller. On the one hand, this can result in a disadvantageous hydrodynamic identifier. If there is a swelling of the hydrodynamic circuit, this may possibly also lead to contact between the turbine and the vibration reduction unit.

Likewise, chamberings of the outer torsional vibration damper on the turbine side are often used conventionally, which may be disadvantageous in the interest of a reduction in space. If, for example, chambered absorber masses are used as part of a speed-adaptive absorber, which are guided over the extended cover plates of the inner torsional vibration damper, it may be disadvantageous that the absorber masses are arranged radially inside the outer torsional vibration damper. By virtue of such an arrangement, its effectiveness and thus the effectiveness of the speed-adaptive absorber can be adjusted if necessary. be limited. It may also be critical in such an arrangement, if necessary, if the absorber masses in the region of the outer torsional vibration damper find no free space to deflect radially outward. This may also result in a restriction of the operability of a corresponding speed-adaptive filter, which may possibly even be exposed to an increased risk of mechanical damage during operation.

As already explained, there is a need to improve a compromise between a damping effect of a torsional vibration damper arrangement on the one hand and its axial installation space on the other hand. In other words, there is a need to further develop the conventional solutions so that their vibration reduction units are more optimally adapted to the axial and radial space restrictions. As will be explained below, embodiments of a torsional vibration damper arrangement just make it possible to improve the aforementioned compromise. Thus, for example, an exemplary embodiment can make easier the use of a speed-adaptive absorber in the front-transverse region, ie in the region of drive trains of a motor vehicle, in which the drive train is arranged in the front region of the vehicle and essentially transversely to the direction of travel of the same.

In the context of the present description, the focus is essentially placed on hydrodynamic starting elements, more precisely on hydrodynamic torque converters with a lockup clutch, embodiments of a torsional vibration damper assembly being by no means limited to this field of application. Without restricting generality, hydrodynamic starting elements are therefore described below, although torsional vibration damper arrangements according to one exemplary embodiment can also be used for other components.

1 shows a schematic representation of a torsional vibration damper arrangement 100 according to an exemplary embodiment of a drive train not shown in FIG. 1. The powertrain may in this case be, for example, that of a motor vehicle, that is to say, for example, that of a passenger car, but also that of another commercial vehicle. In this case, the torsional vibration damper arrangement 100 is just designed and configured such that it transmits a rotary movement from an input 1 10 to an output 120. Both the input 1 10 as well as the output 120 are in this case the torsional vibration damper 100th

The torsional vibration damper arrangement 100 comprises a first torsional vibration damper 130, a damper arrangement 140 and a second torsional vibration damper 1 50. The illustration in FIG. 1 shows the arrangement of the individual components 130, 140, 150 relative to an axial direction 1 60 which is the axis of rotation of the torsional vibration damper assembly 100 and The torsional vibration damper 130 is disposed radially outward of the second torsional vibration damper 150, while the damper assembly 140 and the first torsional vibration damper 130 overlap each other at least partially radially.

The input 1 10 is coupled to the first torsional vibration damper 130 such that the rotational movement is transmitted from the input 1 10 to the first torsional vibration damper 130. From this, the rotational movement is provided in a damped with respect to rotational irregularities form of Tilgeranordnung 140 which emits them in the embodiment shown in Fig. 1 to the second torsional vibration damper 150, which is coupled to the output 120 of the torsional vibration damper assembly 100. In this case, the first torsional vibration damper 130 is embodied in such a way that the rotational movement of the latter is transmitted to the absorber arrangement 140 on a side of the first torsional vibration damper 130 facing the input 1 10 of the torsional vibration damper arrangement 100. In other embodiments, in addition or alternatively, the rotational movement of the first torsional vibration damper 130 may also be transmitted from the first torsional vibration damper 130 to the second torsional vibration damper 150. In other words, in different embodiments, the rotational movement from the first torsional vibration damper may be serially transmitted to the second torsional vibration damper and absorber assembly 140, however, a parallel transmission of rotational motion may also be implemented.

In the exemplary embodiment shown in FIG. 1, the first torsional vibration damper 130 is arranged on a side of the absorber arrangement 140 facing away from the inlet 1 10 of the torsional vibration damper arrangement 100. Likewise, the rotational movement of the input 1 10 at the input 1 10 side facing the first torsional vibration damper 130 is supplied. Thus, the first torsional vibration damper 130 with respect to the supply and the discharge of the rotational movement is completely connected to the input 1 10 side facing.

In order to make this possible in the embodiment shown here, the rotational movement along the axial direction 1 60 radially further inwardly from the input 1 10 to the first torsional vibration damper 130 out as this rotational movement from the first torsional vibration damper 130 to the second torsional vibration damper 1 50 or 50. the absorber assembly 140 is transmitted. As a result, the supply of the rotational movement can take place in a region which is typically less interesting for the implementation of other damping-relevant components. In particular, this arrangement can thus enable a transmission of the rotational movement of the first torsional vibration damper 130 radially outward to the absorber arrangement 140 or the second torsional vibration damper 150. Although Fig. 1 shows a schematic representation, the arrangements of Components with respect to their radial and axial arrangement correctly reproduced each other.

As has already been explained above, the present description essentially describes torsional vibration damper arrangements 100 according to an embodiment which are implemented in connection with a hydrodynamic starting element. Thus, FIG. 1 also schematically shows a turbine wheel 180 of a hydrodynamic starting element 190, which is implemented at least partially radially further inwardly as a spring element of the first torsional vibration damper 130, which can serve as a buffer for the energy of the rotational irregularities of the rotational movement. As a result, axial space can be saved by this arrangement of the first torsional vibration damper 130 by at least partially implementing the turbine wheel 180 of the hydrodynamic starting element 190 radially inside the first torsional vibration damper 130.

The turbine wheel 180 is typically also coupled to the output 120 here. However, this can be done in different ways and ways, as will be explained in more detail below, for example, in connection with FIGS. 2 to 4. For example, the turbine wheel 180 may be directly coupled to the output 120 of the torsional vibration damper assembly 100, also referred to as RTD (Friction Clutch Torsional Vibration Damper) circuitry. If, on the other hand, the turbine wheel 180 is connected on the input side to the second torsional vibration damper 150, this is also referred to as a ZDW circuit (ZDW = two-damper converter), while an input-side connection of the turbine wheel 180 to the first torsional vibration damper 130 is also referred to as a double TTD Circuit (TTD = Turbine Torsion Damper) is called. Corresponding embodiments of such circuits are shown in FIGS. 2, 3 and 4.

FIG. 2 shows a cross-sectional view through a hydrodynamic starting element 190, which is implemented as a torque converter 200. The hydrodynamic starting element 190 thus has a housing 210 which can be connected in a rotationally fixed manner to a crankshaft of a drive motor via one or more connecting pins 220 with a connecting structure 230. The connection structure 230 is implemented here as a flexible connection element 240, which may be designed, for example, to at least partially intercept and dampen tumbling movements of the drive motor.

The housing 210 is configured in two parts with a first housing shell 250 facing the drive motor and a second housing shell 260 facing a downstream transmission. The two housing shells 250, 260 are in this case connected cohesively to one another via a weld 270, but in other embodiments, by other connection techniques be connected to each other. The second housing shell 260 is here also referred to as a pump shell 280 which comprises a bulge 290, in which a plurality of blade flaps 300 are attached. The blades 111 are in the embodiment shown here in the pump shell 280 via corresponding projections 310, which are in engagement with corresponding recesses 320 of the pump shell 280, by inserting and soldering the same materially connected. The blade flaps 300 are also connected via a connecting plate 330 in the interior of the housing 210.

The housing 210 is received via a weld on a housing hub 340 and filled via corresponding holes with a liquid medium, such as an oil, during operation. The pump shell 280 and the blades 300 thus form a pump 350 for the liquid medium in the housing 210, when the housing 210 is put over the connecting pin 220 in a corresponding rotational movement. In this case, the pump wheel 350 generates a flow of the hydraulic medium, which is directed onto a turbine wheel 180 of the hydrodynamic starting element 190. The turbine wheel 180 in this case comprises a turbine shell 370 and a plurality of blade flaps 380, which are connected to the turbine shell 370 via similar projections 390 and recesses 400. In this case, by means of a corresponding passage of the projections 390 of the blade flaps 380 through the recesses 400 and a subsequent soldering thereof to the turbine shell 370, a substantially substance-coherent connection is created. The soldering can be complementary or exclusive. Also, the turbine wheel 180 has, comparable to the impeller 350, a corresponding connecting plate 410.

The turbine wheel 180 is in this case arranged in such a way that the hydraulic flow generated by the impeller when the housing 210 moves causes the turbine wheel 180 to rotate. For this purpose, in the exemplary embodiment shown here, the turbine wheel 370 is connected via a rivet connection 420 to an output hub 430, which meshes with a transmission input shaft 440 via a toothing.

In order to enable a corresponding torque amplification in the presence of a larger speed difference between the turbine wheel 180 and impeller 350, the hydrodynamic starting element 190 further comprises a stator 450, which is guided via a freewheel 460 in the interior of the housing 210.

The hydrodynamic starting element 190 also has a bridging clutch 470, which is implemented as a friction clutch 480. Thus, this has a friction lining 490, which may be connected to a piston 500, for example. The piston 500 can be displaced along the axial direction 1 60 in the housing 210, so as to create or release a frictional contact. Is the friction lining 490 Connected to the piston 500, the housing 210 or the first housing shell 250 facing the drive motor typically has a corresponding counter friction surface in the region of the friction lining 490, via which the friction lining 490 can establish a frictional or non-positive connection with its friction surface. As a result, the rotational movement can be transmitted from the housing 210 to the piston 500.

The piston 500 is in this case designed as part of an actuating element of the friction clutch 480 or lock-up clutch 470, wherein the respective actuation is effected via a change of pressure conditions in a first volume 510 relative to a second volume 520. By a corresponding control of the pressure conditions in the two volumes 510, 520, the friction clutch 480 can thus be closed or opened by moving the piston 500 along the axial direction 1 60. The piston 500 is rotatably connected via a Distanzvernietung 530 with an input member 540 of the first torsional vibration damper 130. In this case, the input component 540 can be produced, for example, as a deep-drawn sheet metal component.

The first torsional vibration damper 130 also has at least one spring element 550 which is directly or indirectly in contact with the input component 540. More specifically, the first torsional vibration damper 130 comprises a plurality of circumferentially distributed spring members 550 at least partially for temporarily storing an energy of one of rotational rotationality superimposed on the rotary motion. Correspondingly, the first torsional vibration damper 130 has an output component 560, which in the exemplary embodiment shown here substantially encloses radially outwards the spring elements 550 implemented as arc or coil springs. The spring elements 550 are in this case also indirectly or directly in contact with the output component 560.

The first torsional vibration damper 130 is hereby implemented as part of a torsional vibration damper arrangement 100 according to an exemplary embodiment, wherein the piston 500 represents the input 1 10 of the torsional vibration damper arrangement 100. As will be discussed below, the output hub 480 in the embodiment shown here forms the output 120 of the output of the torsional vibration damper assembly 100.

The output component 560 and the input component 540 are guided along a side of the first torsional vibration damper 130 facing the input 1 10. In this case, the input component 540 is arranged radially further inwards than the corresponding output component 560, which simultaneously serves as the input of the absorber arrangement 140. The output component 560 of the first torsional vibration The damping damper 130 thus simultaneously serves as the absorber mass carrier 570-1 of the absorber arrangement 140.

In addition to the absorber mass carrier 570-1, the absorber arrangement 140 further has a further absorber mass carrier 570-2, between which a plurality of absorber masses 580 are arranged such that they can move relative to the absorber mass carriers 570 in the event of rotational irregularity. In other words, the absorber mass carriers 570 and the absorber masses 580 are just designed such that the absorber masses 580 are deflected out of a rest position when the absorber arrangement 140 is subjected to rotational irregularity, that is to say to a torsional vibration component, for example. This can be implemented, for example, in that the absorber mass carriers 570 and the absorber masses 580 each have guideways on which guide rollers, which can be implemented as step rollers 670, for example, run along. In this way, relative movement of the absorber masses 580 with respect to the absorber mass carriers 570 can take place.

For its part, the absorber mass carrier 570-2 constitutes an output of the absorber arrangement 140 and an input component 590 of the second torsional vibration damper 150. In the embodiment of a torsional vibration damper arrangement 100 shown in FIG. 2, the absorber mass carrier 570-2, ie the input component 590, is the cover plate 600 -1 executed, which has been described as well as in connection with the torsional vibration damper 130, with at least one spring element 610 directly or indirectly in abutment. By means of a further spacer riveting 620, a further cover plate 600-2 is likewise designed as an input component 590 of the second torsional vibration damper 150. Also with this are the spring elements 610 of the second torsional vibration damper 150 directly or indirectly in abutment.

The cover plates 600 are in this case just designed so that they touch the spring elements 610, which in turn are implemented as bow or coil springs, eccentrically with respect to their center. In a center of the spring elements 610, these are directly or indirectly in contact with an output component 630 of the second torsional vibration damper 150, which is more specifically a hub disk 640 which is located on an area of the hydrodynamic axis facing the axial or axial direction 1 60 Start-up element 190 via the riveting 420 also mechanically non-rotatably connected to the output hub 430.

The additional distance riveting 620 is in this case designed radially inwardly of the second torsional vibration damper 150 or its spring elements 610. Nevertheless, in order to allow the cover plates 600, relative to the hub disc 640 and at least with respect to an angle section, free mobility, the hub disc 640 has a curved elongated hole, which extends beyond the relevant extends the angular range and through which the further Distanzvernietung 620 may extend such that the corresponding free mobility is given. For example, the slot may have a size along the radial direction which is greater than a diameter of the further distance riveting 620 in the region of the hub disc 640.

Correspondingly, the cover plates 600 in the region of the distance riveting 530 also have correspondingly shaped arcuate elongated holes, through which the spacer riveting 530 extends, so that the input component 540 of the first torsional vibration damper 130 relative to the cover plates 600 also enables a corresponding mobility at least over a certain angular range ,

If the friction clutch 480, ie the lockup clutch 470, is closed so that the friction lining 490 produces the frictional connection between the housing 210 and the piston 500, the torque is transmitted directly from the housing 210 to the piston 500 and further along a torque path 650. The torque path 650 thus extends from the input 1 10 of the torsional vibration damper assembly 100, so the piston 500, the Distanzvernietung 530, the input member 540, the spring elements 550 and the output member 560 of the first torsional vibration damper 130. From there, the torque on the also transmitted as Tilgermassenträger 570-1 serving output member 560 on the Tilgeranordnung 140 and the other Tilgermasenträger 570-2, from where the torque on the two cover plates 600, wherein the cover plate 600-1 is identical to the Tilgermassenträger 570-2, the spring elements 610 and the hub disc 640 is transmitted as output member 630 of the second torsional vibration damper 150 via the riveting 420 to the output 120 in the form of the output hub 130.

In the embodiment shown in FIG. 2, therefore, in contrast to a conventional solution, the torque is guided radially inward from the output part or output component 560 of the first torsional vibration damper. This provides axial construction space and makes it possible to use the output member 560 of the outer torsional vibration damper (first torsional vibration damper 130) simultaneously as a Tilgermassenträger, which is also referred to as a support member of the speed-adaptive damper 140.

By this arrangement, it is also possible to present a web-guided speed-adaptive Tilgerkonstruktion in the form of Tilgeranordnung 140, in which also called DAT masses (DAT = speed adaptive absorber) absorber masses 580 and the outer first torsional vibration damper 130 on the same or a comparable radial construction space are arranged. For this purpose, the torque, starting from the piston 500, is first transferred radially inside the absorber arrangement 140 to the input component 540 of the outer first torsional vibration damper 130. The chambering of the outer first torsional vibration damper 130 is performed in the embodiment shown here by the output member 560, which in turn can allow advantages in terms of space.

In the exemplary embodiment of a torsional vibration damper arrangement 100 shown in FIG. 1, the damper carrier 570-2, which is also referred to as the second path plate of the speed-adaptive damper, is simultaneously used as input part or input component 590 for the inner second torsional vibration damper 150. The torsional vibration damper arrangement 100, which is also referred to as a vibration reduction unit, can be designed as a capital letter ZDW circuit, RTD circuit or as a double TTD circuit, depending on the desired circuit. The exemplary embodiment shown in FIG. 2 is an RTD arrangement in which the turbine wheel 180 (turbine) is connected in a rotationally fixed manner to the output hub 430 of the torsional vibration damper arrangement 100.

In the embodiment shown in Fig. 2, the absorber masses 580 of Tilgeranordnung 140 are made in several parts. Thus, in the exemplary embodiment shown here, these have two individual sealing masses 660-1, 660-2, which are in axial connection with one another via stepped rollers 670. The two individual penetrator masses 660-1, 660-2 are arranged on the step rollers 670 such that they can be deflected independently of one another out of their respective rest positions.

Of course, in other embodiments, the absorber masses 580 also in one piece or with more than two Einzeletilgermassen 660, for example, three or more corresponding Einzeleltilgermassen 660 have.

The implementation as a multipiece absorber mass 580 can, for example, bring cost advantages here, since a plurality of axially thin plates can be combined to form a total absorber mass 580. Of course, the previously mentioned one-piece absorber mass 580 may be used in embodiments.

Instead of the construction of the turbine wheel 370 shown in Fig. 2 with the respective projections 390, which protrude through the turbine shell 370 and soldered there to form a material connection, can be used to further save radial and / or axial space also another connection technique. Thus, the protrusions 390 in question can be designed with respect to their corresponding recesses 400 just so that they can indeed be inserted into the recesses 400, but do not protrude beyond a side facing away from the respective blade side. In other words, the blade lobes 380 may be formed so that they are not in the radially outer region through the turbine shell 470 are plugged and soldered there, but soldered in this area to the turbine, welded or connected by other cohesive techniques.

FIG. 3 shows a cross-sectional illustration very similar to FIG. 2 through a hydrodynamic starting element 190 based on a torque converter 200 with a lock-up clutch 470, which in turn is designed as a friction clutch 480. Here, the structure of the torsional vibration damper assembly 100 including the first and second torsional vibration dampers 130, 150 and the absorber assembly 140 and the structure of the torque converter 200 components including the turbine wheel 180, impeller 350, and stator 450 are the same as those of the hydrodynamic shown in FIG Starting element 190. In contrast to the hydrodynamic starting element 190 shown there, however, the turbine wheel in the starting element 190 shown in FIG. 3 is arranged by means of a so-called ZDW circuit. This means that the turbine blade 370 of the turbine wheel 180 is not directly connected to the output hub 430 serving as the output 120, but rather is connected via a riveting 680 to the second cover plate 600-2 of the second torsional vibration damper 150, ie its input component 590. In other words, at least the second torsional vibration damper 150 is connected downstream of the turbine wheel 180 and thus essential components of the torque converter, before a rotational movement transmitted via the turbine wheel is transmitted to the output 120 of the torsional vibration damper arrangement 100 in the form of the output hub 430.

In this way, it may be possible to at least attenuate, if not eliminate completely, rotational nonuniformity or a torsional vibration component superimposed on the rotational movement by means of the second torsional vibration damper 150.

Correspondingly, in the solution shown in FIG. 3, the rivet connection 420, which connects the hub disc 640, that is to say the output member 630 of the second torsional vibration damper 150 to the output hub 430, is designed so that it does not catch the turbine shell 370 of the turbine wheel 180.

4 shows a cross-sectional illustration through a further hydrodynamic starting element 190 based on a torque converter 200, which comprises an exemplary embodiment measured on a torsional vibration damper arrangement 100. Again, the torque converter 200 can be bridged by the use of a bridging clutch 470 implemented as a friction clutch 480.

The structure of the torsional vibration damper assembly 100 and the torque converter 200 in this case corresponds to the basic structure, as this has already been explained in Fig. 2. However, the solution presented here differs in terms of some more details. For example, the tur- binenrad 180 arranged here in the form of a double TTD circuit. For this purpose, the turbine shell 370 is made smaller and so does not extend to the area of the output hub 430 zoom. Rather, in comparison to the solution shown in Fig. 2, the input member 540 of the first torsional vibration damper 130 is pulled radially further inward and rotatably connected via a riveting 690 with the turbine shell 370. Accordingly, the rotational movement transmitted from the impeller 350 to the turbine wheel 180 is provided on the input side of the first torsional vibration damper 130. Thus, not only a rotational movement coupled in via the lock-up clutch 470 but also a rotational movement coupled in via the turbine wheel 180 are conducted both via the first torsional vibration damper 130 and via the second torsional vibration damper 1 50 and the absorber arrangement 140.

In order to allow as unchanged as possible a takeover of as many components as possible of the previously described hydrodynamic starting elements 190, the hydrodynamic starting element shown in FIG. 4 has an optional plate 700, which is connected to the input component 590 of the second torsional vibration damper 150 via the riveting 680 from FIG The second cover plate 600-2 is connected. Thus, the sheet 700 is axially in contact with the stator 450, as was the case with the previously described embodiments with respect to the stator 450 and the turbine shell 370. Thus, in the embodiments described above, the guide wheels 450 each axially bear the turbine shells 370 of the turbine wheels 180.

In order nevertheless to allow free pivoting of the input component 590 of the second torsional vibration damper 150 relative to the output 120 over at least a limited angular range, the rivet connection 420 between the output hub 430 and the hub disk 640 acting as the output component 630 is embodied as in FIG. In other words, while the rivet connection 420 couples the output member 630 of the torsional vibration damper to the output hub 430, it does not provide a rotationally fixed connection to the optional plate 700.

In addition, the absorber assembly 140 differs in terms of the design of the absorber mass 580 of the embodiments described above. While in the embodiments described above, two-piece absorber masses 580 have been used with two Einzeletilgermassen 660-1, 660-2, in the embodiment shown in Fig. 4 is a one piece designed absorber mass 580 between the absorber mass carriers 570-1, 570-2 arranged. As already explained above, this shows the different ways in which the absorber masses 580 can be implemented.

FIG. 4 further shows an embodiment in which the blade lobes 380 on the turbine wheel 180 are welded by means of the previously described soldering, welding or other material cohesive connection with the turbine shell are connected. As has already been explained above, the protrusions 390 which are no longer recognizable in FIG. 4 thus do not pass through the recesses 400 in the turbine shell 370, so that the lack of a corresponding rewinding of the protrusions 390 allows axial space to be saved again.

FIG. 5 shows a cross-sectional representation through a hydrodynamic starting element 190, which in turn is implemented on the basis of a torque converter 200. Again, the hydrodynamic starting element 190 again comprises a torsional vibration damper arrangement 100 according to an exemplary embodiment with the first torsional vibration damper 130, the second torsional vibration damper 150 and the absorber arrangement 140. Again, the turbine shell 370 of the turbine wheel 180 is directly rotationally fixed to the output hub 430, ie Output 120 of the torsional vibration damper 100 coupled, as shown in Fig. 2. However, the corresponding connection differs here from that shown in FIG. 2 due to a structurally deviating design of the second torsional vibration damper 150.

However, before this different embodiment is to be explained in more detail, the different embodiments of the first torsional vibration damper 130 and the absorber assembly 140 will first be described in more detail.

Starting from the input 1 10 of the torsional vibration damper assembly 100, which in turn is the piston 500 of the lock-up clutch 470, in turn via the Distanzvernietung 530, the torque is transmitted radially inwardly to the input member 540 of the first torsional vibration damper 130, which is substantially not from different from that shown in FIG. This in turn is indirectly or directly in abutment with a plurality of spring elements 550. These in turn are indirectly or directly in abutment with the output component 560 of the first torsional vibration damper 130, which, however, extends in one piece at an outer radial end of the absorber arrangement 140 and is configured as an absorber mass carrier 570.

The absorber arrangement 140 according to FIG. 5 has a first single-piece mass 660-1 and a second absorber mass 660-2, which are guided on both sides of the absorption mass carrier 570 via a step roller 710 and corresponding guide tracks in the absorber masses 580 and the absorber mass carrier 570. The two absorber masses 660-1 and 660-2 are also not connected to one another in this embodiment, so they can be deflected independently of each other from their respective rest positions.

The absorber mass carrier 570 or the output component 560 of the first torsional vibration damper 130 further extends radially inwards and forms a central position Here, an at least over a certain angular range free and independent movement of this combined component, which is hereinafter referred to as Tilgermassentrager 570, with respect to the input member 540 of the first torsional vibration damper disposed between two cover plates 600-1, 600-2 second torsional vibration damper 130, this also has an arcuate slot through which the Distanzvernietung 530 extends, with the aid of the piston 500 and the input member 540 of the first torsional vibration damper 130 are rotatably coupled together. As already described above, the oblong hole has a circumferential extent in the radial direction which is greater than a diameter of the spacer riveting 530.

The absorber mass carrier 570 thus forms not only the output component of the first torsional vibration damper 130, but also the input component 590 of the second torsional vibration damper, which, in contrast to the embodiments previously shown, centrally or indirectly abuts the spring elements 610 of the second torsional vibration damper 150. The two cover plates 600-1, 600-2 form correspondingly the output components 630 of the second torsional vibration damper 150. In this case, the cover plate 600-2, which faces the turbine wheel 180, is fixedly connected to the turbine shell 370 via the riveting 680, while the latter Piston 500 and the input 1 10 facing cover plate 600-1 rotatably connected via the rivet connection 420 with the output 120 and the output hub 430. In addition, the two cover plates 600 are also connected via a rivet 720 with each other rotationally fixed.

In other words, in the exemplary embodiment shown here of a torsional vibration damper arrangement 100 in the area of the second torsional vibration damper 150, the geometric arrangement along the axial direction with respect to the input component 590 and the output component 630 is reversed.

In addition, in this embodiment, contrary to the Ausführungsbeispieie previously described and shown the absorber masses 660-1 and 660-2 not axially spaced apart sheet metal plates in the form of two Tilgermassenträger 570-1, 570- 2 out. The absorber masses 660-1 and 660-2 are rather fixed in the axial direction on both sides of the absorber mass carrier 530 and on the output member of the outer first torsional vibration damper 130. Furthermore, this output member 560 of the outer first torsional vibration damper 130 is also used as the input member 590 of the inner second torsional vibration damper. Accordingly, as the output components of the inner second torsional vibration damper 1 50, the two cover plates 600-1, 600-2 used.

Although the RTD circuit of the turbine wheel 180 already shown in FIG. 2 was used in FIG. 5, the turbine wheel 180 can, as already described above, be connected to the torsional vibration dampers by various circuit variants. Rung 100 and its output 120 are coupled in the form of the output hub 430.

6 shows a cross-sectional view through a further hydrodynamic starting element 190, which is designed as a torque converter. As already shown in FIG. 3, this is configured such that the turbine wheel 180 is connected via the riveting 680 to the second cover plate 600-2 of the second torsional vibration damper 150 serving as the input component 590. As already described in connection with FIG. 3, the turbine wheel 180 is thus non-rotatably coupled via the second torsional vibration damper to the output 120 of the torsional vibration damper arrangement 100 in the form of the output hub 430.

Otherwise, the first torsional vibration damper does not differ from FIG. 6 from that shown in FIG. The connection to the absorber arrangement 140 as well as the embodiment of the absorber arrangement 140 with two absorber mass carriers 570-1, 570-2 between which absorber masses 580 are movably arranged, which comprise two individual food masses 660-1, 660-2, are identical to those in FIG Fig. 3 embodiment shown configured.

However, the configuration of the first torsional vibration damper 130 differs from the embodiment shown in FIG. 3. With regard to the output component 560, which at the same time also forms the first absorber mass carrier 570-1, this is designed so that it passes through the input component 540 or that the input component 540 passes through the output component 560. The two components 540, 560 can in this case be configured such that they have corresponding recesses extending over a predetermined angular range, through which the corresponding other component can reach. This may also be possible to save axial space.

In addition, the input component 540 does not completely surround the spring elements 550 of the first torsional vibration damper 130, but leaves them at least partially open radially on the outside. This may make it possible to use larger springs or spring elements 550, since a channel in which the Federeiemente 550 are arranged, is open at the top. As a result, it may be possible to further improve the performance of the torsional vibration damper assembly 100.

In order nevertheless to allow guidance of the spring elements 550 in the first torsional vibration damper 130, the input component 540 has a guide plate 730, which is riveted to the input component 540 and allows support of the spring elements 550 radially inward. In addition, the input component 540 has a contact section 740, via which the spring elements 550 are indirectly or directly in contact with the input component 540. This investment section 740 extends completely over an axial width of the spring elements 550 and has a guide portion 750, by means of which the spring elements are guided at least partially in the axial direction to a side facing away from the piston 500 and the input 1 10th Correspondingly, the input component 540 also has a further guide section 760, which guides the spring elements 550 radially outward and in the axial direction in the direction of the input 1 10 and the piston 500, respectively.

In the exemplary embodiments of a torsional vibration damper arrangement 100 shown in FIGS. 2, 3, 4 and 6, the radial sections of the input components 540 and the output components 560 of the outer first torsional vibration damper 130 are respectively connected to the input 1 10, that is to the left in the relevant FIG Figures, arranged from a spring center of the spring elements 550. In other words, in these embodiments, the input member 540 and the output member 560 of the first torsional vibration damper 130 abut on a common side eccentric to the at least one spring member 550 therewith. In the case of the exemplary embodiments shown here, the common side is the side of the first torsional vibration damper 130 facing the torsional vibration damper arrangement 100. In conventional solutions, the relevant input components and output components are frequently arranged on both sides. This also can be saved in comparison to a conventional solution, if necessary, axial space.

FIG. 7 shows a cross-sectional illustration through a further hydrodynamic starting element 190, which is implemented on the basis of a torque converter 200. The starting element 190 shown in FIG. 7, with its torsional vibration damper arrangement 100 according to an exemplary embodiment, is very similar to the variant shown in FIG. 3. However, the two variants shown in FIGS. 3 and 7 differ with respect to two embodiments. Thus, in the case of the torsional vibration damper arrangement 100 shown in FIG. 7, the absorber mass 580 is configured as one piece as in FIG. 4.

In addition, the connection of the input piston 500 to the input member 540 of the first torsional vibration damper 130 is not implemented via a Distanzvernietung 530, but by means of a connector 770. The connector 770 here comprises a cranked plate 780, by means of a riveting 790 with the piston 500 is connected. The plug connection 770 or the bent plate 780 in this case pass through the two cover plates 600-1, 600-2, which again serve as input components 590 of the second torsional vibration damper 150. The cover plates 600 and the bent plate 780 are in this case designed so that in this case a relative movement of the input member 540 of the first torsional vibration damper 130 to the cover plates 600-1, 600-2, so the input member 590 of the second torsional vibration damper 150 is possible. The connector 770 is, however, with the Eingangssbauteii 540 engages such that upon rotation of the piston 500 about the axial direction 1 60 via the connector 770 and the input member 540 of the first torsional vibration damper 130 is taken and thus set in rotation.

In contrast to the embodiments shown so far, therefore, in the embodiment shown here, the torque of the non-rotatably connected to the piston 500 spline, which is also referred to as a toothed element, transmitted. The input component 540 of the outer first torsional vibration damper 130 is thus connected via the plug connection 770. As a result, if necessary, a cost-optimized connection can be realized in comparison to spacer bolts, as described above.

Finally, FIG. 8 shows a schematic representation of a drive train 800 with a torsional vibration damper arrangement 100 according to an exemplary embodiment, which is connected between a drive motor 810, which is also referred to simply as a motor, and a transmission 820. The motor 810 is connected to the input 1 10, the gear 820 to the output 120 of the torsional vibration damper 100. In this case, the other components of the hydrodynamic starting element 190, ie in particular the components of the torque converter, for example the turbine wheel 180 and the impeller 350, are not shown in order to simplify the illustration.

Fig. 8 illustrates the series connection of the first torsional vibration damper 130 with its spring elements 550, which are often referred to simply as a first spring set. The first torsional vibration damper 130 is followed by the absorber arrangement 140, which is also referred to as the absorber unit, and is adjoined by the second torsional vibration damper 150 with its spring elements 610, which are also referred to as the second spring set.

Optionally, the first spring set, that is to say the spring elements 550 of the first torsional vibration damper 130, which lie in the force flow from the motor 810 to the gear 820 in front of the absorber arrangement 140, are designed in one stage. In this case, the design of these spring elements or the first torsional vibration damper 130, for example, carried out so that this relates to a maximum einleitbares or existing torque a stop security of a maximum of 1, 15 times a rated torque of the drive motor 810. The drive motor 810 is in this case also referred to as a drive machine.

In the embodiments described above, rivets have been used in many places for fastening different components together. These can be implemented, for example, as indented rivets, based on rivet pins, separate rivets or other techniques. Alternatively or In addition, other positive, non-positive and / or cohesive connection techniques can be used. Thus, if necessary, individual components can also be welded together, screwed or connected using other appropriate techniques.

The features disclosed in the foregoing description, the appended claims and the appended figures may be taken to be and effect both individually and in any combination for the realization of an embodiment in its various forms.

REFERENCE CHARACTERS

torsional vibration damper

entrance

output

first torsional vibration damper

Tilgeranordnung

second torsional vibration damper axial direction

radial direction

turbine

Hydrodynamic starting element

torque converter

casing

connecting pins

connecting structure

flexible connection element

first housing shell

second housing shell

welding

pump shell

bulge

Blade tab

head Start

deepening

connecting plate

housing hub

impeller

turbine shell

Blade tab

head Start

recess

connecting plate 420 riveted joint

430 output hub

440 transmission input shaft

450 stator

460 freewheel

470 lock-up clutch

480 friction clutch

490 friction lining

500 pistons

510 first volume

520 second volume

530 distance riveting

540 input component

550 spring element

560 output component

570 Tilgermassenträger

580 absorber mass

590 input component

600 cover plate

610 spring element

620 Further distance riveting

630 output component

640 hub disc

650 torque path

660 single-piece-paste

670 step roller

680 riveting

690 riveting

700 sheet metal

710 step roller

720 rivet connection

730 guide plate

740 investment section 750 leadership section

760 Further guidance section

770 plug connection

780 Bent sheet metal

790 riveting

800 powertrain

810 drive motor

820 gearbox

Claims

claims

1 . A torsional vibration damper assembly (100) for a powertrain (800), such as a motor vehicle, wherein the torsional damper assembly (100) is configured to rotate from an input (110) of the torsional damper assembly (100) to an output (120) of the torsional damper assembly (100) Torsional vibration damper assembly (100), comprising: a first torsional vibration damper (130); a damper assembly (140); and a second torsional vibration damper (150), wherein the first torsional vibration damper (130) is disposed radially outward of the second torsional vibration damper (150); wherein the absorber assembly (140) and the first torsional vibration damper (150) at least partially overlap each other radially; wherein the torsional vibration damper assembly (100) is configured to transmit the rotational motion from the input of the torsional vibration damper assembly (100) first to the first torsional vibration damper (130) and then to the second torsional vibration damper (150) and / or damper assembly (140); and wherein the first torsional vibration damper (130) is configured such that the rotational movement of the first torsional vibration damper (130) on a side of the first torsional vibration damper (130) facing the input (110) of the torsional vibration damper arrangement (100) to the second torsional vibration damper (150). and / or the absorber assembly (140) is transmitted.

2. Torsionsschwingungsdämpferanordnung (100) according to claim 1, wherein the first torsional vibration damper (130) on a said input (1 10) of the torsional vibration damper assembly (100) facing away from the Tilgeranordnung (140) is arranged.

3. torsional vibration damper assembly (100) according to claim 2, wherein the rotational movement along an axial direction (1 60) radially further inwardly from the input (1 10) of the torsional vibration damper assembly (100) to the first torsional vibration damper (130) is guided, as the rotational movement from the first torsional vibration damper (130) to the second torsional vibration damper (150) and / or the absorber assembly (140).

A torsional vibration damper assembly (100) according to any one of the preceding claims, wherein the rotational movement from the input (110) of the torsional vibration damper assembly (100) to the first torsional vibration damper (130) faces the input (100) of the torsional vibration damper assembly (100) Side of the first torsional vibration damper (130) takes place.

5. The torsional vibration damper assembly of claim 1, wherein the first torsional vibration damper comprises at least one spring element coupled between an input member and an output member of the first torsional vibration damper. and wherein the at least one spring element (550) comprises a coil spring, a bow spring and / or a barrel spring.

The torsional vibration damper assembly (100) of claim 5, wherein the input member (540) and the output member (560) of the first torsional vibration damper (130) abut on a common side eccentric to the at least one spring member (550).

7. Torsionsschwingungsdämpferanordnung (100) according to claim 6, wherein the common side is the input (1 10) of the torsional vibration damper assembly (100) facing side of the first torsional vibration damper (130).

8. Torsionsschwingungsdämpferanordnung (100) according to any one of claims 5 to 7, wherein the at least one spring element (550) radially outside at least partially open.

9. The torsional vibration damper assembly of claim 5, coupled to a turbine wheel of a hydrodynamic launching element, wherein the at least one spring element of the first torsional vibration damper extends along an axial direction (1 60) of the torsional vibration damper assembly (100) at least partially radially outside of the turbine wheel (180) is arranged.

The torsional vibration damper assembly (100) of claim 9, wherein the turbine wheel (180) comprises a turbine shell (370) and a plurality of vanes (380), the turbine shell (370) having a plurality of recesses (400) and the plurality of vanes (380) each have at least one projection (390), wherein the projections (390) of the blade lugs (380) and the recesses (400) of the turbine shell (370) are formed such that the projections (390) from a blade side of the turbine shell (390). 370) from in the recesses (400) are insertable so that the projections (390) substantially not project beyond a side facing away from the blade side, the turbine shell (370), and wherein the blades (380) with the turbine shell (370) materially connected , for example, soldered or welded, are.

1 1. A torsional vibration damper assembly (100) according to any one of the preceding claims, wherein the input (110) of the torsional vibration damper assembly (100) is via a plug connection (770) which may comprise, for example, a cranked plate (780) riveted or welded to the input (110) , is connected to an input (540) of the first torsional vibration damper (130).

12. Torsionsschwingungsdämpferanordnung (100) according to any one of the preceding claims, wherein the Tilgeranordnung comprises at least one Tilgermassenträger (570) and at least one Tilgermasse (580), wherein the Tilgermassenträger (570) is adapted to be subjected to the rotational movement, and wherein the absorber mass carrier (570) and the at least one absorber mass (580) are configured to guide the at least one absorber mass (580) so that they at a the rotary motion superimposed torsional vibration component is deflected from a rest position.

13. The torsional vibration damper assembly of claim 12, wherein the second torsional vibration damper comprises at least one spring element that engages the absorber mass carrier as an input of the second torsional vibration damper ,

14. The torsional vibration damper assembly of claim 13, wherein the second torsional vibration damper has a hub disc that abuts the at least one spring element and that acts as an output of the second torsional vibration damper. is coupled to the output (630) of the torsional vibration damper assembly (100), or wherein the second torsional vibration damper (150) comprises at least one cover plate (600) which abuts the at least one spring element (610) and serves as the output (630 ) of the second torsional vibration damper (150) is coupled to the output (120) of the torsional vibration damper assembly (100).

15. The torsional vibration damper assembly of claim 1, wherein the input of the torsional vibration damper assembly includes or is coupled to an output of a friction clutch, wherein the friction clutch is configured to engage the friction clutch Rotational motion to the torsional vibration damper assembly (100), and / or wherein the output (120) of the torsional vibration damper assembly (100) is coupled to or includes an output hub (430).