DE102017000707A1 - Torsional vibration damper, torsional vibration damper with such a torsional vibration damper and drive train with such a torsional vibration damper - Google Patents

Abstract

The present invention relates to a torsional vibration damper (2) with a base part (18) rotatable about an axis of rotation (16), an inertial mass part (20) associated with the base part (18), which counter to the restoring force of a restoring device (24) relative to the base part (18 ), and an adjusting device (30), wherein the return device (22) by changing the restoring force characteristic of the inertial mass portion (20) acting restoring force by the adjusting device (30) is adjustable. In addition, a friction device (80) is provided, by means of which the adjusting device (30) is frictionally lockable while preventing an adjustment of the return device (22). Furthermore, the present invention relates to a torsional vibration damper and a drive train for a motor vehicle with such a torsional vibration damper (2).

Description

The present invention relates to a torsional vibration damper with a base part rotatable about a rotation axis, an inertial mass part associated with the base part which is rotatable relative to the restoring force of a restoring device relative to the base part, and an adjusting device, the restoring device changing a restoring force characteristic of the restoring force acting on the inertial mass part can be adjusted by the adjustment. Moreover, the present invention relates to a torsional vibration damper with such a torsional vibration damper and a drive train with such a torsional vibration damper.

From the DE 10 2014 001 043 A1 For example, a torsional vibration damper is known, which has a base part rotatable about an axis of rotation and an inertial mass part which is assigned to the base part and which is rotatable relative to the restoring part of a restoring device relative to the base part. In addition, an adjusting device is provided, wherein the return device can be adjusted by changing the restoring force characteristic of acting on the inertial mass restoring force by the adjusting device. Said adjusting device essentially has an actuating part arranged on the base part, which can be rotated relative to the base part about the axis of rotation as a result of an inertial force acting on the actuating part during operation of the torsional vibration damper. In other words, relative movements between the actuating part and the base part for adjusting the restoring device, and thus for adjusting the restoring force acting on the inertial mass part, are used here. If the return device is adjusted to the desired extent, then the adjusting device, here the setting part of the adjusting device, is locked in order to counteract a further adjustment of the return device. For this purpose, the known torsional vibration damper on a hydraulic device by means of which the control part can be hydraulically locked. More specifically, the hydraulic device has a piston-cylinder arrangement, which is associated with the control part. Also, the piston-cylinder arrangement of the hydraulic device is controllable such that it allows the movement of the actuating part in only one of the two directions of rotation in order to adjust the return device targeted in one direction.

The well-known torsional vibration damper with its hydraulic device for locking the adjusting device as well as for the targeted change of the restoring force characteristic has proven itself, but has a relatively large and complex structure. In addition, it is desirable to provide a torsional vibration damper, in which an even faster adjustment of the return device by means of the adjustment is possible.

It is therefore an object of the present invention to develop a torsional vibration damper of the generic type such that this on the one hand has a particularly compact and simple structure and on the other hand allows a quick adjustment of the return device on the adjustment. In addition, the present invention seeks to provide a torsional vibration damper with such an advantageous torsional vibration damper and a drive train for a motor vehicle with such an advantageous torsional vibration damper.

This object is achieved by the features specified in the patent claims 1, 11 and 12, respectively. Advantageous embodiments of the invention are the subject of the dependent claims.

The torsional vibration damper according to the invention has a base part rotatable about a rotation axis. The base part can be formed, for example, by a base plate or carrier plate extending essentially in the radial direction. In addition, the torsional vibration damper on a Trägheitsmassenteil, which is associated with the base part such that it is rotated against the restoring force of a restoring device relative to the base member, preferably rotated about the axis of rotation, can be. For example, the inertial mass portion may undergo torsional vibrations relative to the base portion to achieve the desired erosion effect. The return device, which may for example have a spring device for generating a restoring force, is in turn associated with an adjusting device. With the aid of the adjusting device, the restoring device can be adjusted by changing a restoring force characteristic of the restoring force acting on the inertial mass part. Thus, for example, the slope of the restoring force characteristic curve of the restoring force acting on the inertial mass part can be increased or reduced by adjusting the restoring device, so that the rigidity of the restoring device is increased or reduced analogously. If the restoring force characteristic curve of the restoring force acting on the inertia mass part is achieved by adjusting the restoring device, then the adjusting device can be locked while preventing further adjustment of the restoring device. Unlike in the DE 10 2014 001 043 A1 However, a hydraulic device for hydraulically locking the adjusting device described uses a friction device, by means of which the adjusting device can be locked frictionally locking while preventing an adjustment of the return device. The friction device in which it is For example, may be a frictionally engaged brake or clutch, first has the advantage of a relatively compact and simple construction. It has also been found that when using a friction device instead of a hydraulic device, as is known from the DE 10 2014 001 043 A1 It is known that an even faster adjustment of the return device by means of the cooperating with the friction device adjustment is possible. Moreover, it has been shown that by the friction device, a less lashed locking the adjusting device is possible than in the known hydraulic device for locking the adjusting device. In other words, a more accurate setting or setting of the return device by means of cooperating with the adjusting friction device is possible.

As already stated above, the locking of the adjustment takes place by frictional engagement and not hydraulically. Nonetheless, the frictionally engaged friction device could also be hydraulically driven. However, with the friction-operated friction device instead of the hydraulic locking, the advantage is already achieved that a complex and leakage-prone hydraulic structure is at least partially eliminated, which not only simplifies the construction of the torsional vibration damper, but also allows its use in a dry room. To reinforce this advantage even more, the friction device is electrically driven in a preferred embodiment of the torsional vibration damper according to the invention, so that a hydraulic drive can be omitted.

In an advantageous embodiment of the torsional vibration damper according to the invention with an electrically drivable friction device, the friction device has at least one electrically acted upon piezoelectric element or an electromagnet as an actuator. Both the electrically acted upon piezoelectric element and the electromagnet which can be acted upon react relatively quickly in the event of electrical loading in order to achieve the desired locking or release of the adjusting device. Moreover, both can be arranged relatively space-saving on the torsional vibration damper. In principle, both mentioned actuators can form a friction partner of the friction device itself, which could be the case in particular with the piezoelectric element, which expands due to the electrical impingement and thus can be pressed against a friction partner on the adjusting device.

In a further preferred embodiment of the torsional vibration damper according to the invention, a friction part that can be brought or brought into frictional engagement with the adjusting device can be driven via the actuator, that is to say the piezoelectric element or the electromagnet. In this case, the friction part preferably has a friction or contact surface which reinforces the friction with the adjusting device.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the friction device can be transferred from a locking position, in which the adjusting device is frictionally locked, in a release position, in which the return device can be adjusted by the adjustment, and vice versa. In this case, the friction device is preferably designed such that the adjustment device can be moved without friction in the release position of the friction device relative to the friction device in order to achieve a particularly fast movement of the adjustment and thus also a particularly rapid adjustment of the return device.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the friction device can be driven to reach the locking position, so for example by the aforementioned electric drive. In this case, it is preferred if the friction device is biased in the release position. Alternatively, the friction device for reaching the release position, optionally electrically driven, in which case it is preferred when the friction device is biased into the locking position. In both embodiments, the friction device is preferably biased by at least one cooperating with the aforementioned friction member spring element in the release position or locking position. The selection of the respective embodiment depends essentially on the field of application of the torsional vibration damper. If the reset device must be adjusted relatively frequently, both variants are equally suitable. With a relatively small number of adjustments of the return device, however, the embodiment should be selected, in which the friction device is driven to reach the release position and biased into the locked position to save energy. The latter embodiment variant could also be referred to as a normally closed or normally locked friction device in analogy to clutch devices.

In order to ensure the power supply of the electrically driven friction device, in an especially preferred embodiment of the torsional vibration damper according to the invention an electrical generator for generating electrical energy for the friction device is provided by a relative movement or relative rotation between two components of the torsional vibration damper. Thus, the electric generator, for example, on the be arranged a component of the torsional vibration damper and cooperate via a corresponding transmission means for transmitting the relative movement or rotation with the other component of the torsional vibration damper. Here, it is preferable if the electric generator for generating electrical energy for the friction device is provided by a relative movement or rotation between the base part and the return device. In this embodiment, the electric generator is thus closely linked to the torsional vibration damper itself, so that it can be used together with the torsional vibration damper in a drive train, possibly as a module, without major connection problems occur with an adjacent assembly within the drive train.

As an alternative to the embodiment described above, in which the electric generator is designed as an onboard solution with regard to the torsional vibration damper, the electric generator for generating electrical energy for the friction device is arranged in a further preferred embodiment of the torsional vibration damper according to the invention such that this electrical energy generated from a relative movement or relative rotation between a component of the torsional vibration damper and a component of an adjacent assembly within a drive train. For example, the generator could be arranged on a component of an adjacent subassembly and cooperate with a component of the torsional vibration absorber, such as the inertial mass part, via a corresponding transmission device for transmitting the relative movement or rotation.

In a particularly advantageous embodiment of the torsional vibration damper according to the invention, the generator is associated with an electrical memory for storing the electrical energy for the friction device. As was the case with the generator in a previously mentioned embodiment variant, the electrical accumulator is also preferably arranged on a component of the torsional vibration damper so that it can be installed together with the torsional vibration damper as a module within a drive train. This also eliminates an expensive supply of electrical energy from the memory to the friction device and from the electric generator in the electrical storage. In this embodiment, it is also preferred if the electrical memory for storing the electrical energy generated by the electrical generator is integrated in the generator or at least in the generator housing.

In a further particularly preferred embodiment of the torsional vibration damper according to the invention, the adjusting device has a arranged on the base part and lockable by the friction actuator, which is rotatable relative to the base member about the axis of rotation by adjusting the return device due to an acting on the actuating part inertial force. Accordingly, the adjusting part of the adjusting device is thus also designed as a second inertial mass part. Thus, the adjusting part of the adjusting device makes use of the fact that the base part, despite the inertial mass part which is arranged thereon and which can be rotated against the restoring force of the restoring device relative to the base part, is still subject to torsional oscillations - albeit lower. Due to the inertia of the adjusting part of the adjusting device, the adjusting member can be rotated in a rotational vibration underlying base member alternately both in one direction of rotation and in the opposite direction of rotation relative to the base member about the rotation axis to an adjustment of the return device and thus a change in the restoring force characteristic of To effect the inertial mass part acting restoring force. Thus, the restoring force characteristic can be changed by rotating the setting member in the one rotational direction relative to the base member about the rotation axis in a manner such as decreasing the pitch thereof, while the restoring force characteristic is obtained by rotating the setting member in the opposite rotational direction relative to the base member about the rotation axis the opposite way can be changed, for example by increasing the slope of the restoring force characteristic. Consequently, an inertia-conditioned adjustment of the return device by means of the adjusting part of the adjusting device in both directions is possible. The locking of the adjusting device after the desired adjustment of the return device then takes place via the friction device, by means of which the adjusting part of the adjusting device can be locked by friction.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the friction device can be alternately transferred to the locking position and the release position such that the actuating part in one direction of rotation is rotatable relative to the base part and in the opposite direction of rotation is not rotatable relative to the base part. If the actuator rotates due to inertia in the one direction of rotation relative to the base member, the friction device would remain in the release position, while the friction device would be transferred to the locked position, if the actuator wanted to rotate inertially in the opposite direction of rotation relative to the base member. For this purpose, a control device is preferably provided which on the one hand detects the respective behavior of the setting part in advance and on the other hand transfers the friction device correspondingly into the release position or locking position to the desired Behavior, namely to cause the relative rotation of the actuating part relative to the base part in only one of the two directions.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the restoring device has a spring device for generating a setting force, wherein the spring device may have, for example, a spring element or a plurality of spring elements. In addition, the return device has a pivotable about a pivot point lever element, which can also be spoken by a pivot point. For example, the pivotable lever element can be articulated directly or indirectly to the base part via the point of articulation. Here, it is preferred if the lever element is pivotable in a plane spanned by the radial directions of the torsional vibration damper and thus about an axis extending in the axial directions of the torsional vibration damper through the pivot point. The lever element is arranged on the other hand between the spring device on the one hand and the inertial mass part on the other hand, that the force generated by the spring means can be transmitted to the inertial mass portion generating the acting on the inertial mass restoring force. The articulation point can be moved relative to the base part by changing the restoring force characteristic curve of the restoring force acting on the inertial mass part relative to the base part by the adjusting device, optionally the previously mentioned adjusting part of the adjusting device.

While the DE 10 2014 001 043 A1 teaches to move the articulation point for the pivotable lever element along a radial relative to the base part, the articulation point is movable in a further advantageous embodiment of the torsional vibration damper according to the invention by changing the restoring force characteristic of acting on the inertial mass portion restoring force in the circumferential direction relative to the base part. This has the advantage that a torque is sufficient to move the articulation point in the circumferential direction, without the torque would have to be in a translational movement of the articulation point along a straight line or a radial, which simplifies the construction and operation of the torsional vibration damper. Alternatively or additionally, the articulation point is movable along a circular path section, wherein it has proved to be preferable in this context, when the center of said circular path section is formed by the rotational axis of the torsional vibration damper.

In a further particularly preferred embodiment of the torsional vibration damper according to the invention, the return device has an input side pull / push strut for transmitting power between the spring device and the lever element, which is hinged on the one hand at a Stellkraftangriffspunkt on the spring means and on the other hand on the lever element. Alternatively or additionally, the return device has an output-side pull / push strut for transmitting power between the lever element and the inertial mass part, which is articulated on the one hand to the lever element and on the other hand to a restoring force application point on the inertial mass part. In the first-mentioned alternative can thus be dispensed with a guide or the like at both the force application point and at the articulation point of the lever member, a displaceability of the Stellkraftangriffspunktes relative to the input side pull / push strut or to the spring means or a displacement of the pivot point relative to the lever element guaranteed. In the second alternative, however, can be dispensed with the provision of a guide both in the region of Rückstellkraftangriffspunktes and in the region of the articulation point, the displaceability of Rückstellkraftangriffspunktes relative to the inertial mass portion or the output side pull / push strut or a displacement of the pivot point relative to the Lever element allows. Thus, a largely play-free transmitting leverage lever element and input and / or output side pull / push strut is created, which ensures a substantially backlash-free power transmission between the spring means and the inertial mass portion and also can be relatively easily manufactured. It is understood that the advantages mentioned are particularly pronounced when both the input side pull / push strut and the output side pull / push strut is provided. The term of the push / pull strut makes it clear that on the said strut tensile and / or shear forces in the direction of extension between the spring means and / or the inertial mass part on the one hand and the lever element on the other hand can be transmitted.

As already indicated above, the input-side and / or output-side pull / push struts have the advantage that no guides must be provided in the region of the articulation point and the Stellkraftangriffspunktes and / or restoring force application point to a relative movement of the articulation point, the Stellkraftangriffspunktes and / or the Rückstellkraftangriffspunktes relative to the articulated parts. Consequently, in a further preferred embodiment of the torsional vibration damper according to the invention for at least two points or all points from the set consisting of articulation point, force application point and restoring force application point, that the articulation point fixed to the lever element and the adjusting device, optionally the adjusting part of the adjusting device, the actuating force application point is fixedly arranged on the input side pull / push strut and the spring device and the restoring force application point fixed to the output side pull / push strut and the inertial mass part. Under the fixed arrangement is - as already indicated above - to understand here that a relative movement of the respective point to one of the hinged components is largely prevented, so that a simple and substantially backlash-free joint is created.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the input-side pull / push strut is articulated on an input-side linkage point and / or the output-side pull / push strut on an output-side linkage point on the lever element. It is preferred if the input-side articulation point is fixedly arranged on the input side pull / push strut and the lever element and / or the output side pivot point fixed to the output side pull / push strut and the lever element to a largely backlash-free power transmission in this area enable and simplify manufacturing.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the input-side articulation point and the output-side articulation point are spaced apart from one another.

In a further particularly advantageous embodiment of the torsional vibration damper according to the invention, in which both an input-side and an output-side pull / push strut is provided, the articulation point, the input-side articulation point and the output-side articulation point are each arranged at a corner of an imaginary triangle. The imaginary triangle is preferably an isosceles or equilateral triangle.

According to a further advantageous embodiment of the torsional vibration damper according to the invention, the spring device of the return device comprises a spring element. The spring element is preferably a helical spring or helical compression spring. In this embodiment, it is preferred if the spring element can be acted upon both by generating a restoring force in the one circumferential direction and by generating a restoring force in the opposite circumferential direction, if appropriate in each case by compression. By the one spring element serves both the generation of a force in the one circumferential direction and the generation of the actuating force in the opposite circumferential direction by this is compressed in each case, a particularly compact spring means, thus a particularly compact return device created.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the spring device of the return device has a relative to the base part movable, optionally rotatable and / or annular, spring support element, which could also be referred to as a spring support element, wherein the aforementioned spring element is supported on the spring support element or supportable , In this embodiment, it is preferred if the spring support element, optionally around the rotational axis of the torsional vibration damper, is rotatable and / or annular. The annular design of the spring support member has the advantage that it can also be used to support a spring element of the spring means of another return device within the same torsional vibration damper.

In a further particularly advantageous embodiment of the torsional vibration damper according to the invention, the aforementioned spring support element of the spring device interacts with the electric generator to generate electrical energy from the relative movement or relative rotation between spring support element and base part. As already indicated above, it has proven to be advantageous in this case if the generator is arranged on the base part and optionally cooperates with the spring support element via a transmission device for transmitting the relative movement or relative rotation of the spring support element relative to the base part.

In a further advantageous embodiment of the torsional vibration damper according to the invention, the aforementioned spring element of the spring device in one circumferential direction on the spring support member and a first support portion of the base member and in the opposite circumferential direction on the spring support member and a second support portion of the base member is supported or supported. In order to enable the support in the respective circumferential direction on the spring support element, for example, in each case a protruding approach may be provided on the substantially ring-shaped spring support element.

The torsional vibration damper according to the invention has an input side, so for example, a primary element, an output side, so for example a secondary element, an energy storage for torsionally elastic coupling of input and output side in the circumferential direction, so for example a spring assembly, and a torsional vibration damper of the type according to the invention. In this case, the base part of the torsional vibration damper is rotatably connected to the input or output side of the torsional vibration damper or the base part forms the input or output side of the torsional vibration damper at least partially or entirely.

The drive train according to the invention for a motor vehicle has a torsional vibration damper of the type according to the invention, wherein the base part of the torsional vibration damper rotatably connected to a arranged in the torque transmission path of the drive train component, so for example the input or output side of the aforementioned torsional vibration, or the base part is itself in the torque transmission path arranged the drive train.

• 1 eine Vorderansicht einer Ausführungsform eines Drehschwingungstilgers,
• 2 bis 5 den Drehschwingungstilger aus 1 mit unterschiedlichen Positionen des Anlenkpunktes,
• 6 eine geschnittene Darstellung entlang der Schnittlinie A-A in 1 in einer ersten Ausführungsvariante der Reibvorrichtung und
• 7 eine geschnittene Darstellung entlang der Schnittlinie A-A in 1 mit einer zweiten Ausführungsvariante der Reibvorrichtung.

The invention is explained in more detail below with reference to exemplary embodiments with reference to the accompanying drawings. Show it:

• 1 a front view of an embodiment of a torsional vibration damper,
• 2 to 5 the torsional vibration damper 1 with different positions of the articulation point,
• 6 a sectional view along the section line AA in 1 in a first embodiment of the friction device and
• 7 a sectional view along the section line AA in 1 with a second embodiment of the friction device.

1 shows an embodiment of the torsional vibration damper according to the invention 2 , In the figures, the opposite axial directions 4 , 6, the opposite radial directions 8th , 10 and the opposite circumferential directions 12, 14, which may also be referred to as opposite directions of rotation, of the torsional vibration damper 2 indicated by appropriate arrows.

The torsional vibration damper 2 has one in the axial directions 4 . 6 extending axis of rotation 16 on. The torsional vibration damper 2 points around the axis of rotation 16 in the circumferential directions 12 . 14 rotatable base part 18 on. The base part 18 For example, it may be plate-shaped, wherein the base part 18 preferably in the of the radial directions 8th . 10 spanned plane, here the drawing plane, extends. Within a non-illustrated drive train for a motor vehicle, the base part 18 rotatably connected to a arranged in the torque transmission path of the drive train component or even arranged in the torque transmission path of the drive train. Also, the torsional vibration damper 2 be advantageously combined with a torsional vibration damper. In this case, the torsional vibration damper an input side, so for example, a primary element, an output side, so for example, a secondary element, and an energy storage for torsionally elastic coupling of input and output side in the circumferential direction 12 . 14 on, with the base part 18 the torsional vibration damper 2 rotatably connected to the input or output side or the input or output side of the torsional vibration damper forms wholly or in part. Within the powertrain would be a torsional vibration damper in combination with the torsional vibration damper 2 arranged such that the input and output side of the torsional vibration damper would be arranged in the torque transmission path of the drive train.

The torsional vibration damper 2 also has an inertial mass part 20 on top of that, the base part 18 is assigned in the installed state to a torsional vibration damper and / or within a drive train but not in the torque transmission path of the torsional vibration damper and / or the drive train would be arranged, which is the torsional vibration damper 2 different from a torsional vibration damper. The inertial mass portion 20 is formed substantially annular, so that this in the circumferential direction 12 . 14 closed extends. In this case, the inertial mass part 20 in the radial direction 10 inside on the base part 18 be supported or supported. The inertial mass part 20 is the base part 18 assigned such that this at least in a predetermined rotation angle range about the axis of rotation 16 relative to the base part 18 is rotatable. The inertial mass part 20 is designed such that this is its radial distance a to the axis of rotation 16 regardless of which relative inertia position the inertial mass part retains 20 opposite the base part 18 is arranged.

How out 1 can be seen, the torsional vibration damper 2 two reset devices 22 . 24 on, each other in the radial direction 8th . 10 opposite to the torsional vibration damper 2 arranged and formed substantially identical, so that the return devices 22 . 24 with reference to the return device below 22 described the description of the return device 22 equally for the reset device 24 applies. The reset device 22 consists essentially of a lever device 26 and a spring device 28 together. In addition, the reset device 22 an adjusting device 30 associated the adjustment of the return device described in more detail later 22 serves.

The adjusting device 30 has an actuating part 32, which is substantially directly with the lever device 26 the return device 22 interacts. The control part 32 is annular and circumferential in the circumferential direction 12, 14 and formed relative to the base member 18 about the axis of rotation 16 rotatable in a predetermined rotation angle range. To the control part 32 relative to the base part 18 to twist, can the control part 32 due to the on the control part 32 in the circumferential direction 12 . 14 acting forces during the operation of the torsional vibration damper 2 relative to the base part 18 to be twisted. In any case, however, is the control part 32 in the respective relative rotational position to the base part 18 lockable, which will be discussed in more detail later on the lock. At the control part 32 more precisely at one in the radial direction 8th outward-protruding approach 34 of the control part 32 is a point of articulation 36 provided, the fixed and thus immovable to the control part 32 is arranged so that the control part 32 while moving this articulation point 36 around the axis of rotation 16 relative to the base part 18 is rotatable. Thus serves the control part 32 the movement of the later described in more detail articulation point 36 ,

The spring device 28 the return device 22 has a relative to the base part 18 movable spring support element 38 on, which can also be referred to as a spring support element and the support of a spring element 40 the spring device 28 serves, wherein it is at the spring element 40 should act in the illustrated embodiment by a coil spring or helical compression spring whose longitudinal axis is substantially in the circumferential directions 12 . 14 extends, although the longitudinal axis of the spring element 40 is formed in a straight line in the illustrated embodiment. In principle, however, could here also a spring element 40 with a corresponding in the circumferential direction 12 . 14 curved longitudinal axis, thus a bow spring are used. The spring support element 38 is formed substantially annular, with this in the circumferential direction 12 . 14 closed around the axis of rotation 16 extends and the spring support element 38 at least in a predetermined rotation angle range relative to the base part 18 is rotatable about the rotation axis 16. At the in the radial direction 10 inside, substantially annular body of the spring support element 38 are two in the radial direction 8th outward protruding approaches 42 . 44 provided so that the spring element 40 in the circumferential direction 12 at the neck 42 and in the opposite circumferential direction 14 at the beginning 44 can be supported or supported. In addition, the spring element 40 in the circumferential direction 12 at a first support portion 46 of the base part 18 and in the opposite circumferential direction 14 on a second support section 48 of the base part 18 supportable or supported. Consequently, the spring element 40 both generating a force in the one circumferential direction 12 as well as generating a force in the opposite circumferential direction 14 acted upon by compression. Will the spring support element 38 for example in the circumferential direction 12 relative to the base part 18 twisted, so is the spring element 40 in the circumferential direction 12 at the first support portion 46 of the base part 18 and in the circumferential direction 14 on the salient approach 44 the spring support element 38 supported, so that a force of the spring element 40 the spring device 28 in the circumferential direction 14 on the spring support element 38 acts. Will the spring support element 38 however, in the circumferential direction 14 relative to the base part 18 twisted, so is the spring element 40 in the circumferential direction 14 on the second support section 48 of the base part 18 and in the circumferential direction 12 on the salient approach 42 the spring support element 38 supported, so that the spring element 40 a force in the circumferential direction 12 on the spring support element 38 exercises. In addition, on the spring support element 38 one in the radial direction 8th Outwardly projecting arm 50 arranged, which ultimately serves to transmit the force, as will be explained again later.

The lever device 26 the return device 22 indicates a point of articulation mentioned above 36 pivotable lever element 52 on, for this purpose in the radial direction 10 inside at the neck 34 of the adjusting part 32 in the region of the articulation point 36 is articulated and starting from the point of articulation 36 essentially in the radial direction 8th extends to the outside. More specifically, the lever element 52 around one in the axial direction 4 . 6 through the articulation point 36 extending pivot axis relative to the actuator 32 the adjusting device 30 pivotable. Here is the point of articulation 36 fixed to the lever element 52 and the control part 32 the adjusting device 30 arranged. In other words, regardless of the rotational movement of the actuator 32 and regardless of the pivotal movement of the lever member 52 no relative movement of the articulation point 36 opposite the control part 32 and the lever element 52 instead of. Therefore lies in the area of the pivot point 36 a simple joint between the lever element 52 and control part 32 ago, which works largely free of play and ensures easy production. The lever element 52 serves to transmit the actuating force of the spring device 28 generating the inertial mass portion 20 acting restoring force when the inertial mass part 20 relative to the base part 18 around the axis of rotation 16 is twisted. As explained in more detail below, the power transmission takes place between the spring device 28 and inertial mass part 20 but not exclusively via the lever element 52.

The lever device 26 the return device 22 also has an input-side pull / push strut 54 on, the power transmission between the spring device 28 and the lever element 52 serves. So is the input side pull / push bar 54 on the one hand at a force application point 56 on the spring means 28, more specifically on the arm 50 the spring support element 38 of the spring device 28 , and on the other hand at an input-side pivot point 58 on the lever element 52 hinged. In other words, the input side push / pull strut 54 on the one hand in the axial direction 4 . 6 through the force application point 56 extending pivot axis relative to the spring support member 38 and on the other hand to a through the input-side pivot point 58 in the axial direction 4 . 6 extending pivot axis relative to the lever member 52 pivotable. Here is the force application point 56 fixed to the input side pull / push strut 54 and the spring support element 38 the spring device 28 arranged so that in the range of the force application point 56 in turn, a simple, largely backlash-free and relatively easy to manufacture joint between the spring support element 38 and the input side push / pull strut 54 is provided. Also the input side articulation point 58 is fixed to the input side push / pull strut 54 and fixed to the lever member 52 arranged so that any pivotal movements no displacement of the input-side articulation point 58 relative to the input side pull / push strut 54 or the lever member 52, thus a simple, largely backlash-free and simplified in terms of manufacturing joint between the input side pull / push strut 54 and the lever element 52 in the area of the input-side articulation point 58 is provided.

In addition, the lever means 26 the return device 22 an output side push / pull strut 60 on, the power transmission between the lever element 52 and the inertial mass part 20 serves. So is the output side push / pull strut 60 on the one hand at an output-side articulation point 62 on the lever element 52 and on the other hand at a restoring force application point 64 on the inertial mass part 20 hinged, for which purpose a in the radial direction 10 inward protruding approach 66 on the inertial mass part 20 may be provided, on which the output side pull / push strut 60 in the region of Rückstellkraftangriffspunktes 64 is articulated. In other words, the output side push / pull strut 60 on the one hand to a through the output-side pivot point 62 in the axial direction 4 . 6 extending pivot axis relative to the lever member 52 and on the other hand, by the restoring force application point 64 in the axial direction 4 . 6 extending pivot axis relative to the inertial mass portion 20 pivotable. The output side articulation point 62 is fixed to the output side pull / push strut 60 and fixed to the lever member 52 arranged so that in the region of the output-side articulation point 62 a simple and largely play-free joint between the lever element 52 and the output side pull / push strut 60 is provided. Also, the restoring force application point 64 is fixed to the output side push / pull strut 60 and fixed to the inertial mass part 20 , here's the approach 66 of the inertial mass part 20 , arranged so that also in the area of the restoring force application point 64 a relatively simple and largely play-free joint between the output side pull / push strut 60 and the inertial mass part 20 is created.

How out 1 can be seen, the input-side pivot point 58 and the output-side link point 62 spaced from each other on the lever member 52 arranged. Also are the pivot point 36 , the input-side link point 58 and the output-side link point 62 each disposed at a corner of an imaginary triangle 68, the in 1 indicated by dashed lines. Basically, the said triangle 68 have any triangular shape, in the illustrated embodiment, the triangle 68 however, as an equilateral triangle 68 educated. This means that the points mentioned, namely the point of articulation 36 , the input-side link point 58 and the output-side link point 62 the same distance b . c respectively. d to each other ( b = c = d). Alternatively, the triangle could 68 However, be designed as an isosceles triangle, in which only two of the distances b . c . d to match. In this case, it is preferable if the distance b between the input-side articulation point 58 and the point of articulation 36 the distance c between the output-side link point 62 and the point of articulation 36 equivalent.

The force application point 56 has a radial distance e to the axis of rotation 16 on while the restoring force application point 64 a radial distance f to the rotation axis 16 having. It has proved to be advantageous if - as in 1 shown - the radial distance e the radial distance f equivalent. Moreover, there is a gap G between the force application point 56 and the input-side link point 58 and a distance H between the output-side link point 62 and the restoring force application point 64 provided, with the distance G preferably the distance H corresponds, as is the case in the illustrated embodiment. The latter allows in particular a structurally identical or identical design of the two pull / push rods 54 . 60 reducing the number of parts and simplifying assembly.

The articulation point 36 is by means of the control part 32 the adjusting device 30 changing a restoring force characteristic of the inertial mass part 20 acting restoring force relative to the base part 18 movable. More precisely, the point of articulation 36 because of the about the axis of rotation 16 rotatable actuator 32 the adjusting device 30 in the circumferential direction 12 . 14 movable to change the said restoring force characteristic. In this case, the articulation point 36 along an in 1 Dashed line indicated circular path section 70 whose center is from the axis of rotation 16 is formed, relative to the base part 18 to be moved.

Hereinafter, referring to FIGS 1 to 5 different positions of the articulation point 36 relative to the base part 18 and their effect on the restoring force or the restoring force characteristic briefly explained. In the representations of the torsional vibration damper 2 in the 1 to 5 It should be noted that the inertial mass part 20 each in its initial position relative to the base part 18 is shown, in which the inertial mass part 20 not relative to the base part 18 in one of the circumferential directions 12 . 14 is twisted.

In 1 takes the point of articulation 36 a first position relative to the base part 18 a, wherein in this first position of the radial distance i the input-side articulation point 58 and a radial distance k the output side articulation point 62 to the rotation axis 16 correspond to each other.

Will the control part 32 the adjusting device 30 in the circumferential direction 14 relative to the base part 18 around the angle α ₂ starting from 1 twisted, so the articulation point moves 36 also in the circumferential direction 14 relative to the base part 18 in the in 2 shown second position. As a result, the lever device 26 moved so that the radial distance i increased while the radial distance k reduced so that i> k. Will the inertial mass part 20 due to vibrations in the circumferential direction 12 or 14 relative to the base part 18 twisted, it is on the inertial mass part 20 acting restoring force greater than that at a corresponding relative rotational movement of the inertial mass portion 20 in the first position of the articulation point 36 after 1 the case is. It can also be said that the restoring force characteristic at the second position of the articulation point 36 to 2 has a greater slope than the restoring force characteristic at the first position of the articulation point 36 to 1 ,

Will, however, the control part 32 the adjusting device 30 starting from 1 in the circumferential direction 12 relative to the base part 18 around the angle α ₃ twisted, so the articulation point moves 36 in a corresponding manner in the circumferential direction 12 relative to the base part 18 in the in 3 shown third position. Due to the associated adjustment of the lever device 26 is the radial distance i between the input-side pivot point 58 and the axis of rotation 16 now smaller than the radial distance i between the output-side link point 62 and the axis of rotation 16 , Will the inertial mass part 20 in the third position of the articulation point 36 to 3 in one of the circumferential directions 12 . 14 relative to the base part 18 twisted, it is on the inertial mass part 20 acting restoring force less than that in a corresponding relative rotational movement in the first position of the articulation point 36 to 1 the case would be. Consequently, the corresponding restoring force characteristic in the third position of the articulation point 36 to 3 a lower slope than the restoring force characteristic with the articulation point 36 in the first position 1 on.

From the foregoing description it can be seen that due to the different positions of the articulation point 36 relative to the base part 18 that on the inertial mass part 20 acting restoring forces or the restoring force curve can be particularly easily adapted to the respective operating state of the drive train. Of course, here are also other positions of the pivot point 36 along the circular path section 70 possible, whereby in this way preferably a continuous adjustment of the restoring force or restoring force characteristic is possible. Of the above items, the following are to be understood with reference to 4 and 5 two positions will be highlighted again.

In 4 is the point of articulation 36 through the control part 32 the adjusting device 30 after the second position 2 even further in the circumferential direction 14 relative to the base part 18 moved, more precisely, the control part 32 together with the articulation point 36 around the angle α ₄ in the circumferential direction 14 relative to the base part 18 twisted. In this fourth position of the articulation point 36 is one between a straight line 72 through the articulation point 36 and the output-side link point 62 and a straight line 74 through the output-side link point 62 and the restoring force application point 64 included angle β more than 165 °, preferably more than 170 °, particularly preferably 180 °. In this fourth position of the articulation point 36 is the lever device 26 thus adjusted so that the inertial mass part 20 approximately opposite the base part 18 is set, especially the restoring force characteristic of the inertial mass part 20 acting restoring force at an attempted rotation of the same relative to the base member 18 is particularly high. So the torsional vibration damper is 2 with the articulation point 36 in the fourth position 4 especially for the starting process of the drive train suitable in the torsional vibration damper 2 is integrated.

In 5 is the point of articulation 36 still beyond the third position 3 out in the circumferential direction 12 relative to the base part 18 moved, more precisely, the control part 32 around the angle α ₅ in the circumferential direction 12 together with the pivot point 36 relative to the base part 18 twisted so that the articulation point 36 in the 5 shown fifth position. In the fifth position of the articulation point 36 to 5 is one between a straight line 76 through the articulation point 36 and the input-side link point 58 and a straight line 78 through the input-side link point 58 and the force application point 56 included angle γ more than 165 °, preferably more than 170 °, particularly preferably 180 °. Consequently, the restoring force characteristic in this fifth position of the articulation point 36 a particularly low slope, which makes this setting especially suitable for idling in the drive train, in the torsional vibration damper 2 is integrated.

As already stated above, the control part 32 due to the on the control part 32 in the circumferential direction 12 . 14 acting forces during the operation of the torsional vibration damper 2 relative to the base part 18 be twisted to those in the 1 to 5 shown positions of the articulation point 36 and intermediate positions thereof. To these during the operation of the torsional vibration damper 2 on the control part 32 acting forces include one on the control part 32 self-acting inertial force, so that also the control part 32 mutatis mutandis forms a inertial mass part. Added to this is the inertial force of the inertial mass part 20 that over the lever device 26 on the pivot point 36 and thus also on the control part 32 acts. In addition, also the force or force of the spring device 28 the return device 22 over the spring support element 38 and the lever device 26 on the pivot point 36 and thus on the control part 32 Act. Will the base part 18 subjected to a torque that is subject to repetitive torque surges, this would, for example, the consequence that also the control part 32 alternately in the one circumferential direction 14 ( 2 ) and in the other circumferential direction 12 ( 3 ) relative to the base part 18 is twisted, so that the pivot point 36 between the second position 2 and the third position after 3 along the circular path section 70 moved back and forth. This would result in the return device 24 under permanent change of the restoring force characteristic of the inertial mass part 20 acting restoring force would be adjusted. To avoid this and the restoring force characteristic of the inertial mass part 20 can set and maintain effective restoring force targeted, the adjustment 30 , here its control part 32 , is locked. For this purpose, a friction device 80 provided by means of which the adjusting device 30 while preventing an adjustment of the return device 24 frictionally lockable.

The friction device 80 is at the base part 18 attached and one in the radial direction 8th outward-protruding approach 82 of the control part 32 assigned to interact with this. The substantially disc-shaped protruding approach 82 has one in the axial direction 4 facing top 84 and one in the axial direction 6 pointing bottom 86 on, of which at least one than with the friction device 80 interacting friction or contact surface can act. Consequently, the control part 32 through the friction device 80 be frictionally locked to the frictional locking of the adjustment 30 to effect.

From the foregoing description it is apparent that the locking of the adjusting device 30 frictionally and not hydraulically, as in the DE 10 2014 001 043 A1 the case is. Nonetheless, the friction device could 80 be hydraulically powered. To simplify the construction and to avoid leakage, which is usually associated with a hydraulic drive, is the friction device 80 but electrically driven. To provide the required electrical energy, has the torsional vibration damper 2 also an electric generator 88 for generating electrical energy for the friction device 80 on, with the electric generator 88 is arranged such that this electrical energy from a relative movement or relative rotation between two components of the torsional vibration damper 2 generated. So could the electric generator 88 For example, be arranged such that this electrical energy from the relative movement or rotation between the base part 18 and the inertial mass part 20 generated. In the embodiment of the 1 to 5 is the electric generator 88 however, arranged so that this electrical energy from the relative movement or rotation between the base part 18 and the spring support element 38 the spring device 28 the return device 22 generated. For this purpose, the electric generator 88 fixed to the base part 18 arranged.

They are in the axial directions 4 . 6 extending axis of rotation 90 the rotor of the electric generator, not shown 88 is about a rotational drive arrangement 92 with the spring support element 38 in rotary driving connection. In the illustrated embodiment, the rotational driving arrangement 92 essentially of a rotationally fixed with the axis of rotation 90 connected gear 94 . the toothing not shown in the rotary driving engagement with a not shown toothing on the spring support element 38 stands. Consequently, the relative movement or relative rotation between the spring support element 38 and the base part 18 to a relative movement or rotation between the rotor and the stator of the electric generator 88 so that this generates electrical energy.

The electric generator 88 is also an electrical memory for storing the electrical energy for the friction device 80 assigned, has been dispensed with the representation in the figures, wherein the electrical memory, for example in the generator 88 integrated or separately from the generator 88 can be arranged. It is advantageous to arrange the electrical memory on the same component of the torsional vibration damper 2, on which already the generator 88 itself is arranged, here the base part 18 , The same applies to the arrangement of the friction device 80 connected to the same component of the torsional vibration damper 2 should be arranged, on which also the electric generator 88 and / or the memory is arranged, here again on the base part 18 ,

Although not shown in the figures, it is still an alternative arrangement or mode of operation of the electric generator 88 pointed. So can the electric generator 88 For example, be arranged such that this electrical energy from a relative movement or relative rotation between a component of the torsional vibration damper 2 and a component of an adjacent assembly within a powertrain. However, the illustrated embodiment is preferred in that, as a result, the generator 88 together with the torsional vibration damper 2 can be easily installed as a contiguous module in a drive train without major problems with the connection to the adjacent assembly within the drive train.

The friction device 80 can occupy essentially two positions, which will be discussed in more detail below, with reference to the 6 and 7 two embodiments of the friction device 80 to be discribed. So can the friction device 80 from a locking position in which the adjusting device 30 is frictionally locked by the friction device 80 the control part 32 locked in frictional engagement, be transferred to a release position, in which the friction device 80 the control part 32 and thus also the adjusting device 30 releases, so that the return device 22 by means of the adjusting device 30 is basically adjustable, provided that the aforementioned forces act on the actuator 32 and cause its rotation relative to the base member 18.

The friction device 80 can also be transferred so alternately in the locking position and the release position that the control part 32 in the one direction of rotation relative to the base part 18 rotatable and not in the opposite direction of rotation relative to the base part 18 is rotatable to a targeted movement of the articulation point 36 along the circular path portion 70 in only one of the two opposite circumferential directions 12 and 14 to effect, as exemplified below with reference to the 1 . 3 and 5 should be explained.

Will the control part 32 during operation starting from 1 so acted upon by force that this in the circumferential direction 12 relative to the base part 18 twisting, so will the friction device 80 transferred to the release position to the movement of the pivot point 36 in the circumferential direction 12 in the in 3 To show the same position shown. Then change the on the control part 32 acting forces, so this in the opposite circumferential direction 14 relative to the base part 18 would be twisted, then the friction device 80 transferred to the locked position to such a turning back of the actuator 32 relative to the base part 18 to prevent. Then change again to the control section 32 acting forces, so this in the circumferential direction 12 relative to the base part 18 would be twisted, then the friction device 80 in turn transferred to the release position to an even further movement of the pivot point 36 in the circumferential direction 12 relative to the base part 18 to effect. Due to the alternate transfer of the friction device 80 in the locking position and the release position is the pivot point 36 thus successively along the circular path section 70 in the position after 5 moves in which the friction device 80 then longer in the locked position may remain to the achieved change in the restoring force characteristic of the inertial mass part 20 maintain effective restoring force. In an analogous way, the articulation point could 36 also successively in the opposite circumferential direction 14 relative to the base part 18 be moved to, for example, the in 4 to reach the position shown.

Hereinafter, by way of example, two embodiments of the friction device 80 from the 1 to 5 with reference to the 6 or 7 described.

6 shows a first embodiment of the friction device 80 , The friction device 80 has a substantially U-shaped support element 96 on, in the radial direction 10 inside and in the circumferential directions 12 . 14 is formed open. In the radial direction 8th outward extends the protruding approach 82 of the control part 32 between each other in the axial direction 4 . 6 opposite leg 98 . 100 of the support element 96 , On the two thighs 98 and 100 is in each case an electrically actuatable actuator 102 . 104 arranged, with the two actuators 102 . 104 in each case on the mutually facing sides of the legs 98 . 100 are arranged. At the two actuators 102 . 104 each is a friction part 106 . 108 arranged, of which the friction part 106 with the top 84 and the friction part 108 with the bottom 86 of the salient approach 82 can be brought into frictional engagement. At the friction parts 106 and 108 it may for example be friction linings, the friction parts 106 . 108 over the respective actuator 102 , 104 are driven. In the illustrated embodiment according to 6 are the two actuators 102 . 104 each formed by a piezoelectric element, which expands by electrical impingement and thus the respective friction part 106 . 108 presses against the projecting lug 82 to the actuator 32 and thus the adjusting device 30 to lock, thus the friction device 80 to convert into the aforementioned locking position.

6 shows the friction device 80 in the release position, when the actuators designed as piezoelectric elements 102 . 104 are not electrically applied. It should be noted in this context that in the embodiment according to 6 basically also on a friction part 106 . 108 could be waived to the actuators 102 . 104 directly with the protruding approach 82 to be able to frictionally engage, so that in this case the actuators 102 . 104 equally would form the friction part. It should also be noted that basically one of the two actuators 102, 104 could be dispensed with, to only one of the two sides 84 . 86 of the salient approach 82 with the friction device 80 to frictionally engage.

7 shows a second embodiment of the friction device 80 , In the second embodiment is in the protruding approach 82 also one in the preceding 1 to 5 not shown and in the circumferential direction 12 . 14 extending recess 110 is provided, through which in the axial direction 4 . 6 one in the axial direction 6 on the base part 18 fortified strut 112 of the support element 96 the friction device 80 extends. At the over the recess 110 in the axial direction 4 protruding end of the strut 112 is a support head 114 attached. In the axial direction 4 . 6 between the support head 114 and the top 84 of the salient approach 82 is also a friction part 116 arranged with the top 84 of the salient approach 82 is brought into frictional engagement or brought, wherein between the friction part 116 and the support head 114 a spring element 118 , For example, a plate spring, is arranged, by means of which the friction part 116 in the in 7 shown locking position is biased, in which the friction part 116 with the top 84 of the salient approach 82 is brought into frictional engagement. The friction member 116 also extends in the axial direction 6 through the recess 110 to there an electrically acted actuator 120 to be assigned, by means of which the friction part 116 is drivable. In the illustrated embodiment, the actuator is 120 formed by an electromagnet which can be acted upon electrically, for example a coil, wherein the friction part is produced by the electric impingement of the electromagnet 116 in the axial direction 4 against the restoring force of the spring element 118 from the in 7 shown locking position can be driven into the release position, in which the friction part 116 not with the top anymore 84 of the salient approach 82 is in frictional engagement. Here is the friction part 116 preferably along the strut 112 of the support element 96 guided.

In the first embodiment according to 6 must be the friction device 80 to reach the locking position by the actuators 102 . 104 be driven while reaching the release position - the in 6 is shown - only the electrical loading of the piezo elements must be terminated to the friction device 80 automatically return to the release position. In the second embodiment according to 7 must be the friction device 80 while being driven to reach the release position while the friction device 80 is automatically returned to the locked position due to the bias of the spring member 118 when the actuator 120 is no longer electrically charged. It should be noted at this point, however, that when using actuators 102 . 104 In the form of piezo elements also constructions can be used, in which the friction device 80 can be converted by the electrical loading of the piezo elements in the release position, while in the use of an actuator 120 In the form of an electromagnet also constructions can be realized, in which the friction device 80 can be converted by electrical loading of the electromagnet in the locked position.

LIST OF REFERENCE NUMBERS

2

A torsional vibration damper

4

axial direction

6

axial direction

8th

radial direction

10

radial direction

12

circumferentially

14

circumferentially

16

axis of rotation

18

base

20

Inertial mass part

22

Reset device

24

Reset device

26

lever means

28

spring means

30

adjustment

32

adjusting part

34

approach

36

articulation

38

Spring support member

40

spring element

42

approach

44

approach

46

first support section

48

second support section

50

poor

52

lever member

54

input side pull / push strut

56

Force application point

58

input-side coupling point

60

Output side push / pull strut

62

output-side link point

64

Restoring force application point

66

approach

68

triangle

70

Circular path section

72

Just

74

Just

76

Just

78

Just

80

friction device

82

prominent approach

84

top

86

bottom

88

electric generator

90

axis of rotation

92

Rotational drive arrangement

94

gear

96

support element

98

leg

100

leg

102

actuator

104

actuator

106

scuffing

108

scuffing

110

recess

112

strut

114

support head

116

scuffing

118

spring element

120

actuator

a

radial distance

b

distance

c

distance

d

distance

e

radial distance

f

radial distance

G

distance

H

distance

i

radial distance

k

radial distance

α ₂

angle

α ₃

angle

α ₄

angle

α ₅

angle

β

angle

γ

angle

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 102014001043 A1 [0002, 0006, 0018, 0052]

Claims (12)

A torsional vibration damper (2) having a base part (18) rotatable about an axis of rotation (16), an inertial mass part (20) associated with the base part (18), which is rotatable relative to the restoring force of a restoring device (24) relative to the base part (18), and an adjusting device (30), wherein the return device (22) by changing the restoring force characteristic of the inertial mass portion (20) acting restoring force by the adjusting device (30) is adjustable, characterized in that a friction device (80) is provided, by means of which the adjusting device (30) while preventing an adjustment of the return device (22) is frictionally lockable. Torsional vibration damper (2) after Claim 1 characterized in that the friction device (80) is electrically drivable, wherein the friction device (80) preferably has at least one electrically actuatable piezoelement or an electromagnet as actuator (102, 104; 120) and via the actuator (102, 104; 120) Particularly preferably, a friction part (106, 108, 116) which can be brought into frictional engagement with the adjusting device (30) can be driven. Torsional vibration damper (2) after one of Claims 1 or 2 , characterized in that the friction device (80) from a locking position in which the adjusting device (30) is frictionally locked, can be converted into a release position in which the return device (24) by the adjusting device (30) is adjustable, and vice versa, wherein the friction device (80) is preferably drivable to achieve the locking position or the release position and particularly preferably biased into the release position or locking position, optionally by at least one with the friction member (106, 108; 116) cooperating spring element (118). Torsional vibration damper (2) after one of Claims 2 to 3 characterized in that an electrical generator (88) for generating electrical energy for the friction device (80) comprises a relative movement or rotation between two components of the torsional vibration damper (2), preferably between the base part (18) and the return device (22), or between a component of the torsional vibration damper (2) and a component of an adjacent assembly within a drive train is provided, wherein the generator (88) is particularly preferably associated with an electrical memory for storing the electrical energy for the friction device (80). A torsional vibration damper (2) according to one of the preceding claims, characterized in that the adjusting device (30) has an actuating part (32) arranged on the base part (18) and lockable by the friction device (80). acting inertia force with adjustment of the restoring device (22) relative to the base part (18) about the rotational axis (16) is rotatable, wherein the friction device (80) preferably such alternately in the locking position and the release position can be transferred, that the actuating part (32) in a direction of rotation relative to the base part (18) rotatable and in the opposite direction of rotation is not rotatable relative to the base part (18). Torsional vibration damper (2) according to one of the preceding claims, characterized in that the return device (22) has a spring device (28) for generating a force and a pivotable about a pivot point (36) lever element (52) via which the actuating force to generate the on the inertial mass portion (20) acting restoring force on the inertial mass portion (20) is transferable, and the articulation point (36) while changing the restoring force characteristic relative to the base part (18) by the adjusting device (30), optionally the control part (32) of the adjusting device ( 30), wherein the articulation point (36) preferably in the circumferential direction (12, 14) movable or / and along a circular path portion (70) is movable, whose center is particularly preferably formed by the axis of rotation (16). Torsional vibration damper (2) after Claim 6 , characterized in that the return device (22) further comprises an input side pull / push strut (54) for transmitting power between the spring means (28) and the lever member (52) on the one hand at a Stellkraftangriffspunkt (56) on the spring means (28) and on the other hand to the lever element (52) is articulated, and / or an output-side pull / push strut (60) for transmitting power between the lever member (52) and the inertial mass portion (20) on the one hand to the lever member (52) and on the other hand to a Restoring force application point (64) is articulated to the inertial mass portion (20), preferably for at least two points or all points from the set consisting of articulation point (36), Stellkraftangriffspunkt (56) and restoring force application point (64) that the pivot point (36) fixed on the lever element (52) and the adjusting device (30), optionally the adjusting part (32) of the adjusting device (30), the adjusting force application point and the restoring force application point (64) are fixedly arranged on the output side pull / push strut (60) and the inertial mass part (20). Torsional vibration damper (2) after Claim 7 , characterized in that the input-side pull / push strut (54) on an input side Anlenkpunkt (58) and / or the output side pull / push strut (60) at an output-side pivot point (62) on the lever element (52) is articulated, wherein the input-side pivot point (58) preferably fixed to the input side pull / push strut (54 ) and the lever element (52) or / and the output-side articulation point (62) is preferably arranged fixedly on the output-side pull / push strut (60) and the lever element (52) and the input-side and output-side articulation point (58, 62) particularly preferably from each other are spaced apart and optionally with the articulation point (36) each at a corner of an imaginary triangle (68) are arranged. Torsional vibration damper (2) after one of Claims 6 to 8th , characterized in that the spring means (28) comprises a spring element (40), preferably a helical spring or helical compression spring, wherein the spring element (40) particularly preferably both generating a force in the one circumferential direction (12) and generating a force in the opposite circumferential direction (14), optionally each by compression, can be acted upon. Torsional vibration damper (2) after Claim 9 , characterized in that the spring device (28) has a relative to the base part (18) movable, optionally rotatable and / or annular, spring support member (38) on which the spring element (40) is supported or supported, wherein the spring support element (38 ), preferably generating electrical energy from the relative movement or rotation between the spring support member (38) and base member (18), cooperates with the electrical generator (88), optionally attached to the base member (18), and more preferably the spring member (40) in the one circumferential direction (12) on the spring support element (38) and a first support section (46) of the base part (18) and in the opposite circumferential direction (14) on the spring support element (38) and a second support section (48) of the base part (18 ) is supported or supported. Torsionsschwingungsdämpfer with an input side, an output side, an energy storage for torsionally elastic coupling of input and output side in the circumferential direction (12, 14) and a torsional vibration damper (2) according to one of Claims 1 to 10 , wherein the base part (18) of the torsional vibration damper (2) rotatably connected to the input or output side or the input or output side forms. Drive train for a motor vehicle with a torsional vibration damper (2) according to one of Claims 1 to 10 whose base part (18) is non-rotatably connected to a component arranged in the torque transmission path of the drive train or is itself arranged in the torque transmission path of the drive train.

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