DE102012219194A1 - torsional vibration damper - Google Patents

Abstract

A torsional vibration damper arrangement (100) for a drive train, 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), a damper arrangement (140) and a second torsional vibration damper (150), the first torsional vibration damper (130) being arranged radially outside of the second torsional vibration damper (150), the damper arrangement (140) and the first torsional vibration damper (150) being mutually exclusive overlap radially at least partially, the torsional vibration damper arrangement (100) being designed in such a way as to prevent the rotary movement from the input of the torsional vibration damper arrangement (100) first to the first torsional vibration damper (130) and then to the second torsional vibration damper (150) and / or of the damper arrangement (140), and wherein the first torsional vibration damper (130) is designed such that the rotary 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 assembly (100) to the second torsional vibration damper (150) and / or the damper arrangement (140).

Description

Embodiments relate to a torsional vibration damper arrangement for a drive train, as it can be used for example in the context of a motor vehicle and here in particular in the field 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.

As part of a drive train of such a motor vehicle Torsionsschwingungsdämpferanordnungen be used, for example, according to the two-damper transducer principle (ZDW) work. In these, a speed-adaptive absorber is often arranged between two dampers on the so-called intermediate mass of the same. A Tilger differs from other Torsionsschwingungsdämpfern in that in this the rotational movement does not run through corresponding energy-storing elements, but rather these are only stimulated to appropriate vibrations 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 specific 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 so as to increase the effect of this vibration reduction unit.

The DE 10 2008 057 648 A1 relates to a power transmission device, in particular for power transmission between an engine and an output, in which a speed-adaptive absorber is arranged between two series-connected dampers. The DE 10 2009 024 743 A1 refers to a hydrodynamic torque converter in which a speed-adaptive absorber between piston and spring is integrated. The WO 2011/110146 A1 finally 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 power train 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 rotary 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 the 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 the damper assembly, wherein the first torsional vibration damper is configured such that the rotational movement from the first torsional vibration damper to a first torsional vibration damper the input of the torsional vibration damper assembly facing side of the first torsional vibration damper is transmitted to the second torsional vibration damper and / or the Tilgeranordnung.

One embodiment of a torsional vibration damper arrangement is based on the finding that a compromise between the damping capability of the Torsionsschwingungsdämpferanordnung on the one hand and the axial space on the other 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 space is positively influenced by the fact that the first torsional vibration damper is just designed such that the rotational movement is transmitted to the subsequent components at the side of the first torsional vibration damper facing the input of the torsional vibration damper arrangement.

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 torsional vibration damper assembly to the first torsional vibration damper on a side of the first torsional vibration damper facing the input of the torsional vibration damper assembly. This makes it possible to save additional axial space by both the input and 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 installation space 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. As a result, it may possibly be possible to save axial space 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.

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 the turbine wheel along an axial direction of the torsional vibration damper arrangement. This may possibly make it possible to reduce the axial space of the torsional vibration damper assembly or the hydrodynamic starting element by the turbine wheel is at least partially disposed radially within 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 welded. 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 Torsionsschwingungsdämpferanordnung can be reduced and so the axial 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 include 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, in such a torsional vibration damper arrangement according to an exemplary embodiment, the second torsional vibration damper may comprise at least one spring element which is in contact with the absorber mass carrier as 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 also to save axial space as necessary by eliminating corresponding connecting elements.

Optionally, in a torsional vibration damper assembly according to an embodiment, the second torsional vibration damper may include a hub disc in abutment with the at least one spring member and coupled as an output of the second torsional vibration damper to 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. A hub disc is in this case typically centrally, that is arranged centrally to the at least one spring element, while the at least one cover plate is arranged axially offset from the at least one spring element. By both constructions, a compact and thus axial space-saving implementation of a torsional vibration damper arrangement 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 assembly may also be coupled to or include 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. In addition to such a frictional contact, however, a frictional contact also includes a frictional 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 merges substantially in terms of form in itself, ie with a corresponding rotation substantially to itself in the mathematical sense is mapped. 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 the 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 Torsionsschwingungsdämpferanordnung according to an embodiment;

2 shows a cross-sectional view through a hydrodynamic starting element with a Torsionsschwingungsdämpferanordnung according to an embodiment;

3 shows a cross-sectional view through a hydrodynamic starting element with a Torsionsschwingungsdämpferanordnung 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 Torsionsschwingungsdämpferanordnung according to an 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 Torsionsschwingungsdämpferanordnung according to an embodiment in which the Tilgeranordnung comprises a common Tilgermassenträger, which also serves as an output member of a first torsional vibration damper and as an input member of a two torsional vibration damper;

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

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

8th shows a schematic representation of a drive train with a Torsionsschwingungsdämpferanordnung according to an 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 by the same reference numerals may be the same, but possibly also different, in terms of individual, several or all features, for example their dimensions, unless otherwise explicitly or implicitly stated in 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 therefore arranged essential parts of the drive train 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 outward.

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. Such an arrangement can thus possibly limit their effectiveness and thus the effectiveness of the speed-adaptive absorber. 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. Also, this may possibly lead to a restriction of the functionality of a corresponding speed-adaptive filter, which could possibly be exposed during operation even an increased risk of mechanical damage.

As has already been 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 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, therefore, hydrodynamic starting elements will be described below, although torsional vibration damper arrangements according to one exemplary embodiment may also be used for other components.

1 shows a schematic representation of a Torsionsschwingungsdämpferanordnung 100 according to an embodiment of an in 1 not shown drive train. 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. The torsional vibration damper assembly 100 is here just designed and designed so that this rotational movement of an input 110 to an exit 120 transfers. Both the entrance 110 as well as the exit 120 Here are the torsional vibration damper 100 ,

The torsional vibration damper assembly 100 includes a first torsional vibration damper 130 , an absorber arrangement 140 and a second torsional vibration damper 150 , The representation in 1 shows the arrangement of the individual components 130 . 140 . 150 relative to an axial direction 160 which is the axis of rotation of the torsional vibration damper assembly 100 acts and in the axial direction 160 vertical radial direction 170 , Such is the torsional vibration damper 130 radially outside of the second torsional vibration damper 150 arranged while the absorber arrangement 140 and the first torsional vibration damper 130 overlap each other at least partially radially.

The entrance 110 is with the first torsional vibration damper 130 coupled so that the rotational movement of the input 110 to the first torsional vibration damper 130 is transmitted. From this, the rotational movement in a damped with respect to rotational irregularities form the Tilgeranordnung 140 provided this at the in 1 shown embodiment of the second torsional vibration damper 150 which outputs with the output 120 the torsional vibration damper assembly 100 is coupled. The first torsional vibration damper 130 is here just designed so that the rotational movement of this at one of the entrance 110 the torsional vibration damper assembly 100 facing side of the first torsional vibration damper 130 to the absorber arrangement 140 be transmitted. In other embodiments, additionally or alternatively, the rotational movement of the first torsional vibration damper 130 as well from the first torsional vibration damper 130 to the second torsional vibration damper 150 be transmitted. In other words, in different embodiments, the rotational movement from the first torsional vibration damper may be in series with the second torsional vibration damper and the damper assembly 140 However, it can also be implemented a parallel transmission of the rotational movement.

At the in 1 The embodiment shown is the first torsional vibration damper 130 at one of the entrance 110 the torsional vibration damper assembly 100 opposite side of the Tilgeranordnung 140 arranged. Likewise, the rotational movement of the input 110 at the entrance 110 facing side of the first torsional vibration damper 130 fed. Thus, the first torsional vibration damper 130 with respect to the supply and the discharge of the rotational movement completely at the entrance 110 connected side.

In order to make this possible in the embodiment shown here, the rotational movement along the axial direction 160 radially inward from the entrance 110 to the first torsional vibration damper 130 as this is rotational movement of the first torsional vibration damper 130 to the second torsional vibration damper 150 or the absorber arrangement 140 is transmitted. Thereby, the supply of the rotational movement in a range can take place, which is typically for the implementation of others attenuation-relevant components is less interesting. In particular, so this arrangement can be a transmission of the rotational movement of the first torsional vibration damper 130 radially outward lying to the Tilgeranordnung 140 or the second torsional vibration damper 150 enable. Even if 1 shows a schematic representation, the arrangements of the components are reproduced correctly with respect to their radial and axial arrangement to each other.

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

The turbine wheel 180 this is typically the same with the output 120 coupled. However, this can be done in different ways, such as for example in connection with the following 2 to 4 is explained in more detail. For example, the turbine wheel 180 immediately with the exit 120 the torsional vibration damper assembly 100 coupled, which is also referred to as RTD interconnection (RTD = Friction clutch torsional vibration damper). Is, however, the turbine wheel 180 on the input side with the second torsional vibration damper 150 connected, this is also referred to as ZDW circuit (ZDW = two-damper converter), while an input-side interconnection of the turbine wheel 180 with the first torsional vibration damper 130 also referred to as a double TTD circuit (TTD = Turbine Torsion Damper). Corresponding embodiments of such circuits are in the 2 . 3 and 4 shown.

2 shows a cross-sectional view through a hydrodynamic starting element 190 , which serves as a torque converter 200 is implemented. The hydrodynamic starting element 190 has such a housing 210 on, which via one or more connecting pins 220 with a connection structure 230 rotatably connected to a crankshaft of a drive motor is connectable. The connection structure 230 is here as a flexible connection element 240 implemented, which may be configured, for example, at least partially intercept and damp wobble movements of the drive motor.

The housing 210 is here in two parts with a drive motor facing the first housing shell 250 and a downstream of a second transmission facing housing shell 260 designed. The two housing shells 250 . 260 Here are about a weld 270 however, in other embodiments may be interconnected by other connection techniques. The second housing shell 260 is also used as a pump shell 280 denotes a bulge 290 includes, in the several shovel lobes 300 are attached. The shovels 300 are in the embodiment shown here in the pump shell 280 via corresponding projections 310 that engage with corresponding depressions 320 the pump shell 280 are connected by plugging and soldering the same cohesively. The shovels 300 are beyond a connecting plate 330 inside the case 210 connected.

The housing 210 is via a weld on a housing hub 340 taken and filled via appropriate holes with a liquid medium, such as an oil during operation. The pump shell 280 and the shovels 300 form such a pump 350 for that in the case 210 located liquid medium when the housing 210 over the connecting pins 220 is placed in a corresponding rotational movement. The impeller 350 This generates a flow of hydraulic medium, which is on a turbine wheel 180 of the hydrodynamic starting element 190 is directed. The turbine wheel 180 this includes a turbine shell 370 and a plurality of blades 380 which have similar projections 390 and recesses 400 with the turbine shell 370 are connected. This is done by a corresponding passing through the projections 390 the shovel flap 380 through the recesses 400 and then soldering them to the turbine shell 370 created a substantially cohesive connection. The soldering can be complementary or exclusive. Also the turbine wheel 180 points, comparable to the impeller 350 , a corresponding connecting plate 410 on.

The turbine wheel 180 is here just arranged so that the of the impeller when moving the housing 210 generated hydraulic power turbine wheel 180 put in a rotary motion. For this purpose is shown at the here Embodiment, the turbine wheel 370 via a riveted joint 420 with an output hub 430 connected, via a gearing with a transmission input shaft 440 is engaged.

To a corresponding torque gain in the presence of a larger speed difference between the turbine wheel 180 and impeller 350 to allow, has the hydrodynamic starting element 190 Furthermore, a stator 450 on, which has a freewheel 460 inside the case 210 is guided.

The hydrodynamic starting element 190 also has a lock-up clutch 470 on that as a friction clutch 480 is implemented. So this has a friction lining 490 on, for example, with a piston 500 can be connected. The piston 500 can along the axial direction 160 in the case 210 be moved so as to create a frictional contact or solve. Is the friction lining 490 with the piston 500 connected, the housing has 210 or the first housing shell facing the drive motor 250 in the area of the friction lining 490 typically a corresponding counter friction surface over which the friction lining 490 with its friction surface can build a frictional or non-positive connection. As a result, the rotational movement of the housing 210 on the piston 500 be transmitted.

The piston 500 is here as part of an actuating element of the friction clutch 480 or lockup clutch 470 configured, wherein the respective operation via a change of pressure conditions in a first volume 510 towards a second volume 520 is feasible. By a corresponding control of the pressure conditions in the two volumes 510 . 520 so can the friction clutch 480 by moving the piston 500 along the axial direction 160 closed or opened. The piston 500 is about a distance rally 530 with an input component 540 of the first torsional vibration damper 130 rotatably connected. The entrance component 540 can be made here, for example, as a deep-drawn sheet metal component.

The first torsional vibration damper 130 further comprises at least one spring element 550 which is directly or indirectly in contact with the input component 540 stands. More specifically, the first torsional vibration damper comprises 130 a plurality of circumferentially distributed spring elements 550 at least partially for temporarily storing an energy of one of the rotary motion superimposed rotational irregularity or torsional vibration. Accordingly, the first torsional vibration damper 130 an output component 560 on, which in the embodiment shown here implemented as bow or coil springs spring elements 550 radially outwardly substantially encloses. The spring elements 550 stand here with the output component 560 also directly or indirectly in attachment.

The first torsional vibration damper 130 is here as part of a Torsionsschwingungsdämpferanordnung 100 implemented according to an embodiment, wherein the piston 500 the entrance 110 the torsional vibration damper assembly 100 represents. As will be discussed later, the output hub forms 480 in the embodiment shown here, the output 120 the output of the torsional vibration damper assembly 100 ,

The starting component 560 as well as the entrance component 540 are here at one of the entrance 110 facing side of the first torsional vibration damper 130 guided along. The entrance component 540 In this case, it is arranged radially further inward than the corresponding output component 560 , which at the same time as the entrance of the Tilgeranordnung 140 serves. The starting component 560 of the first torsional vibration damper 130 serves as an absorber mass carrier at the same time 570-1 the absorber arrangement 140 ,

In addition to the Tilgermassenträger 570-1 has the absorber arrangement 140 Furthermore, another Tilgermassenträger 570-2 on, between which a plurality of absorber masses 580 are arranged so that they in the event of rotational irregularity relative to the absorber mass carriers 570 can move. In other words, the absorber mass carriers 570 and the absorber masses 580 just designed so that the absorber masses 580 be deflected from a rest position when the absorber assembly 140 a rotational irregularity, so for example a torsional vibration component is exposed. This can be implemented, for example, by the absorber mass carriers 570 as well as the absorber masses 580 each have guideways on which guide rollers, for example, as a stepped rollers 670 can be implemented, run along. This allows a relative movement of the absorber masses 580 related to the Tilgermassenträger 570 respectively.

The Tilgermassenträger 570-2 in turn provides an output of the absorber assembly 140 and an input component 590 of the second torsional vibration damper 150 In the in 2 shown embodiment of a torsional vibration damper assembly 100 Here is the Tilgermassenträger 570-2 So the input component 590 as cover sheet 600-1 executed, which as well as in connection with the torsional vibration damper 130 was described with at least one spring element 610 directly or indirectly in contact. About another distance riveting 620 is another cover plate 600-2 also as an entrance component 590 of the second torsional vibration damper 150 designed. Also with this are the spring elements 610 of the second torsional vibration damper 150 directly or indirectly in attachment.

The cover plates 600 are here just designed so that these are the spring elements 610 , which in turn are implemented as bow and coil springs, eccentrically touching with respect to their center. In a center of the spring elements 610 these stand with an output component 630 of the second torsional vibration damper 150 directly or indirectly in the system, which is more specifically a hub disc 640 acting on one of the axis and the axial direction 160 facing region of the hydrodynamic starting element 190 about the riveting 420 as well with the output hub 430 mechanically non-rotatably connected.

The further distance riveting 620 is in this case radially inward of the second torsional vibration damper 150 or its spring elements 610 executed. Nevertheless, the cover plates 600 based on the hub disc 640 and at least with respect to an angular section to allow free mobility, has the hub disc 640 an arcuate oblong hole which extends over the respective angular range and through which the further distance riveting 620 can extend so 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 area of the hub disc 640 is.

Accordingly, also show the cover plates 600 in the area of distance riveting 530 correspondingly designed arcuate slots through which the distance riveting 530 extends through it, so that the input component 540 of the first torsional vibration damper 130 based on the cover plates 600 Similarly, a corresponding at least over a certain angular range free mobility allows.

So is the friction clutch 480 So the lock-up clutch 470 closed, so the friction lining 490 the frictional connection between the housing 210 and the piston 500 produces, so the torque is directly from the housing 210 on the piston 500 and further along a torque path 650 transfer. The torque path 650 so runs from the entrance 110 the torsional vibration damper assembly 100 So the piston 500 , about the distance rally 530 , the entrance component 540 , the spring elements 550 and the starting component 560 of the first torsional vibration damper 130 , From there, the torque on the as well as Tilgermassenträger 570-1 serving starting component 560 on the absorber arrangement 140 and the other Tilgermassenträger 570-2 transmitted from where the torque over the two cover plates 600 , where the cover plate 600-1 identical to the Tilgermassenträger 570-2 is, the spring elements 610 and the hub disc 640 as a starting component 630 of the second torsional vibration damper 150 about the riveting 420 to the exit 120 in the form of the output hub 130 is transmitted.

At the in 2 In the embodiment shown, in contrast to a conventional solution, the torque is from the output part or output component 560 of the first torsional vibration damper on the motor side guided radially inward. This creates axial space and allows the output component 560 the outer torsional vibration damper (first torsional vibration damper 130 ) simultaneously as Tilgermassenträger, which is also used as a support part of the speed-adaptive absorber 140 is called to use.

By this arrangement, it is also possible a web-guided speed-adaptive Tilgerkonstruktion in the form of Tilgeranordnung 140 represent, in which also called DAT masses (DAT = speed-adaptive absorber) absorber masses 580 and the outer first torsional vibration damper 130 are arranged on the same or a comparable radial space.

For this purpose, the torque is based on the piston 500 initially radially within the Tilgeranordnung 140 to the entrance component 540 the outer first torsional vibration damper 130 to hand over. The chambering of the outer first torsional vibration damper 130 takes place in the embodiment shown here by the output component 560 , which in turn can provide advantages in terms of space.

Also known as the second track of the speed-adaptive absorber Tilgermassenträger 570-2 will be at the in 1 shown embodiment of a torsional vibration damper assembly 100 at the same time as input part or input component 590 for the inner second torsional vibration damper 150 used. The torsional vibration damper assembly 100 , which is also referred to as a vibration reduction unit, can be performed as capital letters ZDW circuit, RTD circuit or as a double TTD circuit depending on the circuit. At the in 2 shown embodiment is is an RTD arrangement in which the turbine wheel 180 (Turbine) non-rotatably with the output hub 430 the torsional vibration damper assembly 100 connected is.

At the in 2 embodiment shown are the absorber masses 580 the absorber arrangement 140 executed in several parts. Thus, in the exemplary embodiment shown here, they have two individual-type adhesive masses 660-1 . 660-2 up, over the step rolls 670 in axial communication with each other. The two single-piece masses 660-1 . 660-2 are like that on the step rolls 670 arranged that they can be independently deflected from their respective rest positions.

Of course, in other embodiments, the absorber masses 580 also in one piece or with more than two individual parts 660 , For example, three or more corresponding Einzeletilgermassen 660 exhibit.

The implementation as a multipart absorber mass 580 In this case, for example, can bring cost advantages, since several axially thin plates to a total absorber mass 580 can be assembled. Of course, the previously mentioned one-piece absorber mass 580 be used in embodiments.

Instead of in 2 shown construction of the turbine wheel 370 with the respective projections 390 passing through the turbine shell 370 protrude and are soldered there to form a material connection, can be used to further reduce radial and / or axial space also another connection technique. Thus, the relevant projections 390 with regard to their corresponding recesses 400 just be designed so that this indeed in the recesses 400 are insertable, but do not protrude beyond a side facing away from the respective blade side. In other words, the blades can 380 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.

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

As a result, it may be possible to also use a rotational nonuniformity or a torsional vibration component, which is superimposed on the rotational movement, with the aid of the second torsional vibration damper 150 at least to dampen, if not completely remove from the rotational movement.

Accordingly, at the in 3 shown solution, the riveted joint 420 that the hub disc 640 So the starting component 630 of the second torsional vibration damper 150 with the output hub 430 connects so designed that this just the turbine shell 370 of the turbine wheel 180 not recorded.

4 shows a cross-sectional view through another hydrodynamic starting element 190 based on a torque converter 200 attached to a torsional vibration damper assembly 100 measured embodiment. Again, the torque converter 200 through the use of a friction clutch 480 implemented lock-up clutch 470 be bridged.

The structure of the torsional vibration damper assembly 100 and the torque converter 200 corresponds to the basic structure, as this already in 2 was explained. However, the solution presented here differs in terms of some more details. For example, the turbine wheel, also referred to as turbine 180 arranged here in the form of a double TTD circuit. For this purpose, the turbine shell 370 made smaller and so does not extend into the area of the output hub 430 approach. Rather, compared to the in 2 solution shown the input component 540 of the first torsional vibration damper 130 pulled radially inward and over a riveting 690 with the turbine shell 370 rotatably connected. Accordingly, that of the impeller 350 on the turbine wheel 180 transmitted rotational movement on the input side of the first torsional vibration damper 130 provided. Thus, not just one over the lock-up clutch 470 coupled rotary motion but also one on the turbine wheel 180 coupled rotational movement both over the first torsional vibration damper 130 as well as the second torsional vibration damper 150 and the absorber arrangement 140 directed.

To a possible unchanged acquisition of as many components of the above-described hydrodynamic starting elements 190 to allow that in 4 shown hydrodynamic starting element an optional sheet 700 on which about the riveting 680 out 3 with the input component 590 of the second torsional vibration damper 150 or the second cover plate 600-2 connected is. That's how the metal stands 700 with the stator 450 axially in abutment, as in the previously described embodiments with respect to the stator 450 and the turbine shell 370 the case was. Thus, in the embodiments described above, the guide wheels 450 each with the turbine shells 370 the turbine wheels 180 axially in contact.

Nevertheless, at least over a limited angular range free pivoting of the input component 590 of the second torsional vibration damper 150 opposite the exit 120 to allow, is the rivet connection 420 between output hub 430 and the as a starting component 630 acting hub disc 640 as in 3 executed. In other words, the rivet connection couples 420 Although the starting component 630 of the torsional vibration damper to the output hub 430 but does not create a rotatable connection to the optional plate 700 ,

In addition, the Tilgeranordnung differs 140 with regard to the design of the absorber mass 580 from the embodiments described above. While in the embodiments described above, two-piece absorber masses 580 with two single-piece masses 660-1 . 660-2 is used in the in 4 embodiment shown in one piece executed absorber mass 580 between the absorber mass carriers 570-1 . 570-2 arranged. As already explained, this shows the different possibilities, such as the absorber masses 580 can be implemented.

4 further shows an embodiment in which on the turbine wheel 180 the shovels 380 are connected to the turbine shell by means of the previously described soldering, welding or other material connection. As already explained before, the in 4 no more than such recognizable projections 390 the recesses 400 in the turbine shell 370 not, so by the absence of a corresponding rewinding of the projections 390 axial space can also be saved here again.

5 shows a cross-sectional view through a hydrodynamic starting element 190 , which in turn based on a torque converter 200 is implemented. Again, includes the hydrodynamic starting element 190 a torsional vibration damper assembly 100 according to an embodiment with the first torsional vibration damper 130 , the second torsional vibration damper 150 and the absorber arrangement 140 , Again, this is the turbine shell 370 of the turbine wheel 180 directly against rotation with the output hub 430 So the exit 120 the torsional vibration damper assembly 100 coupled, as in 2 is shown. However, here the corresponding connection differs due to a structurally different design of the second torsional vibration damper 150 from the in 2 shown.

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

Starting from the entrance 110 the torsional vibration damper assembly 100 , which in turn is the piston 500 the lockup clutch 470 is, in turn, about the distance rally 530 the torque radially inward of the input member 540 of the first torsional vibration damper 130 transmitted, which is essentially not from the in 2 shown differs. This in turn is associated with a plurality of spring elements 550 directly or indirectly in attachment. These are in turn with the starting component 560 of the first torsional vibration damper 130 indirectly or directly in abutment, which, however, in one piece at an outer radial end of Tilgeranordnung 140 extends and as Tilgermassenträger 570 is designed.

The absorber arrangement 140 according to 5 has a first single-piece shotgun 660-1 and a second absorber mass 660-2 on, on either side of the absorber mass carrier 570 over a step roll 710 and corresponding guideways in the absorber masses 580 and the absorber mass carrier 570 are guided. The two absorber masses 660-1 and 660-2 are not connected to each other in this embodiment, so basically can be independently deflected from their respective rest positions.

The Tilgermassenträger 570 or the output component 560 of the first torsional vibration damper 130 extends further radially inwardly and forms a central between two cover plates 600-1 . 600-2 arranged input component 590 of the second torsional vibration damper 150 , To here at least over a certain angular range free and independent movement of this combined component, which in the following as Tilgermassenträger 570 is referred to, with respect to the input member 540 of the first torsional vibration damper 130 to allow, this has an arcuate slot through which the distance riveting 530 extends, with the help of which the piston 500 and the entrance component 540 of the first torsional vibration damper 130 are coupled together rotationally fixed. As previously described, the oblong hole has an extension in the radial direction which is greater than a diameter of the spacer riveting 530 ,

The Tilgermassenträger 570 thus forms not only the output member of the first torsional vibration damper 130 but also the input component 590 the second torsional vibration damper, which, in contrast to the embodiments previously shown centrally with the spring elements 610 of the second torsional vibration damper 150 directly or indirectly in contact. The two cover plates 600-1 . 600-2 make up accordingly the initial components 630 of the second torsional vibration damper 150 , Here is the cover plate 600-2 that the turbine wheel 180 is facing, about the riveting 680 with the turbine shell 370 rotatably connected, while that the piston 500 or the entrance 110 facing cover plate 600-1 over the riveted joint 420 with the exit 120 or the output hub 430 rotatably connected. In addition, the two cover plates 600 via a riveted joint 720 also connected to each other rotatably.

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

In addition, in this embodiment, contrary to the embodiments described and shown above, the absorber masses 660-1 and 660-2 not over axially spaced web plates in the form of two Tilgermassenträger 570-1 . 570-2 guided. The absorber masses 660-1 and 660-2 rather, in the axial direction on both sides of the absorber mass carrier 530 or at the output member of the outer first torsional vibration damper 130 attached. Furthermore, this output component becomes 560 the outer first torsional vibration damper 130 also as an entrance component 590 the inner second torsional vibration damper used. Accordingly, as output components of the inner second torsional vibration damper 150 the two cover plates 600-1 . 600-2 used.

Even if the already in 2 shown RTD circuit of the turbine wheel 180 in 5 As previously described, the turbine wheel may be used 180 by various circuit variants to the torsional vibration damper assembly 100 or their output 120 in the form of the output hub 430 be coupled.

6 shows a cross-sectional view through another hydrodynamic starting element 190 which is designed as a torque converter. This is like already in 3 shown configured so that the turbine wheel 180 about the riveting 680 with the as input component 590 serving second cover plate 600-2 of the second torsional vibration damper 150 connected is. As already related to 3 has been described, so is the turbine wheel 180 over the second torsional vibration damper with the output 120 the torsional vibration damper assembly 100 in the form of the output hub 430 rotatably coupled.

Otherwise, the first torsional vibration damper is different 6 not of that in 3 shown. Also the connection to the absorber arrangement 140 as well as the design of the Tilgeranordnung 140 with two absorber mass carriers 570-1 . 570-2 between those absorber masses 580 are movably arranged, the two Einzeletilgermassen 660-1 . 660-2 are identical to those in 3 designed embodiment shown.

However, the configuration of the first torsional vibration damper differs 130 from the in 3 shown execution. With regard to the starting component 560 , which at the same time also the first Tilgermassenträger 570-1 This is designed so that this is the input component 540 passes through or that the input component 540 the starting component 560 be upheld. The two components 540 . 560 In this case, they can 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 surrounds 540 the spring elements 550 of the first torsional vibration damper 130 not completely, but leaves them radially outside at least partially open. This may make it possible to use larger springs or spring elements 550 insert, since a channel in which the spring elements 550 are arranged, is open at the top. As a result, it may be possible, the performance of the torsional vibration damper assembly 100 continue to improve.

Nevertheless, a guide of the spring elements 550 in the first torsional vibration damper 130 to allow the input member has 540 a guide plate 730 on which with the input component 540 is riveted and a support of the spring elements 550 allows radially inward. In addition, the input component points 540 an investment section 740 on, over which the spring elements 550 directly or indirectly with the entrance component 540 in plant. This investment section 740 extends completely over an axial width of the spring elements 550 and has a guide portion 750 on, with the help of which the spring elements at least partially in the axial direction to a piston 500 or the entrance 110 away side is performed. Accordingly, the input component 540 as well as another leadership section 760 on, the spring elements 550 radially outward and in the axial direction towards the entrance 110 or the piston 500 lead.

In the in the 2 . 3 . 4 and 6 shown embodiments of a Torsionsschwingungsdämpferanordnung 100 are the radial sections of the input components 540 and the starting components 560 the outer first torsional vibration damper 130 respectively the entrance 110 , So left in the relevant figures, from a spring center of the spring elements 550 arranged. In other words, in these embodiments, the input member 540 and the starting component 560 of the first torsional vibration damper 130 on a common side eccentric to the at least one spring element 550 with this in attachment. The common side is in this case in the embodiments shown here that of the Torsionsschwingungsdämpferanordnung 100 facing side of the first torsional vibration damper 130 , In conventional solutions, the relevant input components and output components are often arranged on both sides. This also can be saved in comparison to a conventional solution, if necessary, axial space.

7 shows a cross-sectional view through another hydrodynamic starting element 190 , which is based on a torque converter 200 is implemented. This in 7 shown starting element 190 with its torsional vibration damper arrangement 100 According to one embodiment, this is very similar to the in 3 shown variant. The two in the 3 and 7 However, variants shown differ in terms of two embodiments. Such is the absorber mass 580 at the in 7 shown Torsionsschwingungsdämpferanordnung 100 as well as in 4 designed in one piece.

In addition, the connection of serving as an input piston 500 to the entrance component 540 of the first torsional vibration damper 130 not about a distance rally 530 but implemented by means of a plug connection 770 , The plug connection 770 this includes a bent sheet metal 780 using a riveting 790 with the piston 500 connected is. The plug connection 770 or the bent sheet metal 780 pass through the two cover plates 600-1 . 600-2 which also turn here as input components 590 of the second torsional vibration damper 150 serve. The cover plates 600 and the bent sheet metal 780 are here designed so that in this case a relative movement of the input component 540 of the first torsional vibration damper 130 to the cover plates 600-1 . 600-2 So the input component 590 of the second torsional vibration damper 150 is possible.

The plug connection 770 is however with the input component 540 engage such that upon rotation of the piston 500 around the axial direction 160 over the plug connection 770 also the entrance component 540 of the first torsional vibration damper 130 taken along and put into rotation.

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

8th finally shows a schematic representation of a drive train 800 with a torsional vibration damper assembly 100 according to an embodiment, between a drive motor 810 , which is also referred to simply as an engine, and a transmission 820 is switched. The motor 810 it's like that at the entrance 110 , The gear 820 to the exit 120 the torsional vibration damper assembly 100 connected. Here are the simplification of the presentation other components of the hydrodynamic starting element 190 , ie in particular the components of the torque converter, for example the turbine wheel 180 as well as the impeller 350 , Not shown.

8th illustrates the series connection of the first torsional vibration damper 130 with its spring elements 550 which are often referred to simply as the first spring set. The first torsional vibration damper 130 is the Tilgeranordnung also called Tilgereinheit 140 downstream, to which the second torsional vibration damper 150 with its also called second spring set spring elements 610 followed.

Optionally, the first spring set, so the spring elements 550 of the first torsional vibration damper 130 in the power flow from the engine 810 to the transmission 820 in front of the absorber arrangement 140 lie, are designed in one stage. Here, the interpretation of these spring elements or the first torsional vibration damper 130 For example, carried out so that this based on a maximum einleitbares or existing torque an attack safety of a maximum of 1.15 times a rated torque of the drive motor 810 includes. The drive motor 810 This is sometimes referred to as a prime mover.

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 additionally, 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.

LIST OF REFERENCE NUMBERS

100

torsional vibration damper

110

entrance

120

output

130

first torsional vibration damper

140

Tilgeranordnung

150

second torsional vibration damper

160

axial direction

170

radial direction

180

turbine

190

Hydrodynamic starting element

200

torque converter

210

casing

220

connecting pins

230

connecting structure

240

flexible connection element

250

first housing shell

260

second housing shell

270

welding

280

pump shell

290

bulge

300

Blade tab

310

head Start

320

deepening

330

connecting plate

340

housing hub

350

impeller

370

turbine shell

380

Blade tab

390

head Start

400

recess

410

connecting plate

420

rivet

430

output hub

440

Transmission input shaft

450

stator

460

freewheel

470

lock-up clutch

480

friction clutch

490

friction lining

500

piston

510

first volume

520

second volume

530

Distanzvernietung

540

input member

550

spring element

560

output component

570

Tilgermassenträger

580

absorber mass

590

input member

600

Cover plate

610

spring element

620

Further distance riveting

630

output component

640

hub disc

650

torque path

660

Einzeltilgermasse

670

step roller

680

clinch

690

clinch

700

sheet

710

step roller

720

rivet

730

guide plate

740

contact section

750

guide section

760

Another leadership section

770

connector

780

Bent sheet metal

790

clinch

800

powertrain

810

drive motor

820

transmission

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The 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

• DE 102008057648 A1 [0006]
• DE 102009024743 A1 [0006]
• WO 2011/110146 A1 [0006]

Claims (15)

Torsional vibration damper arrangement ( 100 ) for a drive train ( 800 ), such as a motor vehicle, wherein the Torsionsschwingungsdämpferanordnung ( 100 ) is adapted to a rotational movement of an input ( 110 ) of the torsional vibration damper arrangement ( 100 ) to an output ( 120 ) of the torsional vibration damper arrangement ( 100 ), having the following features: a first torsional vibration damper ( 130 ); an absorber arrangement ( 140 ); and a second torsional vibration damper ( 150 ), wherein the first torsional vibration damper ( 130 ) radially outside of the second torsional vibration damper ( 150 ) is arranged; wherein the absorber arrangement ( 140 ) and the first torsional vibration damper ( 150 ) overlap each other radially at least partially; the torsional vibration damper arrangement ( 100 ) is designed such that the rotational movement of 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 the absorber arrangement ( 140 ) transferred to; and wherein the first torsional vibration damper ( 130 ) is formed so that the rotational movement of the first torsional vibration damper ( 130 ) at one of the entrance ( 110 ) of the torsional vibration damper arrangement ( 100 ) facing side of the first torsional vibration damper ( 130 ) to the second torsional vibration damper ( 150 ) and / or the absorber arrangement ( 140 ) is transmitted. Torsional vibration damper arrangement ( 100 ) according to claim 1, wherein the first torsional vibration damper ( 130 ) at one of the entrance ( 110 ) of the torsional vibration damper arrangement ( 100 ) facing away from the Tilgeranordnung ( 140 ) is arranged. Torsional vibration damper arrangement ( 100 ) according to claim 2, in which the rotational movement along an axial direction ( 160 ) radially further inboard of the entrance (FIG. 110 ) of the torsional vibration damper arrangement ( 100 ) to the first torsional vibration damper ( 130 ) is guided as the rotational movement of the first torsional vibration damper ( 130 ) to the second torsional vibration damper ( 150 ) and / or the absorber arrangement ( 140 ) is transmitted. Torsional vibration damper arrangement ( 100 ) according to one of the preceding claims, in which the rotational movement from the entrance ( 110 ) of the torsional vibration damper arrangement ( 100 ) to the first torsional vibration damper ( 130 ) at the entrance ( 100 ) of the torsional vibration damper arrangement ( 100 ) facing side of the first torsional vibration damper ( 130 ) he follows. Torsional vibration damper arrangement ( 100 ) according to one of the preceding claims, in which the first torsional vibration damper ( 130 ) at least one spring element ( 550 ) located between an input component ( 540 ) and an output component ( 560 ) of the first torsional vibration damper ( 130 ) is coupled, and wherein the at least one spring element ( 550 ) comprises a coil spring, a bow spring and / or a barrel spring. Torsional vibration damper arrangement ( 100 ) according to claim 5, wherein the input component ( 540 ) and the starting component ( 560 ) of the first torsional vibration damper ( 130 ) on a common side eccentric to the at least one spring element ( 550 ) are in contact with this. Torsional vibration damper arrangement ( 100 ) according to claim 6, wherein the common side of the entrance ( 110 ) of the torsional vibration damper arrangement ( 100 ) facing side of the first torsional vibration damper ( 130 ). Torsional vibration damper arrangement ( 100 ) according to one of claims 5 to 7, wherein the at least one spring element ( 550 ) radially outside at least partially open. Torsional vibration damper arrangement ( 100 ) according to one of claims 5 to 8, with a turbine wheel ( 180 ) of a hydrodynamic starting element ( 190 ), wherein the at least one spring element ( 550 ) of the first torsional vibration damper ( 130 ) along an axial direction ( 160 ) of the torsional vibration damper arrangement ( 100 ) at least partially radially outside of the turbine wheel ( 180 ) is arranged. Torsional vibration damper arrangement ( 100 ) according to claim 9, wherein the turbine wheel ( 180 ) a turbine shell ( 370 ) and a plurality of blades ( 380 ), wherein the turbine shell ( 370 ) a plurality of recesses ( 400 ) and the plurality of blades ( 380 ) each have at least one projection ( 390 ), wherein the projections ( 390 ) of the blades ( 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 ( 370 ) into the recesses ( 400 ) are insertable so that the projections ( 390 ) substantially not on a side facing away from the blade side, the turbine shell ( 370 ), and wherein the blades ( 380 ) with the turbine shell ( 370 ) are materially connected, for example, soldered or welded, are. Torsional vibration damper arrangement ( 100 ) according to one of the preceding claims, in which the input ( 110 ) of the torsional vibration damper arrangement ( 100 ) via a plug connection ( 770 ), for example, one with the input ( 110 ) riveted or welded bent metal sheet ( 780 ), with an input ( 540 ) of the first torsional vibration damper ( 130 ) connected is. Torsional vibration damper arrangement ( 100 ) according to one of the preceding claims, in which the absorber arrangement comprises at least one absorber mass carrier ( 570 ) and at least one absorber mass ( 580 ), wherein the Tilgermassenträger ( 570 ) is adapted to be subjected to the rotational movement, and wherein the Tilgermassenträger ( 570 ) and the at least one absorber mass ( 580 ) are designed such that the at least one absorber mass ( 580 ) to be guided so that it is deflected in a rotational movement superimposed torsional vibration component from a rest position. Torsional vibration damper arrangement ( 100 ) according to Claim 12, in which the second torsional vibration damper ( 150 ) at least one spring element ( 610 ) associated with the absorber mass carrier ( 570 ) as input ( 590 ) of the second torsional vibration damper ( 150 ) is in plant. Torsional vibration damper arrangement ( 100 ) according to claim 13, in which the second torsional vibration damper ( 150 ) a hub disc ( 640 ), which with the at least one spring element ( 610 ) is in plant and as output ( 630 ) of the second torsional vibration damper ( 150 ) with the output ( 630 ) of the torsional vibration damper arrangement ( 100 ), or in which the second torsional vibration damper ( 150 ) at least one cover plate ( 600 ), which with the at least one spring element ( 610 ) is in plant and as output ( 630 ) of the second torsional vibration damper ( 150 ) with the output ( 120 ) of the torsional vibration damper arrangement ( 100 ) is coupled. Torsional vibration damper arrangement ( 100 ) according to one of the preceding claims, in which the input ( 110 ) of the torsional vibration damper arrangement ( 100 ) an output of a friction clutch ( 480 ) or coupled to it, wherein the friction clutch ( 480 ) is adapted to the rotational movement of the torsional vibration damper assembly ( 100 ) and / or where the output ( 120 ) of the torsional vibration damper arrangement ( 100 ) with an output hub ( 430 ) or includes.

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