WO2001004507A1

WO2001004507A1 - Torsion spring, torsional vibration damper and device with a torsion spring

Info

Publication number: WO2001004507A1
Application number: PCT/DE2000/002213
Authority: WO
Inventors: Ulrich Rohs
Original assignee: GAT Gesellschaft für Antriebstechnik mbH
Priority date: 1999-07-10
Filing date: 2000-07-10
Publication date: 2001-01-18

Abstract

The invention relates to a torsion spring (1) having spokes (6) with one end located radially inward and another end located radially outward. The inner ends of the spokes and the outer ends of said spokes are connected to one another. Said torsion spring works substantially free of centrifugal force.

Description

Torsion spring, torsional vibration damper and arrangement with one

torsion spring

The invention relates to a torsion spring, a

Torsional vibration damper and an arrangement with a torsion spring.

In general, torsion springs are used to transmit torsional forces in the desired manner. Depending on the area of application, a wide variety of spring arrangements are used for this. For example, torsion bars or spiral springs are used as torsion springs. Likewise, more complex arrangements are also used, in which tangentially arranged spiral springs are mounted between two disks or masses rotatably mounted relative to one another. In particular, the latter arrangements can be adapted to a high degree in terms of their spring properties, but their spring behavior is largely dependent on the centrifugal force.

It is therefore an object of the present invention to provide a torsion spring, the behavior of which is largely independent of the centrifugal force.

As a solution, a torsion spring with spokes with a radially inner and a radially outer end is proposed which the inner ends of the spokes and the outer ends of the spokes are connected to each other. If, in such an arrangement, a force acts on one end of a spoke which is counteracted on the other end of the spoke, this arrangement has the properties of a torsion spring. By connecting the spokes to each other at their respective ends, all spokes are loaded with corresponding forces.

The connection of the spoke ends to one another in such arrangements reduces the influence of centrifugal force compared to arrangements from the prior art. The torsion spring according to the invention therefore maintains its spring characteristic even at high rotational speeds.

The influence of centrifugal force can be further reduced if the spokes are regularly distributed around the circumference of the torsion spring. In particular, the angle between the individual spokes can correspond to the fraction of 360 ° corresponding to the number of spokes.

The space required for a torsion spring according to the invention can advantageously be reduced if the spokes are arranged essentially in one plane. This plane is preferably selected perpendicular to the axis of rotation of the torsion spring. The spring constant of the torsion spring according to the invention can be increased if the spokes are rigidly connected to one another. In addition, the spokes can be integrally connected to one another. Such a one-piece connection can be made outside, inside or outside and inside. Such an arrangement also has the advantage that the torsion spring according to the invention can be manufactured in one work step. In the case of a torsion spring arranged in one plane, punching is possible, for example.

In order to suitably design the spring property, the spokes in particular can be formed from spring steel. If the spokes are connected in one piece, it follows immediately that the connection is also made of spring steel. With excellent spring properties, this ensures simple production of the spring.

The spring characteristic can also be advantageously influenced if the spokes are longer than the radius bridged by the spokes. This results in longer spring travel, which enables a more precise adjustment of the damping characteristics.

In order to avoid unnecessarily large bending of the spokes at individual points thereof, the spokes can be curved. With such an arrangement, the torsional forces to which the spokes are subjected can be countered over a greater length of the spokes. The inner end of a spoke and the outer end of the same spoke can be offset by a connection angle between 0 "and 720 ^l \, preferably between 90 ° and 360", or between 180 "and 360". In this interval, the spokes ensure sufficient inherent strength of the torsion spring and at the same time sufficient variability to adapt the spring characteristics of the torsion spring.

The spokes are preferably arranged in the same direction. With such an arrangement, two different spokes can be arranged in overlapping angular ranges.

The torsion spring can each comprise force transducers located radially on the inside and / or radially on the outside, which are connected to the respective ends of the spokes. These force transducers can also be rigidly or integrally connected to the spokes. In this way, the corresponding forces can be easily introduced into the spring. In particular, it is possible to provide force transducers of this type in a quasi-standardized form on the torsion spring, so that different types of springs can be used without major difficulties. Likewise, with such an arrangement, springs of the same type can easily be used with different assemblies.

A torsion spring according to the invention can have at least one outer contact surface pointing in the circumferential direction and / or at least one in the circumferential direction. have inner bearing surface that is connected to the respective spoke end. Such a contact surface enables a power flow to be built up in a structurally simple manner between a corresponding assembly and the torsion spring. In particular, such a positive connection can be installed by simply plugging the modules and the torsion spring into one another. In this respect, the invention also proposes an arrangement with a torsion spring according to the invention and at least one further assembly, in which the assembly and the torsion spring are positively connected to one another.

The contact surface can be at least in a partial area on a plane that includes the axis of rotation. In the present context, the term "plane comprising the axis of rotation" means a plane in which the axis of rotation runs. With such an arrangement, forces can be applied at right angles to the radius of the torsion spring in this partial area, thereby ensuring high efficiency and low wear.

Adequate inherent rigidity of the torsion spring against tilting can be achieved by identifying at least three spokes.

In contrast, the use of exactly two spokes has the advantage that a greater degree of wrap around the spokes can be achieved than with multiple spokes. Appropriate measures, such as an increase in strength, can also achieve sufficient inherent rigidity in other ways.

A particularly uniform load on the torsion spring, in particular the spokes, can be achieved if the spokes are designed as bending beams, preferably of the same strength. In this way, the life of such a torsion spring can be increased considerably.

The spokes can be made stronger at their ends than in the middle, which can advantageously reduce the volume load in the area of the connections of the spoke ends. This also ensures a more even load on the entire spring, which is advantageous for the life of the spring and the spring properties.

The spokes can have a constant thickness in the axial direction. With such an arrangement, a torsion spring according to the invention is relatively flat with the same properties. Since a necessary change in the strength of the spokes takes place in the spring plane, the overall result is a relatively small volume for such a spring, so that such a spring can be used in a very space-saving manner.

The outer spoke ends and / or the inner spoke ends can be connected to one another via a corresponding connecting ring. When using such a connecting ring, contact surfaces or force transducers with which the torsion spring is to be operatively connected to other assemblies can be provided relatively easily. In particular, this can also be done independently of the exact spoke arrangement. In this way, the spring characteristic can be varied independently of the active connection with other assemblies.

The connecting ring can advantageously have the same thickness in the axial direction as the spokes. Such a torsion spring can easily be punched out of sheet metal, so that the torsion spring according to the invention can be produced relatively inexpensively. It goes without saying that the production of such a torsion spring by punching is also advantageous, regardless of its other features, in order to produce such a torsion spring inexpensively and within a very short time. Accordingly, the invention also proposes such a torsion spring which, according to the manufacturing process, has stamped burrs and / or surface deformations caused by stamping.

On the other hand, punching difficulties can arise if filigree structures, for example very thin spokes, bearing connections of the spokes or tight radii at the roots of the spokes, have to be produced. For such a torsion spring, the invention proposes the production by means of electron or laser beam processes in front. Although these are relatively time-consuming and cost-intensive, they enable the formation of sufficiently filigree structures. Accordingly, the invention also proposes a torsional vibration spring which has been produced in this way and which accordingly has a conversion zone in the surface caused by the electron or laser beam. Such a conversion zone also surprisingly requires an increase in strength, particularly in the filigree and therefore regularly particularly stressed areas, so that the entire torsion spring has a correspondingly longer service life.

A torsion spring according to the invention can preferably also be produced by carrying out rough machining by punching and fine machining by electron or laser beam methods. Here only the filigree areas need to be subjected to fine machining. In this way it is possible to produce a torsion spring quickly and yet with sufficient precision. A torsion spring produced in this way also has a conversion zone in the surface caused by the electron or laser beam and is advantageous regardless of its other features, as already described above.

The torsion spring can be connected in series with or parallel to a friction device. In this way, the torsion spring according to the invention can be used as a spring-damper device. Due to the extremely (laughing design of the invention Torsion spring follows from this the possibility of making the spring-damper device correspondingly flat.

In the present context, the term “switched” describes the fact that a force flow in a corresponding manner, be it in parallel or in series, runs through the corresponding assemblies.

It is also possible to connect a torsion spring according to the invention in series with or in parallel with another spring. Such an arrangement makes it possible in particular to implement a transition from radially inside to radially outside with the aid of a resilient assembly, so that an additional assembly which effects such a transition to power transmission can be dispensed with. In this way, the number of assemblies required for a specific arrangement can advantageously be reduced, which also makes the production of such assemblies correspondingly less expensive. Understandably, this also applies to series connection or parallel connection of a torsion spring according to the invention with a friction device.

If two spoke ends, that is to say the inner or the outer spoke ends, are not rigidly connected to one another, the connection can take place via at least one bearing.

In addition, the bending path of at least one spoke, preferably all spokes, can be limited by a system. This shortens the movable length of the respective spoke, which increases the spring constant. In particular, the system can come into contact with the spoke or the spokes progressively with increasing torsion angle of the torsion spring.

These measures enable the spring constant to be adapted to different circumstances in a very defined manner and to be selected as a function of the angle of rotation. This is particularly advantageous for torsional vibration dampers.

Since the spokes shift depending on the relative direction of rotation between the inner and outer ends of the spokes, the arrangement between the system or systems and spokes can be chosen differently with a positive or negative angle of rotation to one another. This ensures a maximum of individual adaptability.

In addition, it is possible to arrange two torsion springs according to the invention such that the inner spoke ends of a first torsion spring of the two torsion springs are connected to the outer spoke ends of the second torsion spring. It is also possible to arrange two torsion springs according to the invention in such a way that their inner spoke ends or their outer spoke ends are connected to one another. Through these arrangements, a series connection of the two torsion springs can be realized, which has a wider scope with regard to the spring characteristics of the overall spring allows. In particular, suitable stops can be provided, by means of which the characteristic of the overall spring can also be influenced.

It is also possible to connect the respective inner and the respective outer spoke ends to one another in the case of two torsion springs according to the invention. In this way, a parallel connection can be realized, which makes it possible, for example, to form an overall spring, the strength of which can no longer be produced by stamping, by means of two partial springs which can be produced by stamping. Such an arrangement also enables further interventions in the spring characteristic of the overall spring.

In order to avoid the spokes getting caught in a parallel arrangement of such torsion springs according to the invention, connected in series or in parallel, these torsion springs can be arranged in such a way that the spokes of one torsion spring are arranged in the opposite direction to the spokes of the other torsion spring.

In addition, the invention proposes a torsional vibration damper with a torsion spring according to the invention. Such a torsional vibration damper can be, for example, a friction disk damper or a 2-mass torsional vibration damper. It goes without saying that all other types of torsional vibration damper can advantageously be connected to such a torsion spring, the Advantages described above, in particular the relatively small space, apply accordingly to such a torsional vibration damper.

In particular, the invention proposes a Trilok converter with such a torsion spring. In this case, the torsion spring is preferably connected to a turbine of a Trilok converter, as disclosed, for example, in DE 197 51 752, DE 30 29 860 or US 5,590,750. Here, the Trilok converter according to the invention with the torsion spring according to the invention has the advantage over these known Trilok converters that centrifugal friction losses in the spring arrangement or other centrifugal effects are avoided, so that the arrangement according to the invention can be controlled in its properties in an unpredictable manner. As can be seen immediately, the Trilok converter according to the invention is extremely small and inexpensive, since the spring-guiding or force-conducting components can be dispensed with. This is particularly the case if the torsion spring is arranged between a holder carrying a friction device and the turbine.

In addition, the invention also proposes a torsional vibration damper with a torsion spring, which comprises at least one spoke, which has an inner end with a primary mass of the torsional vibration damper and an outer end with a secondary mass of the torsional vibration damper connected is. However, the direction of force flow through the torsional vibration damper plays no role here. In particular, the masses can also be chosen arbitrarily. A torsional vibration damper constructed in this way is distinguished by its extremely simple construction and can therefore be produced particularly cost-effectively and reliably. Here, the connection between the spoke or the spokes and the primary mass and the secondary mass can be selected in accordance with the above-described spoke arrangements. The same applies to the design of the spokes themselves.

Such a torsional vibration damper with only one spoke enables a particularly large angle of rotation between the primary mass and the secondary mass.

It goes without saying that such a torsional vibration damper must additionally have a friction device so that it can perform its damping function.

In particular when only one spoke is used, a parallel connection of two torsion springs, each with one spoke, can be advantageous. On the one hand, this enables large relative angles and, on the other hand, a relatively stable overall structure. In particular, these spokes connected in parallel can be arranged in opposite directions. In particular, such torsional vibration dampers can be connected in series with a clutch. In connection with a clutch, in particular a vehicle clutch, it is particularly necessary to have the greatest possible scope with regard to influencing the spring characteristic with a relatively small installation space. This is ensured by a torsion spring according to the invention.

Further advantages, aims and properties of the present invention are explained with reference to the following description of the attached drawing, in which three preferred embodiments are shown as examples. The drawing shows:

Figure 1 shows a torsional vibration damper with an inventive

Torsion spring in section along the line I-I in Fig. 2,

2 shows the torsional vibration damper according to FIG. 1 in cross section,

FIG. 3 shows section III in FIG. 2,

4 shows a second torsional vibration damper with a torsion spring according to the invention in section,

5 shows a third torsional vibration damper with a torsion spring according to the invention in section, FIG. 6 shows a schematic illustration of two torsion springs according to the invention connected in series,

FIG. 7 shows a schematic sectional illustration of two torsion springs according to the invention connected in series in a different way than in FIG. 6,

FIG. 8 shows two torsion springs according to the invention connected in parallel in a schematic sectional view,

FIG. 9 shows a torsion spring according to the invention in section,

FIG. 10 shows a further torsion spring according to the invention in a partial section,

FIG. 11 shows a further torsion spring according to the invention in a partial section,

FIG. 12 shows a door spring according to the invention in interaction with a Trilok converter with the liquid pressure-dependent friction device closed,

FIG. 13 shows the arrangement according to FIG. 12 with the friction device dependent on the liquid pressure,

14 shows an arrangement according to FIGS. 12 and 13 similar arrangement in which an inventive Torsion spring is connected in series with a tangentially acting spiral spring,

FIG. 15 shows the torsion spring according to the invention used in the arrangement according to FIG. 14 in a partial section,

Figure 16 shows another coil spring according to the invention in section and

FIG. 17 shows another of the arrangement according to FIGS. 12 and 13 similar arrangement.

In the case of fig. 1 to 3 shown torsional vibration damper is a friction disk damper, as it is used in clutch friction disks in motor vehicles. In this friction disc damper, a torsion spring 1 according to the invention connects a shaft 2 with a friction disc 3 of a vehicle clutch. Here, the friction disc 3 is provided with a sheet 4 in the usual manner. This sheet 4 is riveted to an outer connecting ring 5 of the torsion spring 1 according to the invention. The connecting ring 5 connects three spokes 6 at their outer ends. The spokes 6 are connected to each other at their inner end by an inner connecting ring 7.

The inner connecting ring 7 is in positive engagement with the shaft 2 by means of a tongue and groove connection. Here, the inner connecting ring 7 can be shifted coaxially to the shaft axis, as is required for a clutch friction disk. As can be seen immediately, the spokes 6 are regularly distributed around the circumference at an angle of 120 ″ to one another. They are curved, their ends being offset by a connection angle of approximately 180 °. As can be seen, the spokes 6 are arranged in the same direction.

The torsion spring 1 from the outer connecting ring 5, spokes 6 and the inner connecting ring 7 is stamped in one piece from spring steel. The spokes are tapered in their central area relative to the end area and are designed as a bending beam.

A friction device is provided parallel to the torsion spring. This friction device comprises a friction ring 8, which is also attached to the shaft 2 in a form-fitting manner and is axially displaceable to the shaft axis.

The friction ring 8 is pressed against the inner connecting ring 7 of the torsion spring 1 by means of spring struts 9 which are attached to the outer connecting ring 5 of the torsion spring 1. For this purpose, a slope 10 is used, which also serves as a friction surface between the friction ring 8 and the spring struts 9.

Instead of the struts 9, a plate spring or a similar adjustment device can also be used. It also goes without saying that the friction ring can also be arranged radially on the outside. It is also possible to close the friction ring with the spring or the struts connect and rub against the torsion spring 1 or a corresponding friction surface.

As can be seen immediately, the friction disc damper is built according to Fign. 1 to 3 extremely narrow, as tangential spring springs can be dispensed with. This arrangement also makes it possible in particular to compensate for misalignments and angular errors in the spring. With conventional friction disc dampers, this is only possible with great effort.

As can be seen immediately, the interlocking connections between the shaft 2 and the torsion spring 1 form an inner contact surface, while the holes for the rivet connection form outer contact surfaces. Each of the contact surfaces has partial areas that run parallel to a plane running through the shaft axis.

In the case of FIGS. The torsional vibration dampers shown in FIGS. 4 and 5 are 2-mass torsional vibration dampers, in which a spring friction device 13 is provided between a primary mass 11 and secondary mass 12, which are rotatably supported relative to one another. In both exemplary embodiments, a torsion spring 1 according to the invention is connected into the force flow between primary mass 11 and secondary mass 12. In this way, the spring characteristic of these vibration dampers can be varied to a greater extent. As can be seen, the torsion spring 1 in these exemplary embodiments is not designed to be flat in order to take account of structural features of the vibration dampers. However, like the torsion spring of the first exemplary embodiment, these torsion springs can also be punched or punched and deformed in one working step.

In order to switch the torsion spring 1 in these exemplary embodiments into the power flow between primary mass 11 and secondary mass 12, intermediate assemblies 14 (FIG. 5) or 15 (FIG. 5) are provided, each between the spring friction device 13 and the torsion spring 1 are effective. As can be seen, a spring according to the invention can be provided with such torsional vibration dampers by a minimal increase in overall length.

By connecting the outer ends of an inner torsion spring 1 to the inner ends of an outer torsion spring 1, a torsion spring with two torsion springs 1 connected in series can be provided, as shown in FIG. 6. The connection, as this exemplary embodiment shows, can be realized by an intermediate ring 16. Likewise, a series connection can be formed in that two torsion springs 1 are connected to one another on their inner connecting ring, as is shown schematically in FIG. 7 by reference number 17. As can be seen from this figure, oppositely arranged spokes 6 can be provided, so that the spokes 6 cannot get caught. Likewise, two torsion springs 1 can be connected in parallel, as shown in FIG. 8. In this exemplary embodiment, both the outer connecting ring 5 and the inner connecting ring 7 are connected to one another, as is indicated by the reference numerals 18 and 19. Such an arrangement makes it possible, for example, to connect two thin torsion springs 1 to one another to form a relatively strong overall torsion spring. Such an arrangement can make it possible to punch the overall torsion spring, although its actual strength no longer allows punching.

The torsion spring shown in FIG. 9 essentially corresponds to the torsion spring according to FIG. I. However, in the torsion spring shown in FIG. 9, rectangular recesses are provided on the connecting rings 5, 7, which serve as force transducers. As can be seen immediately, these force transducers have surface areas to which forces can be introduced into the torsion spring in the desired spring direction. The force transducers can form fit with corresponding assemblies and only need to be inserted into them. In this way, a relatively simple assembly of the torsion spring is possible. This torsion spring is also essentially punched. However, fillets 6 'and 6 "in the end regions of the spokes 6 on the rings 5 and 7 were cut out or re-cut by means of electron or laser processes in order to produce these regions with extreme precision Torsion spring surprisingly controllable, since these areas influence this behavior relatively strongly. On the other hand, this makes the torsion spring considerably more stable, since in these areas, which are among the most stressed areas of such a spring, a conversion zone caused by the electron or laser process ensures an increase in stability.

The two torsion spring variants according to Fign. 10 and 1 1 have straight spokes 6. While the length of the spokes 6 in the embodiment shown in FIG. 10 corresponds to the radius bridged by them, the spokes of the embodiment shown in FIG. 11 are longer than this radius.

In addition, in the case of FIGS. 10 and 11 illustrated embodiments, the spokes are not rigid at their outer ends, but are movably connected to one another or to the connecting ring 5. Bearing materials or bearings can be provided on this movable connection. In this embodiment too, the regions 6 'and the bearings are formed by means of electron or laser processes.

The two in Figs. The exemplary embodiments shown in FIGS. 12 to 15 show a series connection of a torsion spring 1 according to the invention with the turbine 20 of a Trilok converter. Here, the connection between the torsion spring 1 and the turbine 20 takes place by means of a driver 21, 11

while the torsion spring 1, on the other hand, is connected to a holding plate 30 serving as a holder for a friction device 31 via a driver 32. The in fig. 14 and 15 illustrated embodiment also has a tangential spring coil 22 connected in series with the torsion spring 1. In both exemplary embodiments, the friction device 31 is pressed against a housing 33, which is connected to the pump 34 of the Trilok converter, as a function of an oil pressure prevailing in the Trilok converter. Thus, while at low oil pressure there is a power loss from the housing 33, which is operatively connected to a drive, via the pump 34 to the turbine and then to an output 35 (see FIG. 13), the friction device 31 contacts the housing 33 at a higher oil pressure (see FIGS. 12 and 14) and at least part of the force flows via the friction device 31, the holder 30 and the spring according to the invention for the output. Here, the large gaps caused by the spokes 6 enable the oil pressure to act in an excellent manner on the holder 30.

The torsion spring 1 shown in FIG. 16 essentially corresponds to that shown in FIG. 10. However, the torsion spring 1 shown in FIG. 16 has only two spokes 6 which are wrapped around one another. Here, this torsion spring 1 is shown in Fig. 16 in a state in which the inner and outer spoke ends or the inner connecting ring 7 and the outer connecting ring 5 are rotated relative to one another or are loaded with a torque.

As can be seen, the spokes 6 bear against the inner connecting ring 7 on a system 23 in the case of the angle of rotation shown. If the torque is increased, the system 23 increases toward the outer end of the spoke. The spring constant thus increases because the bending beam length of the spokes 6 is reduced. Conversely, if the torque is reduced, the system 23 is shortened, as a result of which the movable length of the spokes 6 increases and the spring constant decreases accordingly.

As can be seen, the spokes 6 can also come into contact with one another with sufficient torque. It is understood that a similar arrangement can be provided with inverse torque on the outer connecting ring 5 or in the vicinity of the outer ends of the spokes 6.

If the torque is selected to be sufficiently large so that the spokes 6 abut the system 23, a space 24 remains between the system 23 and the inner end of the spoke, as shown in FIG. 16. This facilitates manufacture, among other things, since the gap between the inner connecting ring 7 and the spoke 6 can only be selected to be infinitely small with extreme difficulty. It is true that this intermediate space 24 means that there is no continuous increase in the spring constant, on the other hand, the intermediate space 24 can be chosen to be so small that deviations caused thereby remain meaningless. The intermediate space 24 can have any expedient shape, that is to say also a hole-like recess or the like.

The system 23, on the other hand, can also be arranged with respect to the spokes 6 in such a way that the spring constant changes in stages.

Measures can be provided on the connection between the connecting rings and the spokes in order to ensure an even introduction of force between the spokes and connecting rings. Constrictions or deliberately placed bores or recesses can also be used for this purpose. In particular, the occurrence of very high tension mushrooms on certain surface areas of the spokes or the connecting rings, which lead to a spring break, can be avoided in this way. Here, all measures are available to the person skilled in the art with which such wear breaks can be avoided.

The arrangement shown in FIG. 17 corresponds essentially to the arrangement according to FIGS. 12 and 13, which is why an explanation of the identical assemblies is omitted. In the arrangement shown in FIG. 17, however, a driver 21 'connected to the torsion spring 1 is provided at the radially outer end of the turbine 20, while the holder 30 is connected radially on the inside via a driver 32' Torsion spring 1 is operatively connected. To this extent, in this arrangement, the force flows at a higher oil pressure via the friction device 31 initially via the holder radially inward, and then via the torsion spring 1 radially outward to the driver 21 connected to the torsion spring 1 in a torque-resistant manner. This variation enables the force / friction / torque ratios to be adapted in a suitable manner. An arm 32 "at the outer end of the holder 30 serves only as a guide and only requires a stop at extremely large angles of rotation, as is also known in the prior art.

Claims

claims:

1. Torsion spring, characterized by spokes (6) with a radially inner and a radially outer end, the inner ends of the spokes (6) and the outer ends of the spokes (6) being connected to each other.

2. Torsion spring according to claim 1, characterized in that the spokes (6) are arranged regularly distributed around the circumference.

3. Torsion spring according to claim 1 or 2, characterized in that the spokes (6) are arranged essentially in one plane.

4. Torsion spring according to one of claims l to 3, characterized in that the spokes (6) are rigidly connected to one another.

5. Torsion spring according to one of claims l to 4, characterized in that the spokes (6) are integrally connected to one another.

6. Torsion spring according to one of claims l to 5, characterized in that the spokes (6) are formed from spring steel.

7. Torsion spring according to one of claims 1 to 6, characterized in that the spokes (6) are longer than the radius bridged by the spokes (6).

8. Torsion spring according to claim 7, characterized in that the spokes (6) are curved.

9. Torsion spring according to claim 7 or 8, characterized in that the inner end of a spoke (6) and the outer end of the spoke (6) offset by a connecting angle between 0 "and 720", preferably between 90 "and 360" are.

10. Torsion spring according to one of claims 1 to 9, characterized in that the spokes (6) are arranged in the same direction.

1 1. Torsion spring according to one of claims 1 to 10, characterized by at least one in Um l ngs direction, outer

Contact surface that is connected to the outer spoke ends.

12. Torsion spring according to one of claims 1 to 1 1, characterized by at least one in the circumferential direction inner contact surface which is connected to the inner spoke ends.

13. Torsion spring according to claim 1 1 or 12, characterized in that the contact surface is at least in a partial area on a plane comprising the axis of rotation.

14. Torsion spring according to one of claims 1 to 13, characterized by at least three spokes (6).

15. Torsion spring according to one of claims 1 to 14, characterized in that the spokes (6) are designed as a bending beam, preferably of the same strength.

16. Torsion spring according to one of claims 1 to 15, characterized in that the spokes (6) are formed stronger at their ends than in the middle.

17. Torsion spring according to one of claims 1 to 16, characterized in that the spokes (6) have a constant thickness in the axial direction.

18. Torsion spring according to one of claims 1 to 17, characterized in that the outer spoke ends are connected to one another via an outer connecting ring (5).

19. Torsion spring according to one of claims 1 to 18, characterized in that the inner spoke ends are connected to one another via an inner connecting ring (7).

20. Torsion spring according to claim 18 or 19, characterized in that the connecting ring (5, 7) has the same thickness in the axial direction as the spokes (6).

21. Torsion spring according to one of claims 1 to 20, characterized in that the torsion spring (1) in series with a

The friction device is switched.

22. Torsion spring according to one of claims 1 to 21, characterized in that the torsion spring (1) is connected in parallel to a friction device (8, 9).

23. Torsion spring according to one of claims 1 to 22, characterized in that the torsion spring (1) is connected in series with another spring (13).

24. Torsion spring according to one of claims 1 to 23, characterized in that the torsion spring (1) is connected in parallel to another spring.

25. Torsion spring according to one of claims l to 24, characterized in that the inner or the outer spoke ends are connected via at least one bearing.

26. Torsion spring according to one of claims 1 to 25, characterized in that the bending path of at least one spoke (6) is limited by a system (23).

27. Torsion spring according to one of claims l to 26, characterized in that the system (23) progressively comes into contact with the spoke (6) with increasing angle of rotation.

28. Torsion spring according to one of claims 1 to 27, characterized by areas with a U conversion zone in the surface.

29. Torsion spring according to claim 28, characterized in that the conversion zone is caused by electron or laser beam treatment.

30. Torsion spring according to one of claims 1 to 29, characterized in that at least parts are stamped.

31. Torsion spring, characterized by two torsion springs (1) according to one of claims 1 to 30, in which the inner ends of a first of the torsion springs are connected to the outer ends of the second torsion spring.

32. Torsion spring, characterized by two torsion springs (1) according to one of claims 1 to 31, the inner spoke ends or the outer spoke ends of which are connected to one another.

33. Torsion spring, characterized by two torsion springs (1) according to one of claims 1 to 32, the inner and outer spoke ends of which are connected to one another.

34. Torsion spring according to one of claims 31 to 33, characterized in that the spokes (6) of one torsion spring (1) are arranged in opposite directions to the spokes (6) of the other torsion spring (1).

35. torsional vibration damper, characterized by a

Torsion spring, which has at least one spoke with a radial comprises an inner end and a radially outer end, the radially inner end being connected to a primary mass and the radially outer end being connected to a secondary mass of the torsional vibration damper.

36. torsional vibration damper, characterized by a torsion spring (1) according to one of claims 1 to 34.

37. Torsional vibration damper according to claim 35 or 36, characterized in that the torsional vibration damper is a friction disc damper.

38. Torsional vibration damper according to claim 35 or 36, characterized in that the torsional vibration damper is a 2-mass torsional vibration damper.

39. Torsional vibration damper according to claim 35 or 36, characterized in that the torsional vibration damper is a Trilok converter.

40. Torsional vibration damper according to claim 39, characterized in that the spring is connected to a turbine (20) of the Trilok converter.

41. Torsional vibration damper according to claim 39 or 40, characterized in that the spring in a hydraulic space of the

Trilok converter is arranged.

42. Torsional vibration damper according to one of claims 35 to 41, characterized in that the torsional vibration damper is connected in series with a clutch.

43. Arrangement with a torsion spring according to one of claims 1 to 34 and at least one further assembly, wherein the assembly and the torsion spring are positively connected to each other.