JPH09177889A - Rotation vibration damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To ensure a most suitable load or operation of an energy storage apparatus on all occurring operation conditions, in a rotation vibration damper being of a type having at least two constituting members rotatable against resistance of at least one energy storage apparatus and a load range to compress the energy storage apparatus by the constituting members. SOLUTION: An energy storage apparatus 7 has at least two coil springs and a first coil spring 9 being one of the coil springs is at least partially contained in a hollow chamber formed by using the windings of the other second coil spring 8. In this case, the first coil spring 9 has an end section having at least one winding having a central winding diameter larger than that of the winding contained in the second spring 8. The end section of the first coil spring 9 is supported, as seen from the axial direction of the energy storage apparatus 7, at the winding of the end part of the second coil spring 8.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION The present invention has at least two components which are rotatable against the resistance of at least one energy store, the components having a load range for compressing said energy store. A rotary vibration damper of the type having

[0002]

2. Description of the Prior Art According to US Pat. No. 5,377,796, a hydrodynamic torque converter uses a rotary vibration damper, which is arranged in an outer coil spring and in the spring. It is known to have a type of received internal coil spring. In this case, the inner and outer coil springs have at least approximately the same length.

Such energy stores are used in flywheels composed of a plurality of masses, as can be seen from US Pat. No. 5,367,919. In this case, the energy accumulator is provided between the primary momentum mass which can be connected to the drive motor and the secondary momentum mass which can be connected to the transmission via a clutch, and between both momentum masses. Allows relative rotation against the action of the energy store.

[0004]

SUMMARY OF THE INVENTION The object of the invention is to improve a rotary vibration damper of the type mentioned at the beginning such that the energy store is satisfactorily loaded or functional in all operating conditions which occur. To do so.
Furthermore, it is desired to ensure a particularly simple assembly and a cost-effective production of the rotary vibration damper. Moreover, in the structural form of the rotary vibration damper, it is desired to enable many changes or adjustments of the torque characteristic line or the rotation resistance characteristic line existing between the constituent members that can rotate relative to each other. Therefore, over at least a partial range of the total rotation angle between the constituent members, a very soft rotation range, that is, a rotation range having a slight rotation resistance value and a rotation range having a higher rotation resistance value are realized. I want to get it.

[0005]

SUMMARY OF THE INVENTION The object of the present invention is that the energy store consists of at least two coil springs.
A first coil spring, which is one of the coil springs, is at least partially received inside the hollow space formed by the winding of the other second coil spring, in which case the first coil spring
Coil spring having an end section with at least one winding having a larger central winding diameter than the winding received within the second spring, the end section of the first coil spring having:
This has been solved by being able to bear on the end winding of the second coil spring, as seen in the axial direction of the energy store.

[0006]

The energy accumulators used to implement the invention each have at least one first coil spring, which coil spring is at least partially due to the winding of the second coil spring. It is received inside a limited spring inner chamber. In this case, the first coil spring has at least two windings, of which the first winding is able to receive this winding inside the second coil spring. And a second type of winding has a second central winding diameter greater than the first central winding diameter. In this case, this second type of winding is located outside the spring inner chamber limited by the winding of the second coil spring, as seen in the direction of the longitudinal axis of the energy store.

According to the inventive design of the energy store, the coil having the larger central coil diameter of the first coil spring is connected to the second coil spring, that is to say the end area or end of the second coil spring. It is guaranteed that the winding can be supported. This ensures that the first coil spring is kept positioned relative to the second coil spring when viewed in the direction of rotation of the rotary vibration damper. Therefore, the first coil spring cannot move freely inside the second coil spring. Upon compression of the energy store, at least one winding having the larger central diameter of the first coil spring is provided with at least one load range of the at least one rotatable component and the second coil spring. Is clamped between one end region or end winding of the rotor, the first coil spring circumferentially maintains the defined position inside the rotary vibration damper and thus the rotary vibration damper. It is also guaranteed that no imbalance will occur during the operation of the vessel. Such an imbalance occurs when using an energy store with an outer coil spring and a shorter inner coil spring provided therein. The energy accumulators constructed according to the invention are arranged symmetrically in the rotational vibration damper in the circumferential direction,
This allows the imbalance to be eliminated in practice.

At least one of the larger central diameter turns of the first coil spring may be supported by the end turns of the second coil spring with a support ring interposed. It is particularly advantageous if the winding of the first coil spring having the larger central diameter bears directly on the winding of the second coil spring. Both windings of the first and second coil springs in contact with each other may advantageously be arranged such that they make contact over at least 40% of the circumference of the winding. In the case of a linear energy store, the largest possible contact area is desired.

If an intermediate ring is used between at least two windings of both springs which are associated with one another,
The sides of this ring are expediently adapted to the course of the respective windings of both coil springs, so that a satisfactory mutual support and load of both coil springs is ensured. If such an intermediate ring is used, the windings may have leads, possibly for matching the springs, with the leads of the other windings. In this case, the side surfaces of the intermediate ring can have suitable slopes on which the windings are supported. In particular for the outer coil spring, the above-mentioned construction is advantageous. This is because, in this case, the end winding can be formed by simply cutting off or separating the spring wire. Therefore, in such a configuration, it is not necessary to grind suitable end turns at least in the outer coil spring. Intermediate ring is first
Of the spring is received in a winding having a smaller central winding diameter.

In order to ensure satisfactory mutual support of both coil springs, at least one of the windings of the first coil spring and at least one end winding of the second coil spring have the same central winding. It is particularly advantageous to have a line diameter. This prevents the mutually supporting windings from being displaced relative to one another in the radial direction. This is of particular significance in energy stores loaded in blocks. The turns of the coil spring can be chamfered at least slightly, at least in the area of mutual contact.

The first coil spring has one large diameter spring coil which can be clamped between at least one load range of the rotatable component and the end coil of the second coil spring. In spite of the fact that it can have only strips, it is also advantageous for many applications that the first coil spring has at least two large-diameter windings. In this case, the windings having the larger diameter may be arranged such that they are at least substantially in contact with each other when the first coil spring is unloaded and when viewed in the axial direction of the coil spring. it can.

[0012] For more applications, the first coil spring has a further coil having a predetermined coil lead following the coil carried by the end coil of the second coil spring, Thereby the first coil spring forms another spring section which is effective in series with the second coil spring, for which the spring range of the first coil spring received in the second coil spring is Advantageously, it is parallel to the second coil spring.

It is also advantageous for many applications that both coil springs have at least approximately the same wire diameter. However, for other use cases the first
It is also advantageous for the coil spring in question to have a smaller wire diameter than the second coil spring. However, the first coil spring can have a larger wire diameter than the second coil spring.

It is particularly advantageous that at least the section of the first coil spring which is receivable in the inner space defined by the windings of the second coil spring is shorter than the length of the second coil spring. Is. This makes it possible to realize a rotary vibration damper having at least two stages of spring characteristic lines. According to another feature of the invention, the energy store may have a third coil spring configured similarly to the first coil spring. In this case, the windings with the smaller median diameter of the first and second coil springs are respectively inserted into one end region of the second coil spring. In this case, the first and third coil springs each only extend over a partial range of the length of the second coil spring. Between the opposite end windings of the first and third coil springs, a predetermined relative rotation is possible against the action of the second coil spring between the constituent parts of the rotary vibration damper. There is play or space to play. The first and third coil springs can in this case have the same wire diameter or different wire diameters. Furthermore, the spring values of the first and third coil springs can be different.

It is particularly advantageous that the windings of the first coil spring and optionally the third coil spring have a winding direction different from that of the winding of the second coil spring. is there. The elastic windings of the coil spring can have at least approximately the same winding leads. However, the winding leads of the second coil spring may be larger or smaller than the winding leads of the first coil spring and possibly the third coil spring received inside this second coil spring. Is also purposeful.

With respect to the longitudinal axis, it is particularly advantageous if the energy store has a relaxed, curved shape when using an energy store with a large length-to-outer diameter ratio. For this purpose, at least one of the coil springs has a precurved shape in the relaxed state. In this case, however, most use cases
It is expedient if both coil springs, and possibly all three coil springs, have a pre-curved shape in the relaxed state. It is advantageous for the coil springs to have different bending radii with respect to the longitudinal axis of the energy store, but in many other cases it is advantageous to construct the coil springs with at least approximately the same bending radius. Is. This also facilitates assembly.

When using a pre-curved coil spring, the first coil spring and possibly the third coil spring coil which axially adjoin the end coil of the second coil spring are , In the relaxed state of the energy store,
It is particularly expedient if it is in contact with at least the radially inner region of the end winding of the second coil spring.

Particularly preferred is a coil spring having a spring range which is receivable in the second coil spring, from a coil having a small central coil diameter to a coil or coil having a large central coil diameter. Providing at least one intermediate winding having a section that extends helically into the section.

The end winding of the second coil spring and the end winding of the first coil spring or optionally of the third coil spring having a large central diameter are described in DE-A 42229416. Advantageously, it is constructed as shown in the book. This guarantees a satisfactory load on the coil spring, and the risk of breakage of the end windings is significantly reduced.

The energy accumulator is preferably configured to allow a pivot angle of at least 30 ° between the mutually rotatable components of the rotary oscillator in both rotational directions. . It is expedient if at least two, and at most four, energy stores are preferably arranged symmetrically with respect to the axis of rotation of the rotary vibration damper.

The rotary vibration damper is preferably a component of a flywheel consisting of a number of masses, or advantageously formed like this.

[0022]

BRIEF DESCRIPTION OF THE DRAWINGS Additional features and advantages of the invention will now be described with reference to the drawings.

The rotary vibration damper, shown partially in FIGS. 1 and 2, forms a split flywheel 1. This flywheel 1 has a first or primary flywheel mass body 2 and a second or secondary flywheel mass body 3 which can be fixed to an output shaft (not shown) of an internal combustion engine. A friction clutch can be fixed to the second flywheel mass body 3 with a clutch disc interposed. Via the clutch disc, an input shaft of the transmission, which is also not shown, can be connected and disconnected. The flywheel masses 2 and 3 are rotatably supported by bearings 4 therebetween. In the illustrated embodiment, this bearing 4 is arranged radially outside of a hole 5 for passing a fixing screw for attaching the first flywheel mass 2 to the output shaft of an internal combustion engine. A damping device 6 is effective between both flywheel masses 2 and 3. This damping device 6 has an energy store 7,
At least one of the energy stores 7 is formed by coil compression springs 8,9. In particular, as can be seen in FIG. 2, the coil compression spring 9 is completely received in the field completely in the space formed by the winding 8a of the spring 8 or, in other words, both coil springs 8, 9 are of their length. They are located almost inside and outside each other. In the illustrated embodiment, the extension angle or length 11 of the section 10 of the coil spring 9 received in the coil spring 8 is smaller than the length 12 of the outer coil spring 8. It is expedient in this case for the spring section 10 of the spring 9 to be 30 ° and 90 °.
Between the outer spring 8 and the outer spring 8 by a value which is preferably in the range between 45 ° and 70 °. However, the difference length or the difference angle can also be larger or smaller than said value.

Both flywheel masses 2, 3 have a load range 14, 15 or 16 for the energy store 7. In the illustrated embodiment, the load ranges 14, 15 are defined by the sheet metal parts 17, 18 forming the first mass body 2.
It is formed by the stamped part provided in the. The load range 16 provided between the load ranges 14 and 15 in the axial direction is
It is formed by a flange-shaped load component 20, which is connected to the secondary bounce mass 3 via rivets 19, for example. This component 20 serves as a torque transmission member between the energy store 7 and the flywheel mass 3. The load range 16 is formed by radial arms or overhangs provided on the outer circumference of the flange-shaped load component 20. The component 17 produced by cold deformation of sheet metal material serves to secure the first flywheel mass 2 or the entire split flywheel 1 to the output shaft of an internal combustion engine. On the outside in the radial direction, the component 17 is connected to a component 18, which is likewise manufactured from sheet metal.
Both components 17 and 18 form a ring-shaped chamber 21 with a torso-shaped region 22. Ring-shaped chamber 21
Alternatively, the torso-like region 22 is at least partially filled with a viscous medium, for example grease. Between the monoliths or the load areas 14, 15 when viewed in the circumferential direction, the components 17, 18 limit the torso-like area 22 and receive the energy store 7 and guide it both radially and axially. The bulges 23 and 24 are formed. At least when the device 1 rotates, the windings of at least the spring 8 are
7 and / or 18 bears the extent that limits the torso-like area 22 radially outwards. In the embodiment shown, attrition protection 25 is provided, which is formed by at least one sheet metal intermediate layer or sheet insert.
5 bears at least a spring 8 radially. The attrition protection body 25 extends circumferentially advantageously over at least the entire length or angular dimension of the relaxed energy store 7. Due to the fact that at least the winding of the spring 8 is supported by centrifugal force, the length of the energy store 7 or the coil spring 8 is increased between this winding and the component frictionally engaged with this winding. When changing or compressing, a friction damping effect related to the rotational speed is produced.

Inside the radial direction, the radially extending component 17 has an intermediate part or boss 26. This intermediate portion or boss 26 receives or holds the bearing ring inside the ball bearing 4. The outer bearing ring of the ball bearing 4 holds the flywheel mass body 3.

As can be seen in particular in FIG. 2, the load range 16 is angularly smaller than the load ranges 14 and 15 for positioning the energy store 7 in the circumferential direction, so that the theory shown in FIG. Starting from a stationary or starting position, it is possible to rotate the flywheel masses 2 and 3 slightly in both directions of rotation without a spring effect.

FIG. 3 shows the end region of the energy store 7 shown in FIG. In this case, in FIG. 3a the spring 9 is shown in section and in FIG. 3b it is shown completely, ie from the outside. This allows the course of the individual windings of this spring 9 to be better seen with respect to the course of the windings of the spring 8. The coil spring 9 has an end section 27 which in the embodiment shown has approximately two complete windings 28. The winding adjacent to the end winding 29 of the coil spring 8 is the end winding 29.
Directly to, and at least radially inwardly of, the range 30
It is supported by. This ensures that when the energy store 7 forms a block, torque is transmitted at least through the area inside the windings 28, 8a. However, it is advantageous that the end winding 29 and the adjacent winding 28 bear against each other over a large circumferential extent, so that the spring 8 is compressed by the end section 27 when the energy store 7 is compressed. It is a perfect load. The winding 28 of the end section 27 connected to the coil spring 8 and at least the end winding 29 and preferably the other winding 8a of the spring 8 have at least approximately the same central winding diameter 30, so that both It is advantageous if a good support between the coil springs 8 and 9 is ensured. The spring section 10 of the coil spring 9 received inside the passage or cavity defined by the winding 8a of the coil spring 8 has a winding 9a with a smaller central winding diameter 31. FIG.
As can be seen from (a) and (b), the windings of the springs 8 and 9 are wound in opposite directions, and have the leads in the opposite directions when viewed in the circumferential direction of the windings. That is, this means that the winding of one spring rises clockwise, while the other spring rises counterclockwise. In this case, the winding 8a,
The size of the leads of 9a can be the same size or different. In this case, it is advantageous that the size of the lead of the winding 8a is larger than the size of the lead of the winding 9a. The latter is shown in the drawing.

It is expedient that both coil springs 8 and 9 have at least approximately the same wire diameter. However, for many applications, the wire cross section of the coil spring 9 has a smaller diameter than the wire cross section of the coil spring 8.

When the energy storage device 7 is compressed, the spring 9 is used.
The windings of the end section 27 of FIG. 2 are clamped or clamped between the corresponding end winding 29 of the spring 8 and the load range 14, 15 or 16 (FIGS. 1 and 2).

The cross-sections of the wires of the springs 8, 9 and their respective winding leads and the length 11 of the spring section 10 and the length of the spring 8 are:
The windings 8a of the spring 8 are in harmony with each other so that when the full pivoting angle possible between the two mass bodies 2 and 3 is swiveled.

It is particularly advantageous for the assembly and function of the rotary vibration damper that at least one of the coil springs 8, 9 has a pre-curved shape in the relaxed state. Also, in many other cases, both coil springs 8, 9 have a pre-curved shape in a relaxed state, with respect to the longitudinal axis of the energy store 7,
Both coil springs 8, 9 preferably have at least approximately the same radius of curvature. However, for some applications, the radius of curvature of at least one of the springs 8 and 9 is equal to the average radius 32 (FIG. 2) in which the energy store 7 is incorporated, in order to optimize the stress in the corresponding spring wire.
It is advantageous if they are chosen to be somewhat larger or smaller than.

The outer diameter of the winding 9a is the same as the winding 9 of the spring section 10.
It is adapted to the inner diameter of the winding 8a so that a is guided radially by the winding 8a with virtually no play or only a slight play. As can be seen from FIG.
The energy store 7 or the coil spring 8 has a large length-
Due to the outer diameter ratio, a large turning angle is possible between both flywheel mass bodies or flywheel members 2, 3.

Further, as can be seen from FIGS. 3 to 3B, the coil spring 9 has an intermediate winding 33 for connecting the windings 9a and 28 to each other. This intermediate winding 33 forms a section that extends spirally from a winding with a small central winding diameter 31 to a winding with a large central winding diameter. In this case, the intermediate winding 33 is constructed and positioned with respect to the windings 28, 29 so that a sufficient support for the operation of the rotary vibration damper is ensured between both springs 8 and 9. . The above-described defined course or the defined position of the intermediate winding 33 is maintained by the curved shape given to the coil springs 8 and 9 in advance. This is because the springs 8 and 9 cannot rotate relative to each other due to the above curve.

In order to increase the service life of the springs 8 and 9 or to prevent the end winding 29 of the spring 8 and the end winding 34 of the spring 9 from being broken, said end winding is a patent of the Federal Republic of Germany. Advantageously, it is described in published application 4229416.

In the construction of the energy accumulator 7 shown in FIG. 2, two such energy accumulators are arranged around the ring-shaped chamber 21. In this case, as can be seen from FIG. 2, the installation is carried out so that there is substantially no imbalance in the system. The end sections of the spring 9 are therefore arranged diametrically opposite one another.

Based on the configuration according to the present invention, the coil spring 9
The spring section 10 received in the coil spring 8 is uniquely positioned relative to the spring 8 in the circumferential direction, so that the spring section 10 does not move or float inside the coil spring 9. This avoids an unbalanced configuration during operation of the rotary oscillator.

According to an embodiment not shown, at least one spring 8 can receive two coil springs which are constructed like spring 9. Moreover, one spring 8
In the second end region, as shown in FIG. 2, however, it is also possible to receive a spring 9 which is appropriately adjusted in length. The length 11 of each spring section 10 must in some cases be appropriately shortened. In this case, there is a play or gap between the facing end areas of the appropriate spring sections 10 of both springs.

The individual springs can have the same spring value. However, it is also advantageous for the springs to have different spring values.

The energy accumulator 107 of FIGS. 4 to 4 (b) is constructed similarly to the energy accumulator 7 of FIGS. 3 to 3 (b). That is, the energy store 107 likewise has two coil springs 108 and 109. The coil spring 109 differs from the coil spring 9 in that it has only one complete winding 128 having a large central winding diameter. With regard to the other features, however, the spring 109 corresponds to the spring 9. For example, in this case also, there is a spiral intermediate winding 133.

The energy store 207 according to FIGS. 5 to 5 (b) likewise has two coil springs 208, 209.
have. These coil springs 208, 209 are inserted in and out in a manner similar to that described in connection with the embodiment of FIGS. 3 to 3b, when viewed in the longitudinal direction of the energy store 207. There is. An important difference between the embodiment of FIGS. 3 to 3b and the embodiment of FIGS. 5 to 5b is the construction of the end section 227 of the spring 209 which is supported by the spring 208. It is in. In particular, as can be seen in FIG. 5, the end section 227 comprises a winding section 228 wound in a ring or spiral. The ring-shaped area 228a of the winding section 228 is in this case the area 228a.
Are configured to extend circumferentially from about 210 ° to 280 °. In this case, FIG. 5 to FIG.
As can be seen, the cross section of the wire remains substantially maintained, i.e. constant. In the embodiment of FIGS. 5 to 5b, the ring-shaped winding area 228a extends circumferentially over approximately 270 °. That is, end winding or winding section 228 is not ground when viewed in the longitudinal direction of energy store 207. Such polishing is performed, for example, in FIGS.
In the case of the winding section 34 or winding of the spring 9 shown in (b) of FIG. The winding section 228 is provided only in the free end region on the outer circumference of the wire forming the winding 228.
Four. As can be seen from FIG. 5, the polishing section 234,
Ensuring that the total outer contour of the energy store 207 or the end section 227 has a circular form. When viewed in the axial direction of the coil spring 209, it has no lead angle or substantially no lead angle. Between the ring-shaped winding area 228a and the winding 209a received inside the spring 208, a spiral winding area ensuring a transition from the winding 209a to the winding or the winding area 228a. 233 is provided. In the embodiment according to FIGS. 5 to 5b, the winding 209a and the end winding range 228a.
Each central winding diameter corresponds to the value 31 or 30 in FIG.

For many applications, the coil spring 9,
109,209 is a second corresponding spring 8,108,20
8 to be supported by 8 following its end sections 27, 227 or following its end windings 28, 128, 228,
It has a further winding with a given winding lead, whereby the spring section of the spring 9,109,209 (FIG. 3) is received in series with a suitable spring 8,108,208 or inside the latter spring. An additional spring section is formed which is effective in series with the spring section 10) in a and b. With such a configuration of the energy store, a three-step spring characteristic line is possible when using two springs. in this case,
The additional spring section of the corresponding spring 9, 109, 209 has a lower spring value than the assigned spring 8, 108, 208, so that the additional spring range and the corresponding spring 8, 108, 208. Can initially be valid in series. In this case, the additional spring area first forms a block, so that after that the springs 8, 108, 208
Only can be valid. Springs 8, 108, 20
After the 8 has been compressed, this spring 8, 108, 20
Since the windings 9, 109, 209 received in 8 act in parallel, the total spring value of the energy store is increased.

In the embodiment shown in FIGS. 3 to 3 (b), the windings 28 with a large central winding diameter have a predetermined spacing instead of abutting each other, and this end section 27.
Can produce a damping effect over a predetermined relative rotation angle between the two flywheel masses 2, 3. In this case, the spring value of the winding 28 forming the end section 27 is advantageously smaller than that of the spring 8.

The claims in this specification do not limit the achievement of other patent protections. Applicants reserve the right to claim patents for other features heretofore disclosed in the specification and / or drawings.

References to the dependent claims show modified embodiments of the independent claims with the features of each dependent claim. That is, the citation of dependent claims does not indicate an abandonment of the independent protection of the features of the referenced dependent claim.

The subject matter of the dependent claims, however, also constitutes an independent invention having a construction unrelated to the subject matter of the preceding dependent claims.

Furthermore, the invention is not limited to the embodiments described in the specification. Rather, numerous variations are possible within the framework of the invention. In particular, new features are created or manufactured by features which are inventive and combinable in connection with, for example, the features or elements or method steps described in the description and examples and claims and shown in the drawings, Variations, parts and combinations and / or materials are possible which, as far as inspection and working methods are concerned, form new process steps or continuations of process steps.

[Brief description of the drawings]

1 is a cross-sectional view of a damping device according to the present invention.

2 is a partial cross-sectional view taken along the line II-II of FIG.

FIG. 3 shows an inventive configuration of an energy store for use in the device according to FIGS. 1 and 2.

FIG. 4 is a diagram showing another configuration of the energy storage device according to the present invention.

FIG. 5 shows additional possibilities for the configuration of the energy store.

[Explanation of symbols]

 1 flywheel 2 primary flywheel mass body 3 secondary flywheel mass body 4 bearing 5 hole 6 damping device 7 energy accumulator 8, 9 coil spring 10 section 11 length 12 extension dimension 14, 15, 16 load range 17, 18 metal Thin plate part 19 Rivets 20 Load component part 21 Ring-shaped chamber 22 Torso-shaped range 23, 24 Bulging part 25 Abrasion protection body 26 Boss 27 End section 28 Roll 29 End roll 30 Center roll diameter 31 Center roll Strip diameter 32 Central diameter 33 Intermediate winding 34 End 107 Energy storage 108, 109 Coil spring 128 Winding 133 Intermediate winding 207 Energy storage 208, 209 Coil spring 227 End section 228 Winding section 233 Winding range 234 Polishing part

Front Page Continuation (72) Inventor Thomas Lauinger Germany Ettlingen Reingoldstraße 9 (72) Inventor Holger Zeitl Germany Buhl Honaustraße 29

Claims (21)

[Claims] 1. At least two components which are pivotable against the resistance of at least one energy store,
A rotary vibration damper of the type wherein said component has a load range for compressing said energy store, said energy store comprising at least two coil springs, one of which is a coil spring. One coil spring is at least partially received inside the cavity formed by the winding of the other second coil spring, in which case
The first coil spring has an end section with at least one winding having a larger central winding diameter than the winding received inside the second spring, the end section of the first coil spring being Is capable of being supported by the end winding of the second coil spring when viewed in the axial direction of the energy accumulator. 2. At least two components rotatable against the resistance of at least one energy store,
In a rotary vibration damper of the type in which the component has a load range for compressing the energy store, the energy store has at least one first coil spring, the coil spring being at least Partly received in the spring inner chamber bounded by the windings of the second coil spring, the first coil spring having at least two windings, the first winding being A second central winding diameter having a first central winding diameter that enables the winding to be received within a second coil spring, the second type winding being larger than the first central winding diameter. Has a central winding diameter, in this case the second
Rotational vibration damper, characterized in that the winding of the kind is outside the inner spring chamber, which is limited by the winding of the second coil spring, as seen in the direction of the longitudinal axis of the energy store. 3. The second type of winding has a central winding diameter that enables the second type of winding to be supported by the end winding of the second coil spring. Rotary vibration attenuator. 4. At least one of the windings of the first coil spring
3. A rotary vibration damper according to claim 1 or 2, wherein one and the at least one end winding of the second coil spring have the same central winding diameter. 5. The at least one spring winding of the first coil spring having a large diameter is between the load range of the at least one rotatable component and the end winding of the second coil spring. The rotary vibration damper according to any one of claims 1 to 4, which can be tightened in. 6. A rotary vibration damper as claimed in claim 1, wherein both coil springs have at least approximately the same wire diameter. 7. A rotary vibration damper according to claim 1, wherein the first coil spring has a smaller wire diameter than the second coil spring. 8. A rotary vibration damper as claimed in claim 1, wherein the first coil spring has at least two windings with a large diameter. 9. The rotary vibration damper according to claim 8, wherein the windings are in contact with each other in the unloaded state when viewed in the axial direction of the first coil spring. 10. The section of any one of claims 1 to 8 wherein the section of the first coil spring that is receivable in the inner chamber bounded by the winding of at least the second coil spring is shorter than the second coil spring. A rotary vibration damper according to item 1. 11. The rotary vibration damper according to claim 1, wherein the winding of the first coil spring has a winding direction different from that of the winding of the second coil spring. . 12. A rotary vibration damper according to claim 1, wherein both coil springs have at least approximately the same winding leads. 13. The winding pitch of the second coil spring is greater than the winding pitch of the windings of the first coil spring received therein, according to any one of claims 1 to 12. Rotational vibration attenuator. 14. The rotary vibration damper according to claim 1, wherein at least one coil spring has a precurved shape in a relaxed state. 15. The rotary vibration damper according to claim 1, wherein both coil springs have at least approximately the same radius of curvature with respect to the longitudinal axis of the energy store. 16. The energy storage device according to claim 1, wherein the energy storage device has a large length-outer diameter ratio.
A rotary vibration damper according to the item. 17. The winding of the first coil spring bounding the end winding of the second coil spring is relaxed in the energy store at least in the radial inner range of the end winding. The rotary vibration damper according to any one of claims 1 to 16, wherein the rotary vibration dampers are in contact with each other. 18. A first coil spring having at least one intermediate winding having a section helically extending from a winding having a small central winding diameter to a winding having a large central winding diameter.
The rotary vibration attenuator according to any one of claims 1 to 17, which has three. 19. The energy accumulator between the components which can be rotated relative to each other allows a rotation angle of at least 30 ° in both directions of rotation. Rotary vibration attenuator. 20. The rotary vibration damper according to claim 1, wherein at least two energy accumulators are provided symmetrically with respect to the rotational axis of the rotary vibration damper. 21. The rotary vibration according to claim 1, wherein the rotary vibration damper is a component of a flywheel consisting of a plurality of mass bodies or forms such a component. Attenuator.