DE102013211966A1 - Tilgerschwingungsdämpfer - Google Patents

Abstract

A Tilgerschwingungsdämpfer (100) according to an embodiment, for example, for a drive train of a motor vehicle, for damping a vibration component of a rotary movement, comprises at least two absorber masses (110) which are designed to perform in response to the rotational movement of a vibration to the vibration component thereof to dampen; at least one guide member (130) configured to movably guide the absorber masses (110) such that the absorber masses (110) are staggered along a circumferential direction perpendicular to a rotational axis (120) of rotational movement and capable of independently performing the oscillations and at least one spacer member (170) connected to and rotatably supported by at least one guide member (130) and configured to prevent two absorber masses (110) adjacent to each other circumferentially from contacting each other.

Description

Embodiments relate to a Tilgerschwingungsdämpfer, for example for a drive train of a motor vehicle, for damping a vibration component of a rotational movement. Tilgerschwingungsdämpfer can be used for example in the context of starting elements, for example in a hydrodynamic torque converter of a motor vehicle.

In many start-up elements, which are also referred to as start-up couplings, Tilgerschwingungsdämpfer be used to dampen rotational irregularities, for example, originate from an internal combustion engine. In these, due to the principle of operation, for example due to the jolting release of the energy, torque impulses occur, which are transmitted via the crankshaft to an input of such a starting element. To keep them from an output of the starting element, which in turn is often coupled to an input of a gearbox, keep away, but at least attenuate, vibration dampers can be used to dampen such and other vibration components of the rotational movement of the crankshaft.

Vibration damper here often have a vibratory system or a system which is able to temporarily store energy by energy storage elements. Depending on the specific implementation of a corresponding vibration damper in this case, for example, spring elements or other energy storage can be used.

In Tilgerschwingungsdämpfern vibration pendulum masses, which are also referred to as absorber masses, for storing energy peaks in a corresponding rotational movement are used. In contrast to many other vibration dampers, in which the rotational movement to be transmitted and thus the torque to be transmitted is coupled to an input side of the vibration damper and decoupled at an output side, absorber vibration dampers typically have only one connection with which they are coupled to the rotational movement to be damped become. In other words, in them the spring elements, ie the absorber masses, typically are not arranged in the torque flow. The connection of the Tilgerschwingungsdämpfers serves both to receive the aforementioned energy peaks as well as to deliver the cached energy.

In addition to the pure function of the Tilgerschwingungsdämpfers, namely the damping of a vibration component of a rotary motion, a variety of additional demands are made on Tilgerschwingungsdämpfer today. For example, they should be as easy to produce as possible. Likewise, they should exploit the available space as efficiently as possible. So is often only a predetermined space available for a starting element, which share the individual components of the starting element with each other. In mechanical systems for vibration damping, the size of a component often has an important influence on its function. In view of the limited space available, however, this may result in boundary conditions with regard to the most efficient possible utilization of the space available for the absorber vibration damper, for example.

Likewise, there are efforts to build with the simplest possible technical means and with the least possible effort a corresponding Tilgerschwingungsdämpfer and to be able to integrate into a corresponding starting element. Thus, there is also a need here to make a production of an absorber vibration damper as efficient and simple as possible, in which case a compromise could possibly be made with regard to the use of material, the actual manufacturing effort in terms of assembly and possibly further boundary conditions and parameters.

Due to the fact that Tilgerschwingungsdämpfern appropriate absorber masses are used, which in turn perform vibrations to dampen a vibration component of the rotational movement, it may be necessary under certain operating conditions that the absorber masses cause noise from the driver of a vehicle, in which the starting element is integrated, its passengers or other persons and passers-by, are perceived as disturbing.

Depending on the concrete implementation of such a Tilgerschwingungsdämpfers so metallic noise can be caused, for example, during the starting of the engine or even during its shutdown can occur.

During operation of a Tilgerschwingungsdämpfers occur in addition to the weight in particular also centrifugal forces acting on the absorber masses. Due to the centrifugal force, which is caused by the engine speed, if necessary, the absorber masses of such a Tilgerschwingungsdämpfers also referred to as weights are optionally pressed radially outward. The centrifugal force is dependent on the speed, the center of gravity and the mass of the absorber masses. The speed represents the size, which is slightly influenced during operation. When stopping the engine, for example, the engine speed is reduced until it finally stops (0 rpm).

During engine shutdown, an engine speed is reached in which the weight force acting on the absorber masses exceeds the magnitude of the centrifugal forces acting on the absorber masses. At this point, it may happen that the individual absorber masses collide and thus cause the aforementioned disturbing noises.

Likewise, such noises can be generated for example by rolling over which the absorber masses can be stored. If these bump into their stops their trajectories, this may also be accompanied by a disturbing noise. By the impulse of the absorber masses so a noise can be generated that the driver, the passengers of the vehicle or other persons are not used to and therefore bothersome. There is thus also the effort here to reduce the occurrence of noise during the operation of a Tilgerschwingungsdämpfers, to minimize or possibly even completely off.

In addition to starting elements, as they can be used for example in a drive train of a motor vehicle, Tilgerschwingungsdämpfer can also be used in other rotating systems in which a damping of a vibration component of the rotational movement is necessary or advisable. Examples come from the field of machine tool construction, but also other areas of mechanical engineering and vehicle construction in which corresponding rotational irregularities occur or can occur in a rotary motion.

The US 2011/0031058 A1 refers to a vibration damping device in a drive train of a vehicle. The vibration damper system includes three damper masses that dynamically move along a predetermined path in response to differences in rotational speed of a housing of the system. There is provided a spacer unit, which may comprise a plurality of spacer elements. This limits movement of the absorber masses when the absorber masses reach endpoints of the predetermined path.

Therefore, there is a need to improve a trade-off between simplifying the manufacture of a damper vibration damper, reducing noise occurring during operation, efficiently utilizing the available space and the performance of the damper. This requirement is borne by a damper vibration damper according to claim 1.

A Tilgerschwingungsdämpfer according to an embodiment, which can be used for example in a drive train of a motor vehicle for damping a vibration component of a rotary movement comprises at least two absorber masses, which are designed to perform in response to the rotational movement to a vibration in order to dampen the vibration component thereof. It also comprises at least one guide member, which is designed to guide the absorber masses such that the absorber masses are offset along a circumferential direction perpendicular to a rotational axis of the rotational movement and can execute the oscillations independently of one another. The Tilgerschwingungsdämpfer further comprises at least one connected to at least one guide member and rotatably mounted thereon spacer element, which is designed to prevent that touch two along the circumferential direction adjacent absorber masses.

Embodiments is thus based on the finding that a compromise between a simplification of the production, a reduction of the noise generated during operation, a more efficient use of the available space and the performance of the vibration is achieved by providing at least one spacer element, which with connected to at least one guide member and is rotatably supported and formed to this, in order to prevent that touch two adjacent along the circumferential direction Tilgermassen. The fact that the spacer element prevents two absorber masses adjacent to one another along the circumferential direction can thus be used to prevent or reduce noise development as a result of the impacting of the absorber masses. In addition, noise can be reduced or prevented by the impact of rolling elements, which lead the absorber masses in careers at the ends of the raceways. In addition, as will be explained below, a corresponding spacer element, implemented due to its design space-saving and mounted in a simple manner.

By rotatable support of the spacer is meant that the spacer rotates in a stationary manner about an axis which is substantially radially spaced parallel to the axis of rotation of the rotary motion of the absorber vibration damper. Adjacent are two objects, between which no further object of the same type is arranged.

The spacer element can, when a damper mass meets the spacer, make a rotational movement or be deflected. This can be made possible that the spacer element converts a part of the kinetic energy of the absorber mass into its own kinetic energy. For example, such a noise, compared with a non-rotatably mounted spacer can be reduced.

In some other embodiments, the spacer element may have an abutment contour which is designed to abut against a corresponding absorber mass application contour of at least one absorber mass. In this case, the contact contour of the spacer element is, for example, an outer contour, edge or surface of the spacer element which can come into contact with at least one of the absorber masses. By contacting, for example, a touch is meant when the damper damper is in a position which it occupies as long as the centrifugal force acting on the damper mass remains quantitatively below the oppositely directed weight force component of the damper mass. By Tilgermassenanlagekontur example, an outer contour, edge or surface of the absorber mass means that can come into contact with the spacer in an assembled state. The shape of the spacer and its plant contour is variable, since the absorber mass contour contour of the absorber masses can be adapted constructively if necessary, the investment contour of the spacer.

In some other embodiments, the contact contour of the spacer element is formed so that it can simultaneously abut flat on the Tilgermassenanlagekontur the first absorber mass and the Tilgermassenanlagekontur the second absorber mass. So it may possibly be possible that the spacer element not only prevents the meeting of two circumferentially adjacent absorber masses. In addition, it may also be possible at the same time to prevent the absorber masses, with their rolling elements, with which they are guided in raceways, from hitting the end of these raceways. So it may possibly be possible to prevent with a common spacer for two absorber masses that beat them with their rolling elements in the ends of the raceways. Furthermore, if necessary, it is thus possible to allow a movement of two adjacent absorber masses to be damped and / or braked in a similar manner or in a similar region.

In some further embodiments, the spacer element is arranged such that a point of contact between the contact contour of the spacer element and the absorber mass contour of the absorber mass lies on an edge of the absorber mass facing the axis of rotation. Thus, the spacer element can be arranged at a small radius of the guide member. It may thus possibly be possible to create a repayment vibration damper with the smallest possible moment of inertia in the same construction as other erosion damping damper.

In some embodiments, the spacer element is arranged such that a point of contact between the contact contour of the spacer element and the absorber mass contour of the absorber mass lies on an edge of the absorber mass facing away from the axis of rotation. Thus, it may possibly be possible to further simplify the production, for example the assembly of the absorber vibration damper, because the spacer element can be mounted on an outer circumference of the absorber vibration damper.

In some further embodiments, the spacer element is arranged such that a point of contact between the contact contour of the spacer element and the absorber mass contour of the absorber mass lies in a region in the radial direction, between the edge of the absorber mass facing away from the axis of rotation and the edge of the absorber mass facing the axis of rotation. It may possibly be possible that the available space of the vibration damper is used more efficiently. The spacer element does not require its own or only a smaller area in the radial direction on the guide component.

In some other embodiments, the spacer element has a bore as a bearing structure, which is designed to be rotatably connected to a correspondingly designed bearing structure, for example a rivet or a bore, in the guide component. Thus, a rotatable attachment of the spacer to the guide member can be made possible in a simple manner. Additionally or alternatively, the bearing structure may optionally be formed as a plain bearing or roller bearings. By way of example, a corresponding bearing structure on the guide component could comprise a spacer bolt or rivet, which serves to connect two guide components. The spacer bolt fulfills several functions. For example, an additional or separate component as a bearing structure on the guide component could be dispensed with.

In some other embodiments, the spacer element as a bearing structure on a bolt. The guide component can have a bore as a corresponding bearing structure. Thus, if necessary, a simple production of the bearing structure in the guide component can be made possible.

In some other embodiments, the spacer element has a bore as a bearing structure. The guide member may have as a corresponding bearing structure a rivet or bolt which is connected to the guide member. For example, a weakening of the guide component, as a bore would cause it, for example, can be avoided.

In some other embodiments, the spacer element comprises a leg that forms the contact contour. The leg may protrude from the bearing structure. Thus, it can be made possible that the spacer element can be produced as an easily manufactured component. The spacer element may comprise a second leg and / or be formed symmetrically. This makes it possible for the spacing element to be able to make contact in a simple way simultaneously with a first absorber mass and an absorber mass which is adjacent in the circumferential direction.

In some other embodiments, the spacer element is at least partially stiff. If necessary, a partially rigidly formed component can also be completely, ie rigid in all sections. A rigid component may in this case be substantially non-elastic, non-deformable and / or dimensionally stable. A rigid component could, for example, in a shock with the absorber mass, not convert a kinetic energy of the absorber mass or only in an insignificant area in deformation energy and even perform a rotational or evasive movement. A small construction of the spacer can be made possible. Further, for example, vibration of the absorber mass can not be prematurely decelerated by receiving deformation energy. The rigid spacer may be of any shape. The stiffness can be achieved by selecting a suitable material and / or by constructive measures. For example, the spacer element is designed as a solid body. A simple production of the spacer can be made possible.

In some embodiments, the spacer element is at least partially elastic. A partially elastically formed component, if necessary, also completely, that is elastically formed in all sections. An elastically formed component can essentially be reversibly deformed within a certain range and can be designed to convert a portion of the kinetic energy of the absorber mass that impinges on the spacer element into deformation energy. The elasticity of the spacer element can be achieved either by selecting an elastic material (eg elastomers, rubber, rubber) and / or by suitable design measures (for example sheet metal or bent wire parts, resilient constructions). So it can be made possible that a shock between absorber mass and spacer is damped. Further noise, which would occur in a collision between the spacer and the absorber mass, could be reduced and / or avoided.

In some other embodiments, the spacer may comprise a combination of rigid and resilient sections. As a result, if necessary, a formation of the areas with the desired properties can be achieved.

In some further embodiments, the spacer element comprises a wound material or is wound. A wound component is constructed, for example, according to the principle of a spiral spring or spring-like. The windings or windings can form the bearing structure of the spacer element. For example, if necessary, free ends of the material, that is to say the non-wound regions of the material, can form the contact contour. As a wound material, any kind of materials, for example, metal in the form of sheet or wire, may be used. Thus, a simple production of the spacer element can be achieved.

In some other embodiments, the spacer element has at least one material recess. Material recesses are recesses in the component meant that serve the weight and / or material savings. For example, through holes, pockets or blind holes can be introduced in a solid body. Even with the spring-like or wound trained components corresponding recesses may be present at not or only slightly loaded components. Thus, if necessary, it may be possible for the spacer elements to be made comparatively light and to have the lowest possible influence on the total mass of the absorber vibration damper.

In some further exemplary embodiments, the contact contour of the spacer element has at least one outwardly curved contact region viewed from a rotation axis of the spacer element. For example, the contact area can be designed to be in contact with a concavely curved portion of the absorber mass contour. As a result, it may possibly be possible that a correspondingly designed absorber mass contour contour can not slip over a highest point of the outwardly curved contact area. As a result, the absorber mass or a movement of the absorber mass can be limited.

In some further exemplary embodiments, the absorber mass contour contour has at least one convexly curved contact area. A convexly curved component essentially has an outwardly curved region, for example in a direction of the spacer element. This curved area is designed to be in contact with the contact contour of the spacer element. Components that are in contact with each other are in contact with each other, i. the spacer and the absorber mass are in contact or in contact. Thus it can be made possible that, when the contact contour and the absorber mass contour are in contact with each other, they can still slide past each other or over a certain range, this relative movement of the two components to each other, at the latest when the two highest points meet, is stopped.

In some other exemplary embodiments, the absorber mass contour has at least one concavely curved contact area. A concaved member has an inwardly curved portion, i. here away from the spacer element. This inwardly curved region is designed to be in contact with the contact contour of the spacer element. The inwardly curved region of the absorber mass system contour can accommodate an outwardly arched anal region of the spacer or provide a contact surface. For example, a movement of the absorber mass relative to the spacer can be stopped.

In some other embodiments, at least one of the absorber masses in an outer contour has a substantially U-shaped recess, which is designed to receive a leg of the spacer element with play. In other words, the Tilgermassenanlagekontur is formed to abut against a plurality of separate contact areas of the contact contour of the spacer. By way of example, a first abutment region can lie on an area of the abutment element of the spacer element facing away from the axis of rotation of the guide component and a further abutment region on an area of the spacer element facing the axis of rotation of the guide component. It can be made possible that the spacer element, viewed in the radial direction, is inserted into a middle region of the absorber masses. By receiving or guiding the spacer element in the example U-shaped recesses of the absorber masses, the movement or deflection of the spacer can be limited to a certain angular range. Thus, a coupling of the absorber masses or a movement of the absorber masses can be effected by the spacer in a certain range in a structurally simple manner within a certain frame.

As materials for the spacer element, all possible materials and material combinations can be used, for example metallic materials, such as iron, copper, aluminum and / or alloys thereof, in the form of a sheet or wire. Additionally or alternatively, as a material, a plastic, such as thermoset, thermoplastic or elastomer or material combinations thereof may be used. In some embodiments, the use of injection-moldable materials, or plastics offers. In addition or as an alternative, composites which comprise glass fibers or carbon fibers may also be used as material, for example composite materials, such as fiber-reinforced plastics. It may be possible to make the spacer from a most suitable material. In other words, depending on the required rigidity and strength criteria, the spacing element can also be designed as a plastic element. In this case, the use of a flexible material, such as elastomer and a dimensionally stable plastic, for example, thermoplastic is possible.

In some further exemplary embodiments, the spacer element, for example a surface of the spacer element or the contact contour of the spacer element, has a coating. For example, the coating is designed to possibly increase a static friction between the contact contour of the spacer and the Tilgermassenanlagekontur. Thus, it can be made possible that the spacer better stops movement of the absorber mass, the absorber mass does not slide over a surface of the spacer element. Additionally or alternatively, the coating can also be attached to the Tilgermassenanlagekontur the absorber mass. As material for the coating, any materials, for example materials that improve a static friction or spring rate, such as elastic materials or materials with a coarse surface in question.

In some embodiments, the coating is used in combination with spacers made of plastic. Thereby, the material property of the spacer made of plastic can be improved. In other words, the surface of the spacers or plastic springs can be coated for better adhesion or spring rate.

The embodiments disclosed in the foregoing description, the appended claims and the appended figures and their individual features may be individually as well as individually be of any importance and implementation in any combination for the realization of an embodiment in its various forms.

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

Show it:

1a a partial elevational view of a Tilgerschwingungsdämpfers in a driving operation;

1b a partial elevation view of in 1a shown Tilgerschwingungsdämpfers in a rest position;

1c a view of the absorber masses of Tilgerschwingungsdämpfers after 1b in a resting position;

1d a view of the absorber masses of Tilgerschwingungsdämpfers after 1a in a maximum deflected position;

1e a perspective view of the Tilgerschwingungsdämpfers after 1d with the absorber masses in a maximum deflected position;

2 a partial elevational view of a Tilgerschwingungsdämpfers according to an embodiment;

3 a partial elevational view of a Tilgerschwingungsdämpfers according to an embodiment;

4a a plan view of the absorber masses of a Tilgerschwingungsdämpfers according to an embodiment;

4b a perspective view of the absorber mass according to 4a ;

4c a plan view of a spacer according to the embodiment of the 4a ;

4d a side view of the spacer according to 4c ;

4e a side view of the spacer according to 4c ;

4f a perspective view of the spacer according to 4c ;

5a a partial elevational view of a Tilgerschwingungsdämpfers according to an embodiment;

5b a cross-sectional view through the Tilgerschwingungsdämpfer according to 5a ;

5c an enlarged section of the cross-sectional view of the Tilgerschwingungsdämpfers according to 5b ;

5d a perspective view of the Tilgerschwingungsdämpfers according to 4c ;

6a a plan view of a spacer element according to an embodiment;

6b a side view of the spacer according to 6a ;

7a a plan view of a spacer element according to an embodiment;

7b a side view of the spacer according to 7a ;

8a a plan view of a spacer element according to an embodiment;

8b a side view of the spacer according to 8a ;

9a a plan view of a spacer element according to an embodiment;

9b a side view of the spacer according to 9a ;

10a a plan view of a spacer element according to an embodiment;

10b a side view of the spacer according to 10a ;

10c a side view of the spacer according to 10a ;

11a a plan view of a spacer element according to an embodiment;

11b a side view of the spacer according to 11a ;

11c a side view of the spacer according to 11a ;

12a a plan view of a spacer element according to an embodiment;

12b a side view of the spacer according to 12a ;

12c a side view of the spacer according to 12a ;

13a a plan view of a spacer element according to an embodiment;

13b a side view of the spacer according to 13a ;

13c a side view of the spacer according to 13a ;

14a a plan view of a spacer element according to an embodiment;

14b a side view of the spacer according to 14a ;

14c a side view of the spacer according to 14a ;

15a a plan view of a spacer element according to an embodiment;

15b a side view of the spacer according to 15a ;

15c a side view of the spacer according to 15a ;

16a a top view of a spacer ;.

16b a side view of the spacer according to 16a ;.

16c a side view of the spacer according to 16a ;.

16d a detail of a plan view of a Tilgerschwingungsdämpfers with a spacer according to 16a ,

In the following description of the accompanying drawings, like reference characters designate like or similar components. Further, summary reference numbers are used for components and objects that occur multiple times in one embodiment or in one representation, but are described together in terms of one or more features. Components or objects which are described by the same or in a combination of reference symbols can be identical in terms of individual, several or all features, for example their dimensions, but possibly also different, unless the description makes explicit or implicit reference to the description.

As already briefly explained above, vibration dampers and here, for example, Tilgerschwingungsdämpfer used in a variety of technical fields, which include, for example, drive trains of a motor vehicle, but also other technical areas. Vibration dampers and Tilgerschwingungsdämpfer can be used, for example, when a rotational movement rotational nonuniformities, as they can occur, for example, principle of internal combustion engines. In internal combustion engines that follow, for example, the Otto principle or the diesel principle, occur abruptly force unfolding and thus jerky torque peaks, which can be reflected both in the generated torque, as well as in the current speed of such an engine.

If, for example, in a drive train between such an internal combustion engine and a transmission, a starting element is switched, which serves to enable the engine to continue running even when the vehicle is at a standstill, it may already be in the interest of the manufacturer of the vehicle due to considerations with regard to ride comfort The vehicle concerned and its customers are to remove the rotational irregularities from the rotational movement of the crankshaft of the engine before reaching the input shaft of the transmission, but at least reduce or dampen. For this purpose, vibration dampers can be used in the context of appropriate starting elements, which are typically based on that energy peaks of the rotational movement, so for example torque peaks or short-term speed peaks are stored in energy storage before they are in turn passed to the input shaft of the transmission. As starting elements in this case both hydrodynamic starting elements, so for example a torque converter also referred to as a converter, but also based on a frictional connection starting elements and combinations of both concepts can be used.

Vibration damper often have an input component and an output component, between which the energy storage elements are used and via which the transmission of the rotational movement takes place. In Tilgerschwingungsdämpfern, which are also referred to as "absorber", the torque flow does not take place via the corresponding energy storage elements. Rather, Tilgerschwingungsdämpfer often have a connection or a connection component, which are coupled to the energy storage elements absorber masses are mounted or guided by one or more guide members so that at a deflection, ie a vibration of the respective absorber masses a center of gravity is moved radially , As a result, the absorber masses in the force field generated by the rotational movement, which among other things, the centrifugal force of the rotational movement includes, gaining potential energy. Corresponding Tilgerschwingungsdämpfer are also referred to as speed-adaptive Tilger.

Energy that has flowed into the absorber masses for a short time, can accordingly be deducted from this again and coupled via the connection component in the rotational movement at a corresponding time again. Therefore, a Tilgerschwingungsdämpfer can attenuate vibration components, possibly even completely eliminate by temporarily caving the vibration energy occurring and couples back into the rotational movement accordingly.

The absorber masses are in this case often made of a metallic material, that is, for example, a metal, an alloy or a similar metallic material, which may include, for example, non-metallic components. However, depending on the operating state of such a Tilgerschwingungsdämpfers metallic noise may possibly arise, which may be bothersome by the driver of such a motor vehicle or the passengers of the motor vehicle, but also by passers-by or other observers. Corresponding metallic noise can occur, for example, in normal vehicle operation, but also in crawl operation of the vehicle. Likewise, you can in the context of the shutdown of the internal combustion engine, which is also referred to as a motor, occur. This is especially relevant for engine start-stop (MSA) automatics, such as those used to save energy.

By switching off the engine in the vehicle, the speed and thus the centrifugal force of the absorber masses of the designated as speed-adaptive absorber Tilgerschwingungsdämpfers is reduced. From a certain speed then the weight forces can take an increased influence on the position of the absorber masses in Tilgerschwingungsdämpfer so that they may possibly collide with each other. This effect can cause the unwanted noise described above.

The perceptibility of these sounds can be increased, for example, by the fact that the transmission inertia can still run after a few seconds even after stopping the engine. By running after the damper assembly, which includes the Tilgerschwingungsdämpfer, the absorber masses of Tilgerschwingungsdämpfers can beat each other or in their respective attacks.

1a shows a plan view of a Tilgerschwingungsdämpfer 100 according to an embodiment, the four absorber masses 110-1 . 110-2 . 110-3 and 110-4 , each using two roles 160 or rolling elements on a first guide member 130-1 and one in 1a only partially shown second guide member 130-2 stored or guided so that the absorber masses 110 can make a vibration to a vibration component of one in the Tilgerschwingungsdämpfer 100 introduced rotary motion about the axis of rotation 120 of the absorber vibration damper 100 to dampen. The absorber masses 110 For example, they may be solid or formed as a laminated core. The two guiding components 130 are over four spacer bolts, in the present embodiment, the same time the bearing structure 131-1 to 131-4 of the guide component 130 train, interconnected.

In further embodiments, not shown, the Tilgerschwingungsdämpfer may have a different number of guide components, for example, only one guide member, three or four guide members, which can be arranged between the individual sheets from which the absorber mass can be constructed. Further, the guide members may be any of a variety of fasteners, for example, screws, connectors, for example, with a different number of fasteners, for example, one, two, three, five, six, or with a number of fasteners, with the number Tilgermassen corresponds, be connected.

The guide component 130-1 moreover, for example, along the axis of rotation 120 one in the torsional vibration damper 100 Introducing rotary motion fixed flange 180 on. The flange 180 is here as a flange structure of the first guide member 130-1 executed and has several holes 181 on, with whose help the flange 180 is mechanically drehverbindbar on another assembly.

In further embodiments, not shown, a flange or a connection structure for mechanical connection with another module may have all sorts of other shapes, so for example offset or stepped executed, comprise a different number of holes and / or have other connection means.

Both the first guide component 130-1 as well as the second guide component 130-2 have Führungsbauteillaufbahnen 140 on, on or over which the roles 160 roll. The guide component tracks 140 of the first guide component 130-1 Correspond to this with the corresponding Führungsbauteillaufbahnen 140 of the second guide member 130-2 , For example, in an external steering of the absorber mass 110 a shift of the center of gravity along a radial direction, the perpendicular to the axis of rotation 120 stands to allow to have the absorber masses 110 Tiger grounding component raceways 150 which are essentially to the leadership component raceways 140 the guide components 130 correspond.

1a shows a situation in a normal operation or driving operation of a vehicle, above a certain limit speed (no slow creep). The centrifugal force F quantitatively exceeds the opposite weight component G of the absorber mass 110 , The absorber masses 110 or flyweights work synchronously. All absorber masses 110 are in a radially maximum outer position, but are in a zero position and are not deflected ie the rollers 160 are in a middle position of the Führungsbauteillaufbahnen 140 and the absorber mass leadership careers 150 , From this situation, it could lead to an undesirable noise by striking the absorber masses 110 or more precisely, the roles 160 at the ends of the Führungsbauteillaufbahn 140 or the ends of the absorber mass raceways 150 or by the juxtaposition of adjacent absorber masses, such as the absorber masses 110-1 and 110-2 come. This may for example be the case when the absorber masses 110 be excited or tend to a greater amplitude of vibration due to the vibration occurring, as the constructively defined maximum swing angle permits.

The absorber vibration damper 100 includes four spacers 170 , The spacers 170 are made as shaped springs, for example, from bent sheet metal. In 1a are two spacers 170-1 and 170-2 recognizable. The two other spacers are each in the area of the bearing structures 131-3 and 131-4 arranged but of the guide member 130-2 covered. Each of the spacers 170 is with a storage structure 190 at one of the storage structures 131 of the guide component 130 rotatably mounted.

In other words, the spacer elements can be plugged onto a rivet or rivets or spacers or inserted into bores of the guide components or the web plates. For this purpose, the spacer elements may have a bolt. By way of a clearance fit between a bearing structure of the spacer element and a bearing structure of the guide component, the at least one spacer element can be freely movable relative to the guide component. The design of the spacer element, which is also called a form spring, a guide pin or a retaining lug as a bearing structure instead of a bore as a bearing structure is conceivable. Alternatively, the spacer can be plugged onto a shaft. In this case, the spacer can be used on a different attachment structure than the rivet (spacer, spacer bolts) and can thus be freely placed in the web plates, if necessary. If necessary, the track plates can be provided with corresponding holes.

As in 1a , based on the bearing structures 131-1 . 131-2 . 131-3 and 131-4 recognizable, are the four spacers 170 arranged on a common circumference.

The spacer element 170 has an investment contour 200 on. The absorber masses 110 each have a corresponding Tilgermassenanlagekontur 220 on. Here is the investment contour 200 of the spacer element 110 the area of a circumferential or outer contour of the spacer element 170 which is substantially parallel to the axis of rotation 120 runs and is suitable with the absorber mass 110 or the Tilgermassenanlagekontur 220 to contact, or a movement of the absorber mass 110 to stop. The absorber mass contour 220 is an area of the absorber mass 110 that with the spacer element 170 in contact or contact.

1b shows a situation in another operating state of the Tilgerschwingungsdämpfers 100 depending on the speed of rotation. The illustrated situation may occur in a so-called slow creep when a transmission input shaft rotates at a lower speed than the engine speed. The weight G of the absorber mass 100 In this condition, they are significantly higher than the opposite components of centrifugal force F. Another operating condition similar to that in 1b situation shown is the stopping of the engine when the transmission input shaft lags behind a few seconds. At a certain point in time, the weight G exceeds the absorber mass 100 the opposite component of the centrifugal force F. The absorber masses fall in both operating states 110 uncontrolled in the direction of the weight G down.

1c shows the same operating state as 1b , For better clarity, the guide components 130 in 1c hidden. The absorber mass contour 220 includes, as for the absorber mass 110-3 described by way of example, four concave areas 221-1 to 221-4 These are curved inwards, towards an absorber mass center M. Two adjacent concaved areas are each over a high point 222 separated, ie the adjacent concave arched areas 221-1 and 221-2 are over the high point 222-1 separated. The high point 222-2 separates the neighboring areas 221-2 and 221-3 , The high point 222-3 separates the areas 221-3 and 221-4 , The two middle concave inward domed areas 221-2 and 221-3 are essentially the same. The two outer concave concave areas 221-1 and 221-4 are also essentially the same. Here is a distance between the high points 222-1 and 222-2 , which is the first middle concave inward arched area 221-2 enclose, greater than a distance between the high point 221-1 and an outer point 222-5 which has the outer concave inward arched area 221-2 ie includes the two middle concave inward domed areas 221-2 and 221-3 are each comparatively larger, or have a greater extent than the two outer concave inwardly curved areas 221-1 and 221-4 ,

In some embodiments, not shown, the absorber mass contour contour may have any suitable shape, for example any curve, a straight line and / or a step shape. The spacer element 170 includes in its investment contour 200 an investment area 210 pointing in one direction to the absorber mass 110 out, arched outwards.

As in 1c recognizable, fall the absorber masses 110 in the described states in the direction of the weight G. In this case, the absorber mass falls 110-2 with their absorber mass contour 220 in an investment area 230-1 on the spacer element 170-4 and in an investment area 230-2 on the spacer element 170-4 , The investment area 230-1 lies in the fourth concave concave area 221-4 at the Tilgermassenanlagekontur 220 and touches the spacer 170-1 in an investment area 210 the plant contour 200 in the area of a right thigh 205 , In other words, the spacers 170 as damper elements in a speed-adaptive absorber or Tilgerschwingungsdämpfer 100 to prevent metallic noise by striking the absorber masses 110 , which are also called flyweights Flyweights at a tail or the raceways 140 or 150 and / or serve each other.

The investment area 230-2 lies at the Tilgermassenanlagekontur 220 in the second concave area 221-2 near the high point 222-1 and touches the investment contour 200 of the spacer element 170-4 in an investment area on a leg 206 , The investment area 210 in the plant contour 200 of the spacer element 170-4 lies closer to a rotation axis in this embodiment 171 of the spacer element 170-4 , as with the spacer element 170-1 , Through the two investment areas 230-1 and 230-2 the absorber mass 110-2 can prevent the absorber mass 110-2 with their rolling elements 160 against the ends 151 the absorber mass leadership careers 150 suggests. Furthermore, it prevents the absorber mass 110-2 with an edge 111 against an edge 112 the absorber mass 110-3 suggests.

The absorber mass 110-1 relies on the absorber mass 110-2 at the spacers 170-1 and 170-2 from.

Because the absorber masses 110-1 and 110-2 both fall in the same direction of weight G, the spacers become 170-1 . 170-2 and 170-4 the in 1c shown situation not or only slightly deflected.

The absorber mass 110-3 lies with the concave inward curved area 221-4 the absorber mass contour 220 at the plant contour 200 in the area of the right thigh 205 of the spacer element 170-4 at. An investment area 230-3 the absorber mass 110-3 is further away from a rotation axis 171 of the spacer element 170-4 as the investment area 230-2 between the absorber mass 110-2 and the right thigh 206 of the spacer element 170-4 ,

Furthermore, the absorber mass is supported 110-3 with the absorber mass contour 220 at the plant contour 200 of the spacer element 170-3 in the area of the right thigh 206 in an investment area 230-4 from. The investment area 230-4 lies at the Tilgermassenanlagekontur 220 at the high point 222-1 , The investment area 210 the plant contour 200 of the spacer element 170-3 is compared to the abutment areas of the spacers 170-1 and 170-4 at a closer distance to the axis of rotation 171 of the spacer element 170-3 ,

The absorber mass 110-4 relies on the absorber mass 110-3 at the spacers 170-3 and 170-2 from.

In other embodiments, not shown, depending on the contact contour of the absorber mass and / or the spacer and other investment areas may arise.

1d shows the absorber vibration damper 100 in a maximally deflected situation. This situation may occur in an operating condition when the damper vibration damper 100 when driving (ie over a certain limit speed) is operated and the absorber masses 110 due to vibrations occurring in relation to the guide components 130 be deflected. Also in 1d is the second guide component 130-2 hidden for the sake of clarity.

In the in 1d shown deflected state, the investment areas or points of contact between the absorber mass system contour change 220 the absorber mass 110 and the investment contour 200 the spacers 170 , Since at the in 1d illustrated situation all absorber masses 110 behave the same way, the investment areas are exemplary for the absorber mass 110-3 described.

The absorber mass 110-3 relies on a first location, a first investment area 230-5 with the concave inward curved area 221-4 on the contact contour of the spacer 170-4 in the area of the right thigh 205 on the spacer element 170-4 from. At a second place, one investment areas 230-6 supports the absorber mass 110-3 on with their Tilgermassenanlagekontur 220 at the plant contour 200 of the spacer element 170-3 in the area of the left thigh 206 from. The investment area 230-6 lies at the Tilgermassenanlagekontur 220 at the second concave area 221-2 and in the area of the first high point 222-1 , Depending on the degree of deflection and / or load of the Tilgerschwingungsdämpfers also other investment areas may arise.

1e shows a perspective view of 1d , As in 1e recognizable, the storage structure protrudes 131 over the spacer element 170 out, so possibly the second in 1e not shown guide component 130-2 can be attached to these and the bearing structure 131 also as a spacer bolt as a bearing structure 190 serves. In other words, the spacer element 170 rotatable on the spacer bolt, which is the two guide components 130 interconnected, stored.

In other embodiments, not shown, the Tilgerschwingungsdämpfer a different number of absorber mass, for example, one, two, three, five, six, seven, ... have. The Tilgerschwingungsdämpfer may also have a different number of spacers. In some embodiments, the number of spacer elements corresponds to the number of absorber masses, so that a spacer element is arranged between two absorber masses. In some other embodiments, fewer or more spacers are provided as absorber masses.

2 shows a plan view of another embodiment of a Tilgerschwingungsdämpfers 300 with four absorber masses 310 , Essential components are analogous to the previously described Fig. And the, Tilgerschwingungsdämpfer 100 educated. In the following, only the differences will be discussed. For clarity, the second guide component 130-2 partially shown excluded. The absorber masses 310 differ from the absorber masses 110 through their absorber mass plant contour 320 , The absorber mass contour 320 includes on one side edge 111 the absorber mass 310-1 a U-shaped recess. The U-shaped recess of the Tilgermassenanlagekontur 320 thus forms both an investment area for one of the axis of rotation 120 facing side 207 of the spacer element 310 , for example, the left thigh 206 as well as an abutment area for one of the rotation axis 120 opposite side 208 of the spacer element 310 , for example, the thigh 206 , Analogously includes the absorber mass 310 at the edge 112 also a U-shaped training.

The spacers 170 in the embodiment of 2 are analogous to the spacer elements 170 of the 1 educated. Difference to the previous embodiment is a radius on which the spacers 310 or the storage structure 131 on the guide component 130 arranged, or are attached. The spacers 170 are substantially at a radius near an outer circumference of the guide member 130 arranged.

3 shows a further embodiment of a Tilgerschwingungsdämpfers 400 with four absorber masses 110 , The absorber vibration damper 400 essentially corresponds to the absorber vibration damper 100 , Difference is the arrangement of the spacer elements 170 , The spacers 170 are arranged so that they each have the absorber masses 110 in the investment area 230 at the Tilgermassenanlagekontur 220 on an edge 410 the absorber mass 110 Touch the axis of rotation 120 turned away from the rotational movement. That is, the spacers 170 are on a larger radius than the absorber masses 110 arranged. Further, the spacers 170 in the embodiment of 3 arranged so that their investment area 210 to the axis of rotation 120 points.

The investment area 230 becomes at the Tilgermassenanlagekontur 220 between a side edge 111 and the axis of rotation 120 opposite edge 410 educated. Here shows the absorber mass contour 220 a convex curved area. The convex arched area as an investment area 230 one touches in the direction of the axis of rotation 120 curved outer contour of the right leg of the spacer 205 ,

In other words, the spacers, as in the 1a . 2 and 3 shown, placed above, below and / or between the absorber masses. The spacers between the absorber masses act as energy storage in the radial direction, ie the spacers are compressed according to their position. A use of the spacer element directly between the absorber masses is possible with appropriate adaptation of the geometry of the absorber masses.

The 4a shows a further embodiment of a Tilgerschwingungsdämpfers 500 with four absorber masses 510 , The absorber vibration damper 500 is essentially analogous to Tilgerschwingungsdämpfer 100 educated. However, the absorber masses differ 510 in your Tilgermassenanlagekontur 520 from the absorber mass contour 220 the absorber masses 110 , The absorber mass contour 520 has analogous to Tilgermassenanlagekontur 220 four concave, concave areas 530-1 to 530-4 on, by high points 531-1 to 531-3 are separated from each other. However, a distance in the radial direction between the high points 531 and the concave inward curved areas 530 , or their lowest point lower than in the absorber masses 110 , or the Tilgermassenanlagekontur 220 educated.

The absorber vibration damper 500 includes four spacers 540 , These are analogous to the spacer elements 170 on a storage structure 131 rotatably mounted. 4b shows a perspective view of the Tilgerschwingungsdämpfers 500 , For the sake of clarity is also the second guide member 130-2 not shown.

The 4c to 4f show enlarged representations of the spacer 540 , The spacer element 540 points as a storage structure 190 a hole on. The plant contour 200 of the spacer element 540 is analogous to the Tilgermassenanlagekontur 520 , as in 4a shown, shallower than the spacer element 170 educated. The investment areas 210 , each on a left leg 205 and 206 in the installation situation on one of the rotation axis 171 are also slightly outwardly arched, being meant to bulge outwards, in the direction in which they are in an assembled state, as in 4a shown the absorber mass 510 is arranged.

The spacer element 540 has a lower area 560 on that in a mounting situation of the rotation axis 120 is facing. The area 560 is concave, so the area 560 has a radius substantially corresponding to a radius at which the spacer element 540 with its lower area 560 on the guide component 130 is arranged.

The spacer element 540 has a substantially triangular shape, differing from the guide structure 190 one leg each 205 and a thigh 206 extends away. The same length thighs 205 and 206 meet at an upper tip 570 that is the lower area 560 lies opposite, together. The top tip 570 is also convex outwards. From the top tip 570 considered, towards a right corner 212 of the spacer element, the contact contour first has an outwardly curved region, to which an inwardly curved region with a low point 580 followed. From the low point 580 the system contour curves 200 to the lower tip 212 back out. The left thigh 206 or the contact contour in the area of the left thigh 206 is analogous.

Furthermore, the spacer element comprises 540 two recesses 550 , These have a substantially triangular shape and are each substantially similar to a shape of the legs 205 and 206 educated. The recesses 550 penetrate the material of the spacer element 540 Completely. In further embodiments, not shown, the recesses 550 also be designed as blind holes. Thus, in embodiments, also not shown, the recesses may have all possible shapes and patterns, such as holes, through holes, blind holes, pockets in triangular, rectangular and / or polygonal shape. The recesses 550 can allow the spacer element 540 can be made with the same size with a lower Wipe and a lower material usage.

The 5a to 5d show a damper vibration damper 600 with four absorber masses 510 according to an embodiment. The absorber vibration damper 600 is essentially analogous to the Tilgerschwingungsdämpfer 500 educated. The main difference is the spacer element 650 , The spacer element 650 is essentially analogous to the spacer element 540 educated. The four spacers 650 are arranged on the radius R. An investment contour 200 of the spacer element 650 essentially corresponds to the contact contour 200 of the spacer element 540 , Unlike the spacer element 540 is the spacer element 650 made of solid material or formed as a solid body. The spacer element 650 has no pockets or recesses. The spacer element 650 may be formed of rigid material or elastic material.

5b shows for better understanding a sectional view of the Tilgerschwingungsdämpfers 600 , 5c shows an enlarged view of the rotatable mounting over the bearing structure 131 , which are at the same time the two guiding components 130 combines. In 5d is the absorber vibration damper 600 in a perspective view with two guide components 130 shown.

The 6 to 16 show different embodiments of spacers or a shaped spring made of spring steel or general steel. Made of sheet steel, the spacer can be manufactured in various variations. The design variations are limited only by the production cost. These can analogously to the spacer elements already described in one of the Tilgerschwingungsdämpfer after the previously described embodiments be used. In other words, movement of the absorber masses can be predetermined by the geometry of the webs both in the absorber masses of the raceways and in the guide components or web plates. In vehicle crawl operation or when stopping the engine, it may happen that the centrifugal force is insufficient to keep the absorber masses in their desired position. Depending on the angular position of the absorber or Tilgerschwingungsdämpfers they can either fall freely or slide along the tracks or tracks down. The spacer elements can prevent a desired movement absorber masses in the raceways or tracks by supporting these against each other. Thus, the falling down of the absorber masses in their tail ends or raceway ends is prevented and prevents the development of noise, by impacting components or the clacking noise.

The 6a and 6b show different views of a spacer 660 according to an embodiment. The spacer element 660 is made of a wound material, for example of a metal, for example a sheet metal, for example a spring plate, as well as in 6b recognizable. The windings or windings form a bearing structure 190 for pivotal connection with the bearing structure 131 of the guide component 130 serves. Free ends of the material coming from the winding or bearing structure 190 protrude, each forming a right thigh 205 and a left thigh 206 out. The plant contour 200 of the spacer element 660 is essentially concave arched outward. The free end, the thigh 205 forms, extends from a crossing point 214 the windings, or the bearing structure of the two free ends to a right-hand tip 212 of the spacer element 660 , Between the crossing point 214 and the right top 212 is an outwardly arched, ie from the axis of rotation 171 of the spacer element 660 wayward investment area 661 educated. At the right top 212 the material is bent or kinked, back in the direction of the axis of rotation 171 but only so far that between one end 662 of the material and the bearing structure 190 makes a gap exists. As a result, if necessary, an elastic property of the spacer element 660 be achieved.

To save weight and / or to avoid sharp edges, the spacer element has 660 in the area of the right tip 212 a circular segment-shaped material recess 663 on. The left thigh 206 of the spacer element 660 is analogous. In further embodiments, not shown, the material recess may have any shape or pattern, for example: triangle, rectangle, polygon, circular and / or oval.

The 7a and 7b show a spacer 670 according to an embodiment. The spacer element 670 is analogous to the spacer element 660 shown as a wound component, as well as in the side view in 7b of the spacer element 770 is recognizable. The storage structure 190 is formed over the winding. From the winding 190 each one right leg protrudes 671 and an opposite left thigh 672 from. The right thigh 671 ends in a right top 675 , The thigh 672 ends in a left tip 676 , The thigh 671 protrudes from the winding 190 in the form of a tangent at a point of contact 677 and extends to a lower low point 679 , The lower low point is approximately at a height of the outer circumference of the bearing structure 190 , At the low point, a slope of the leg changes 671 , The thigh ends roughly with its tip 675 at a height of the point of contact 677 at the thigh 671 of warehouse structure 190 or winding protrudes. The left thigh 672 is symmetrical to the right thigh 671 educated.

The 8a and 8b show under a spacer 680 according to an embodiment. The spacer element 680 points as a storage structure 190 a C-shaped clamp on. An integrally formed component, the right leg 681 and a left thigh 682 has, is with its mid-range 683 on an outer periphery of the bearing structure 190 attached or connected, leaving an opening 684 the bearing structure 190 the connection point 683 opposite. At each of the thighs 681 and 682 has the spacer element 680 , as in 8b recognizable, recesses 685 on. The recesses 685 are each formed substantially rectangular and arranged so that the contact contour in the region of the right leg 681 essentially H-shaped looks.

The 9a and 9b show a further embodiment of a spacer element 690 , The storage structure 190 is analogous to the bearing structure 190 at the spacer element 680 designed as a C-shaped bracket. From the warehouse structure 190 protrude thighs 672 and 671 the thighs in their shape 672 and 671 of the spacer element 670 of the 7a and 7b correspond.

The 10a . 10b and 10c show an enlarged view of the spacer 170 of the 1 . 2 and 3 , Here it can be seen that the spacer element is formed as a one-piece bent sheet metal part. The storage structure 190 is formed by an almost closed circular perimeter. At one point, where the bearing structure is open, one leg protrudes in each case 205 and 206 from. Everyone who leg 205 and 206 is at an outer tip 112 respectively. 113 bent back towards the bearing structure.

The 11a to 11c show a spacer 690 according to an embodiment. The spacer element 690 is manufactured as a one-piece bent wire part. Similar to the spacer 170 protrudes from the storage structure 190 a right thigh 691 from. This changes in a turning point 692 at one end of the circular bend of the bearing structures 190 its slope and is bent by about 180 ° in a radius. In a second turning point 693 changes again a slope of the bend and the leg has one in the direction of the central axis 171 arched shape. An end 694 of the thigh 691 is essentially at an altitude of the second inflection point 693 , A left thigh 695 is symmetrical to the leg 691 educated.

The 12 to 15 Show spacer elements, which are made of plastic or plastic molded spring. In other embodiments, not shown, the spacer elements of 12 to 15 also be made of any other suitable materials.

The 12a . 12b and 12c show a spacer 700 according to an embodiment. The spacer is made as a solid body and has the shape of a circle segment. In a central area of the circle segment is used as a warehouse structure 190 introduced a bore. The plant contour 200 at the spacer 700 includes a surface of the circle segment. By selecting a suitable radius of the circle segment, the investment contour 200 be formed steeper or shallower.

The 13a . 13b and 13c show a spacer 710 according to an embodiment. In its form corresponds to the spacer element 710 essentially the spacer element 690 , wherein the bearing structure 190 not designed as a C-shaped bracket, but closed.

The 14a . 14b and 14c show a spacer 720 according to an embodiment. The spacer element 720 has a bore as bearing structure 190 on.

From a middle area where the bearing structure 190 is introduced, protrude a right thigh 721 and a left thigh 722 from. The right thigh 721 and the left thigh 722 have the shape of a circular arc. A middle area 723 into which the hole as a bearing structure 190 is substantially centrally located on an inner circumference of the two legs 721 and 722 or the circular arc arranged.

The 15a . 15b and 15c show a spacer 730 according to an embodiment. The spacer element 730 is essentially analogous to the spacer element 720 educated. The spacer element 730 is different from the spacer element 720 only in the form of the bearing structure 190 , At the spacer element 730 is the storage structure 190 no hole, which is introduced into the spacer element, but a bolt or rivet, which is the spacer element 730 protrudes.

16a to 16d show a spacer 800 , The spacer element 800 has three legs 810 . 820 and 830 on. The thigh 810 to 830 are in a central area 840 connected with each other. The spacer element 800 includes as a fastening structure 190 a feather. The spring may be in a corresponding attachment structure or recess of the guide member 130 , as in 16d shown used. As already described, prevents the spacer element 800 the collision of the absorber masses. In other words, the bearing structure 190 of the spacer element as a retaining lug or spring for the fixation and / or guidance in the web plates, or guide components be executed rectangular or rounded. The spacer element 800 or spring element does not act as an energy storage between the two circumferentially arranged absorber masses 110 , The absorber masses 110 lie down with the absorber mass contour 220 or its underside on the spacer element 800 from.

The embodiments disclosed in the foregoing description, the appended claims and the appended figures, and their individual features, may be relevant and implemented both individually and in any combination for the realization of an embodiment in its various forms.

LIST OF REFERENCE NUMBERS

100

repayment vibration

110

repayment mass

111

edge

120

Rotary axis (absorber vibration damper)

130

guiding member

131

bearing structure

140

Guiding member career

150

Tilgermassenführungslaufbahn

151

Career end

160

rolling elements

170

spacer

171

Rotation axis (distance element)

180

flange

181

drilling

190

bearing structure

200

contact contour

205

right thigh

206

left thigh

207

the axis of rotation facing side

208

the axis of rotation averted side

210

plant area

212

right top

213

left top

214

intersection

220

Tilgermassenanlagekontur

221

concave arched area

222

high point

230

plant area

300

repayment vibration

310

absorber mass

320

Tilgermassenanlagekontur

400

repayment vibration

410

opposite edge

500

repayment vibration

510

absorber mass

520

Tilgermassenanlagekontur

530

concave arched area

531

high point

540

spacer

550

bag

560

lower area

570

upper tip

580

deepest area

600

repayment vibration

650

spacer

660

spacer

661

plant area

662

The End

663

material recess

670

spacer

671

right thigh

672

left thigh

675

right top

676

left top

677

point of contact

679

low

680

spacer

681

right thigh

682

left thigh

683

connecting structure

684

opening

685

recess

680

spacer

691

right thigh

692

turning point

693

second turning point

694

The End

695

left thigh

700

spacer

710

spacer

720

spacer

721

right thigh

722

left thigh

723

middle area

730

spacer

800

spacer

810

leg

820

leg

830

leg

840

Central area

900

Tilgerschwingungsdämpfer

F

centrifugal

G

weight force

A

neckline

R

radius

M

Tilgermassenmitte

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

• US 20110031058 A1 [0013]

Claims (15)

Tailstock vibration damper ( 100 ), for example, for a drive train of a motor vehicle, for damping a vibration component of a rotational movement, having the following features: at least two absorber masses ( 110 ) configured to vibrate in response to the rotational movement to dampen the vibration component thereof; at least one guide component ( 130 ), which is adapted to the absorber masses ( 110 ) such that the absorber masses ( 110 ) along an axis of rotation ( 120 ) are disposed offset from the rotational movement of the vertical circumferential direction and can perform the vibrations independently; at least one with at least one guide component ( 130 ) connected and rotatably mounted thereto spacer ( 170 ) formed to prevent two absorber masses adjacent to each other along the circumferential direction (FIG. 110 ) touch. Tune vibration damper according to claim 1, wherein the spacer element ( 170 ) an investment contour ( 200 ), which is designed to be connected to a corresponding absorber mass system contour ( 220 ) at least one absorber mass ( 110 ). Tilgerschwingungsdämpfer according to any one of the preceding claims, wherein the contact contour ( 200 ) of the spacer element ( 170 ) is designed so that these at the same time at the Tilgermassenanlagekontur ( 220 ) of the first absorber mass ( 110 ) and the absorber mass contour ( 220 ) of the absorber mass following in the circumferential direction ( 110 ) can lie flat. Tune vibration damper according to one of the preceding claims, wherein the spacer element ( 170 ) is arranged so that a contact area between the contact contour ( 200 ) of the spacer element ( 170 ) and the absorber mass contour ( 220 ) of the absorber mass ( 110 ) on one of the axes of rotation ( 120 ) facing edge of the absorber mass ( 110 ), one of the axis of rotation ( 120 ) of the absorber mass ( 110 ) facing away from the absorber mass ( 110 ) or in a region in the radial direction, between the axis of rotation ( 120 ) facing away from the absorber mass ( 110 ) and the axis of rotation ( 120 ) facing edge of the absorber mass ( 110 ) lies. Tune vibration damper according to one of the preceding claims, wherein the spacer element ( 170 ) a storage structure ( 190 ), for example a bore or a bolt, which is designed to engage with a correspondingly formed bearing structure ( 131 ), for example a rivet or a bore in the guide component ( 130 ) to be rotatably connected, wherein from the bearing structure ( 190 ) at least one leg ( 205 ) protrudes, the investment contour ( 200 ). Tune vibration damper according to one of the preceding claims, wherein the spacer element ( 540 ) is at least partially stiff. Tune vibration damper according to one of the preceding claims, wherein the spacer element ( 170 ) is at least partially elastic. Tune vibration damper according to claim 7, wherein the spacer element ( 660 ) comprises a wound material, wherein free ends ( 205 . 206 ) of the material, the contact contour ( 200 ) form. Tune vibration damper according to one of the preceding claims, wherein the spacer element ( 540 ) at least one material recess ( 550 ) having. Tilgerschwingungsdämpfer according to any one of the preceding claims, wherein the contact contour ( 200 ) of the spacer element ( 170 ) at least one of a rotation axis ( 171 ) of the spacer seen from, outwardly curved investment area ( 210 ) having. Tilgerschwingungsdämpfer according to any one of the preceding claims, wherein the absorber mass contour contour ( 220 ) at least one convexly curved contact area ( 222 ), adapted to the plant contour ( 200 ) of the spacer element ( 170 ) to be in contact. Tilgerschwingungsdämpfer according to any one of the preceding claims, wherein the absorber mass contour contour ( 220 ) is formed in order to at several separate contact areas of the spacer ( 170 ), for example between one of the axes of rotation ( 120 ) of the guide component ( 130 ) facing away from the area of the plant contour ( 200 ) of the spacer element ( 170 ) and on one of the rotation axis ( 120 ) of the guide component ( 130 ) facing region of the spacer element ( 170 ). Tailstock vibration damper according to claim 12, wherein at least one of the absorber masses ( 110 ) has an essentially U-shaped recess in an outer contour, designed to form a limb ( 205 ) of the spacer element ( 170 ) playful record. Tilgerschwingungsdämpfer, wherein the spacer element ( 170 ) as a material, a metallic material and / or plastic. Tilgerschwingungsdämpfer according to any one of the preceding claims, wherein a surface, a contact contour ( 200 ), the spacer element ( 170 ) has a coating which is designed to, a static friction between the investment contour ( 200 ) of the spacer element ( 170 ) and the absorber mass contour ( 220 ) to enlarge.

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