JPH08240244A - Rotational vibration damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a spring base supporting a spring sufficiently under any operating condition by connecting the spring base or an intermediate member to at least one adjacent end part area of the spring for preventing loss of the spring base. SOLUTION: In assembly of a spring 10 and a supporting member 30, an additional part 32 is pressed into a matching end part area in the spring 10, so that an end part coil 29 is expanded, and consequently, an interval or an inner width 39 is increased first of all. That is, an end part section 37 is pushed back toward the radial outside. The moment when the end part section of the coil 29 or the end part section 37 reaches the height of a groove or an integrally molded part 34, the end part coil 29 can be elastically returned. Consequently, the interval or the inner width 39 is reduced again, and the end part section 37 is radially engaged in a groove 34, that is, the end part section 37 is snapped to be connected. In this way, the supporting member 30 is held to the spring 10 so as not to be lost.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION The present invention relates to at least two rotatable elements that resist the resistance of at least one energy store.
A rotary vibration damper comprising two members, said member having a load range for compressing an energy store formed by at least one coil spring, wherein A rotary vibration damper of which at least one end is angularly shiftable or rotatable with respect to said member and is adapted to cooperate with a spring mount which serves to support the corresponding spring end. Regarding

[0002]

PRIOR ART German Patent Application Publication No. 361
A rotationally elastic clutch for damping vibrations, which is known from U.S. Pat. No. 0,127, is constructed as a two-inertia flywheel, in which case a primary inertia body, which can be connected to a drive motor, and a transmission via the clutch. A rotationally elastic member that absorbs vibration is provided between the secondary inertial body that can be coupled to the device, and these members enable relative rotation of both inertial bodies. . The rotationally elastic member is in this case formed by an energy store with a coil spring. These energy accumulators are constrained by the load range provided on the two inertial bodies when they rotate relative to each other. In this case, a cover plate that supports the coil springs may be provided between the load range and the coil springs. Further, in this known configuration, 2
In inertial flywheels a long energy store is used which is formed by a plurality of springs arranged one behind the other, i.e. in series. A conical intermediate member is provided between the springs inserted in the chamber. Other structural features of the intermediate member are not disclosed in the above specification.

German Patent Application Publication No. 3721
No. 711 and German Patent Application Publication No. 3
No. 721712 further discloses support members for supporting the end regions of long springs, which support members are provided with an add-on, which add-on When it is advanced from the end range of the corresponding spring, it is possible to re-enter the spring end range. Such a support member can certainly be used in the form of a receptacle which is substantially closed in cross section and adapted to the outer diameter of the spring, but does not fit the outer circumference of the spring. Or when used in connection with a spring receiving chamber which is substantially unclosed in cross-section, such support members may twist or snag to cause the support into the corresponding spring. The entry of the members is no longer possible, which causes the rotary inertia damper, the two inertia flywheel, to fail or even at least damage the support member and / or the spring.

[0004]

SUMMARY OF THE INVENTION The object of the invention is therefore to improve a rotary vibration damper of the type mentioned at the outset so that the spring end cooperating with the spring base is perfectly supported under all operating conditions. SUMMARY OF THE INVENTION It is an object of the present invention to provide a spring base which is capable of supporting a variety of uses and configurations of a rotary vibration damper. In this case, it is furthermore desired that a particularly simple assembly and an inexpensive production of the rotary vibration damper are possible. The configuration of the rotary vibration damper according to the invention also provides, between two relatively rotatable members, a torque characteristic line or a torsional resistance produced by an energy store or coil spring which resists the rotation of both members. It is desired that a wide variety of suitability for each use case of the characteristic line is possible. That is, in the present invention, it is desired to be able to realize an extremely soft twist resistance characteristic line having a small spring strength and / or a multi-step twist resistance characteristic line.

[0005]

In order to solve this problem, in the structure of the present invention, in the rotary vibration damper of the type described at the beginning, the spring base or the intermediate member is at least one.
It is permanently attached to the adjacent end areas of the two springs.

[0006]

With this construction, it is ensured that the spring bed always maintains the optimum position for loading the spring. The spring mount or the intermediate member has at least one integral molding for positioning and / or fixing, which integral molding, viewed in the direction of the longitudinal axis of the spring, adjoins the at least one spring. It intersects with or is covered by the end area. Advantageously, this integrally formed part is formed by a protrusion or an add-on of the intermediate member or the spring mount, and this protrusion or add-on of the chamber formed or surrounded by the corresponding spring winding. Engaged in. For fixation in at least one spring, a spring base or support member is integrally molded such that at least one end winding or end region of the spring engages from the outside to ensure fixation to the at least one spring. It may have a part or a range.

The fixing method for fixing the spring base or the supporting member for the coil spring of the rotary vibration damper according to the present invention is, in effect, a plurality of coil springs which are effective directly in series and are arranged one behind the other. It can also be used when using an energy store consisting of Such spring mounts or supporting members are preferably provided between the end regions or the end turns of the series-effective springs. This makes it possible to ensure satisfactory support between the springs arranged in series and, if necessary, to arrange the inner coil spring in at least one of the coil springs arranged in series. And
The inner coil spring may likewise be loaded via at least one spring bed which acts as an intermediate support member.

Further advantageous configurations of the rotary vibration damper according to the invention are set forth in claims 2 and below.

[0009]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will now be described with reference to the drawings.

The rotary vibration damper shown partially in FIGS. 1 and 2 has a split flywheel 1, which is fixed to a driven shaft (not shown) of the internal combustion engine. It has a first or primary inertial body 2 and a second or secondary inertial body 3. A friction clutch can be fixed to the second inertial body 3 via a clutch disc, and an input shaft (not shown) of the transmission can be connected / disconnected via the clutch disc. Inertia 2 and 3
Are rotatably supported on each other via bearings 4,
In the illustrated embodiment, this bearing 4 is arranged radially outside a hole 5 for passing a fixing screw for attaching the first inertial body 2 to a driven shaft of an internal combustion engine. Between the two inertia bodies 2 and 3 the shock absorber 6 is effective,
The shock absorber 6 has an energy store 7, at least one of which is formed by a compression coil spring 8, 9, 10. As is particularly apparent from FIG. 2, the compression coil spring 9 is housed in the chamber formed by the winding 8a of the spring 8 or, in other words, both coil springs 8 and 9 are distributed over their entire length. Located inside and outside each other. In the embodiment shown, the angular extension or length 11 of the inner coil spring 9 in the circumferential direction is shorter than the extension or length 12 of the outer coil spring 8. In this case the inner spring 9 is the outer spring 8
On the other hand, it is advantageous if the value 13 is short, which corresponds to a magnitude of 1 ° to 5 °. However, this length difference or angular difference 13 may be greater. It is also possible that both springs 8, 9 have the same length or the same angular extension. A coil spring 10 is operatively connected in series to the coil springs 8 and 9 that operate in parallel with each other. Although no inner spring is provided in the illustrated embodiment shown in FIG. 2, it may be advantageous to provide such an inner spring for some applications. If an inner spring is provided, this inner spring is housed in the spring 10 in the same manner as the inner spring 9 in the outer spring 8. Furthermore, it may be advantageous for some applications that only the outer spring 8 is provided, i.e. the inner spring 9 is omitted.

Both inertial bodies 2 and 3 have a load range 14, 15 or 16 for the energy store 7. In the illustrated embodiment, the load ranges 14 and 15 are formed by embossed portions formed on the thin metal plate members 17 and 18 forming the first inertial body 2. When viewed in the axial direction, the load range 16 provided between the load ranges 14 and 15 is
For example, it is formed by at least one flange-shaped load member 20 connected to the secondary inertial body 3 via a rivet 19. This member 20 acts as a torque transmission element between the energy store 7 and the inertial body 3. The load range 16 is formed by radial arms provided on the outer circumference of the flange-shaped load member 20. The member 13 formed by cold deformation of the thin metal plate material is
The inertial body 2 or the divided flywheel 1 as a whole is fixed to the driven shaft of the internal combustion engine. On the outside in the radial direction, the member 17 is a member 1 which is likewise manufactured from sheet metal.
Combined with 8. Both members 17 and 18 form a ring-shaped chamber 21 having an annular area 22. The ring-shaped chamber 21 or the annular region 22 is at least partially filled with a viscous medium such as grease. Between the integrally formed part or the load ranges 14 and 15 when viewed in the circumferential direction, the members 17 and 18 have the curved part 2
3 and 24 are formed, and these curved portions 23 and 24 are formed.
Limits the annular area 22 and receives the energy store 7 and guides it in radial and axial directions. At least when the flywheel 1 is rotating, the windings of the springs 8 and 10 limit the radially outer side of the annular region 22, the member 17 and / or
Or it is supported in the range of 18. In the embodiment shown, an antiwear body 25 is provided, which is formed by at least one tempered sheet metal intermediate layer or metal sheet insert, in which the springs 8 and 10 are arranged radially. Supported by. The anti-wear body 25 is circumferentially advantageously at least at the relaxed energy store 7.
Extend over the entire length or angular length of. Due to the centrifugal support of the windings of the springs 8 and 10, between the windings and the members frictionally engaged with the windings, the energy store 7 or the stores 8 and 10 are When the length is changed or compressed, frictional damping related to the number of rotations occurs.

The radially extending member 17 has a radially inner portion or boss 26 which receives or holds the inner race of the ball bearing 4. The outer race of the ball bearing 4 holds the inertial body 3.

As can be seen especially from FIG. 2, the load range 16
Is angularly smaller than the load ranges 14 and 15, so that the inertial body 2 and the inertial body 2 can be started from the theoretical rest position or the starting position shown in FIG. 3 is capable of relatively small rotation in both rotation directions.

As shown in FIG. 2, an intermediate member 30 is provided between the end windings 27, 28 and 29 of the springs 8, 9 and 10 which face each other or are adjacent to each other. The member 30 may be referred to as a spring mount or spring seat, and the end windings 27, 2 of the springs 8, 9 and 10
Serves to support 8, 29 or end areas. Figure 2
In the embodiment shown in FIG. 1, the intermediate member or spring support member 30 comprises a ring-shaped region 31 for supporting the springs 8, 9 and 10 in the circumferential direction and an additional part extending perpendicularly to the ring-shaped region 31. Alternatively, it has a protrusion 32 which extends into the hollow chamber defined by the winding 10a, i.e. in the end region of the spring 10. In the illustrated embodiment, the support member 30 is hollow and has a notch 33. As can be seen from FIG. 2, the energy accumulator 7 or the coil springs 8, 9, 10 forming the energy accumulator are in the load range 1
There are no support members or spring mounts in the end areas directed to 4, 15, 16. However, it is also possible to provide at least one of the ends of the energy store 7 with a support member or a spring mount.

The support member 30 is connected to the compression coil spring 10 so as not to be lost. For this purpose, the support member 30
There is a mating connection between the spring and the spring 10, which in the illustrated embodiment is a snap connection, as will be explained in more detail below in connection with FIGS. 3 and 4. Is configured as.

As can be seen from FIG. 3, the spring mount or support member 30 has an integrally formed or recessed portion formed by a ring-shaped groove 34, which is in the axial direction. The additional portion 32 is provided immediately adjacent to the ring-shaped range 31. Outer diameter portion 35 of additional portion 32
Corresponds to at least the inner diameter portion 36 of the spring winding 10a of the spring 10 (FIG. 4). Advantageously, the outer diameter 35 is
It is somewhat smaller than the inner diameter 36, at least in the region of the spring end directed towards the support member 30.

As can be seen in FIG. 4, the free end section 37 of the end winding 29 adjacent to the support member 30 extends radially towards the spring axis 38 and the remaining extent of the spring end winding 29. Or is bent or bent with respect to the spring winding 10a. With this configuration, an inner width 39 smaller than the inner diameter portion 36 of the end winding 29 and the winding 10a or smaller than the outer diameter portion of the additional portion 32 is generated. During the assembly of the spring 10 and the support member 30, the additional part 32 is pushed into the corresponding end region of the spring 10, so that the end winding 29 is expanded first of all, which results in a spacing or inner width 3
9 grows first. That is, the end section 37 is pushed outward in the radial direction.

The end section or end range 37 of the winding 29
As soon as the groove reaches the height of the groove or the integrally formed part 34,
The end windings 29 can elastically return, so that the distance or inner width 39 is reduced again, so that the end regions 37 engage radially in the groove 34, i.e. snap-fit. As a result, the support member 30 is held against the spring 10 so as not to be lost. The add-on portion 32 has a tapered portion 39a at its free end, and this tapered portion 39a is
It facilitates the pushing of the add-on portion 32 into the opposite end region of the spring 10. End area 37 via taper 39a
Can be pushed radially outward.

As can be seen in connection with FIG. 5, the end wrap 29 has an end area 37 that radially engages the groove 34.
Except for, the pitch or pitch angle is the same as that of the winding 10a provided between the end windings 29 of the spring 10.
The end section 37 of the spring 10, at least in the relaxed state of the spring 10, has a ring-shaped area 31 or a support member 3.
It extends parallel to the 0 support surface 31a (FIG. 3).
To this end, as can be seen in FIG. 5, the end region 37 is bent from its position 37a shown in broken lines to the position shown in solid lines, towards the longitudinal axis 38 of the spring 10.

At the end 39 of the spring 10 adjacent to the load range 14, 15, 16 the last winding is deformed in a manner known per se into the penultimate winding in the direction of the spring axis 38. Are contacted by means of which the last winding forms a load surface which extends at least approximately perpendicular to the spring axis 38. Configuring the last strip in this way is described, for example, in DE-A 42229.
No. 416 is proposed. Both coil springs 8 and 9 likewise have correspondingly chamfered end turns in both end regions thereof, so that the load range 1
A satisfactory loading of the coil springs 8, 9 by 4, 15, 16 and a satisfactory support of the coil springs 8, 9 in the ring-shaped area 31 of the intermediate member or support member 30 is ensured.

The coil springs 8 and 10 may have equal spring strength or different spring strengths. Also, the length ratio between the spring 8 or 9 and the spring 10 can be adapted to the respective use case,
In this case, this length ratio has a value between 0.5: 1 and 3: 1, preferably between 1: 1 and 2: 1.

The use of the support member 30 has the following advantages: springs having a large ratio of spring length to spring diameter can be connected in series, in which case it is always guaranteed that: . That is, a satisfactory loading of the opposite end areas of these springs is ensured and slipping or disengagement of the support member 30 from the corresponding springs is reliably avoided. This ensures that the intermediate member is always loaded satisfactorily and is not destroyed by the springs 8 and 10 due to their inclined position between the corresponding end areas.

If at least one inner spring 9 is used, this inner spring 9 can be of short design. This is because due to the tightness of the inner spring 9, it does not have to extend over at least part of the length of the spring 10.

Furthermore, the intermediate member 30 allows the use of inner springs which differ in length and / or strength.
That is, it is possible to provide at least one inner spring inside the spring 10, in which case the inner spring has the same length as the spring 10 or is shorter than the spring 10.
May be long.

For some applications, configurations such as that shown in FIG. 6 are also advantageous. In the configuration shown in FIG. 6, the intermediate member 130 has a ring-shaped support range 131 from which the additional parts 132, 132a extend in both axial directions or both circumferential directions of the flywheel 1. There is. In this configuration of the intermediate member 130, the spring 1
0 not only has a positive connection with the intermediate member, as seen in the axial direction 38 of the energy store 7, but the spring 8 also has a positive connection with the intermediate member. As a result, both springs 8 and 10 are rigidly connected to each other when viewed in the circumferential direction of the flywheel 1. In such a configuration, as compared with the configuration shown in FIG.
It must be constructed as short as the length or extension of 32a.

Furthermore, the add-on portion 132a shown in FIG. 6 may also be constructed such that the add-on portion is also fitted to the inner spring 9. If it looks like this,
At least the spring 9 is connected to the spring 10.

Further, the intermediate member 230 shown in FIG.
In the above configuration, the intermediate member is a stepped addition portion 232a.
And in this case each step is an integrally formed part or groove 2.
34 and 234a, and the end windings of the springs 208 and 209 are engaged with the integrally formed portion or groove at least in a partial area. By being configured in this way, the inner spring 209 becomes the outer spring 20.
It is possible to additionally prevent the inner spring 209 from slipping out of the outer spring 208, substantially non-slip with respect to FIG. The intermediate member 230 can also have an add-on 232 for the spring 10 shown in FIG. 2, as shown by the dashed lines in FIG. 7, which add-on 232 prevents the spring 10 from being lost. Combined with 10.
When using an inner spring located inside the spring,
The add-on part 232 can be configured correspondingly to the add-on part 232a, so that the second inner spring can also be connected to the intermediate member 230.

As shown in FIG. 8, two outer springs 308, 310 are arranged in series via a support member 330, and one inner spring 309, 309a is arranged inside each spring 308, 310. In the illustrated embodiment, the intermediate member 330 is merely hooked to the inner spring 309, i.e., is permanently coupled to the inner spring 309.

As is apparent from the above description, there are various possibilities regarding the hooking type or the fixing type of the intermediate members 30, 130, 230, 330 and the spring adjacent to the intermediate members, and In this case the intermediate member is permanently connected with at least one of these springs. However, the corresponding intermediate member may also have a connection with a plurality of springs or with all adjacent springs.

In the embodiment shown in FIG. 9, the spring mount or support member 430 coupled to the spring 409 has an add-on portion 432 with a thread-shaped integral molding 434 formed on the outer periphery. There is. End winding 409a of spring 409
Are formed so that the end windings can be screwed into the thread-shaped integrally formed portion, and the inner diameter of the end winding 409a is preferably configured as follows. That is, in this case, the end winding 409a has a radial preload (Vorspannun).
With g), it is in contact with the additional portion 432, which makes it possible to prevent the spring base or the supporting member from slipping out of the end region of the spring 409 due to rotation.

In the embodiment shown in FIG. 2, only two springs or sets of springs are connected in series. However, configurations are also possible in which three or more springs or sets of springs are connected in series, in which case the invention according to the invention is between the spring ends of the springs or sets of springs facing each other. It is possible to provide a support member according to.

As in the case of the present invention, the at least one spring-tight bearing element is not lost and can be provided in the end areas of the corresponding springs which are directed towards the load ranges 14, 15, 16. Good. For example, in the embodiment shown in FIG. 2, the springs 8 and 10 may be constructed in one piece, that is to say form only one spring, and the support member 3
A zero may be provided at the spring end 39b of the spring 10. If the springs 8 and 10 are integrally formed, the spring 8
It is possible to provide a support member configured as in FIG. 7, FIG. 8 or FIG. When the springs 8 and 10 are integrally formed,
Thus, if a continuous outer spring is used, the spring mount or support member 30 shown in FIG. 2 is dispensed with between the load ranges 14, 15, 16 belonging to the spring.

The at least one end winding of the coil spring, which is fastened to the spring bed, is seen in the longitudinal direction of the corresponding coil spring, even one winding before the last, in the longitudinal direction 3 of the spring.
It can be brought into contact by deformation towards 8. This has already been described in DE-A 42229416. In this case, it is advantageous for the end windings thus configured to have a smaller inner diameter than the remaining windings, so that the end windings have a corresponding spring mount. Can be snapped into the groove. Such a configuration of spring end turns 208a is shown in FIG. If the end region of the spring is configured in this way, a large contact surface can be obtained between the spring and the spring base during the compression of the spring, whereby the force generated by the compression of the spring is It can be distributed over a large bearing surface of the spring bed.

The energy accumulator 507 shown in FIG. 10 differs from the energy accumulator 7 shown in FIG. 2 mainly in the following points. That is, in the energy storage unit 507 shown in FIG. 10, the coil spring 509a is received inside the coil spring 510. And this spring 509a
Is rigidly connected to the spring support member 530 at least in the circumferential or axial direction 538 of the energy store 507. As in FIG. 2, the outer spring 508 and the inner spring 509 provided inside the outer spring 508 are also provided in this embodiment.
And springs 510, 5 are provided.
09a is connected in series.

The inner spring 509a has a significantly higher spring strength than the outer spring 510. The length of the inner spring 509a as viewed in the circumferential direction or in the direction of the spring longitudinal axis 538 is significantly shorter than the length of the outer spring 510.

The length or angular length of the strong inner spring 509a in the relaxed state is as follows: that is, before the inner spring 509a is contracted, that of the relatively soft outer spring 510 having a small spring strength. It is selected so that the twist angle is guaranteed.

As can be seen in FIG. 10 on the basis of the distance between two adjacent windings, the inner spring 50
9a has a smaller pitch than the outer spring 510 when viewed in the direction of the axis 538 of the energy store 507.
In the illustrated embodiment, the spring 509a is configured with respect to the spring 510 as follows. That is, in this case, when the relative rotation occurs between the two inertial bodies 2 and 3 shown in FIG. 1, the winding of the inner spring 509a is changed before the winding of the outer spring 510 becomes a block shape. It is block-shaped, which makes it possible to avoid overloading the outer spring 510.

The inner spring 509a is, however, also relative to the outer spring 510 in the following manner: at large amplitudes, which are already significantly higher than the nominal torque produced by the internal combustion engine due to the large spring strength of the inner spring 509a. The generated torque is absorbed exclusively by the inner spring 509a in a spring-elastic manner, which results in a more sensitive outer spring 5 with respect to the block load (Blockbeanspruchung).
It may be configured so that 10 only needs to receive a portion of the high torque. When the inner spring 509a sufficiently absorbs the shock of torque or absorbs it elastically, the block load of the outer spring 510 can also be performed, that is, the block load of the outer spring 510 can also be considered.

In a variation of the embodiment shown in FIG. 10, the inner spring 509a has a larger winding pitch than the outer spring 510 when viewed in the direction of the spring axis 538 of the energy store 507. Can be

In an advantageous configuration, the pitch of the turns of the inner spring 509a is opposite to the pitch of the turns of the outer spring 510. Viewed in the same axial or circumferential direction of the energy store 507, this means that the windings of one spring are wound with a corresponding pitch in the clockwise direction, while the windings of the other spring are wound. This means that the strips are wound in a counterclockwise direction with a corresponding pitch.

The angle of rotation between the two inertia bodies 2, 3 and thus the two inertia bodies 2, 3 through which the two springs 509a and 510 are connected in parallel to each other is, for example, 5 ° to 20 °. The value is °. This angle may, however, be larger depending on the application, and in extreme cases the inner spring 509a may be, for example, the spring 8,
9 may be constructed slightly shorter than the outer spring 510. However, advantageously, the inner spring 509a is preferably adapted to avoid overloading the turns of the outer spring 510 when at least one of the two springs 509a, 510 locks in a block. . The outer spring 510 has the following spring strength, that is, a spring strength that causes a torsional resistance of 0.5 to 4 Nm / ° between the relatively rotatable components 2 and 3. Can be Spring 509a
The twisting resistance generated by, for example, 20 to 8
It is a value of 0 Nm / °. However, this value may also be larger or smaller. However, the inner spring 5
09a is 20 to 50 between both constitutional groups 2 and 3.
It is advantageous to have a spring strength which gives rise to torsional resistances of the value Nm / °.

Spring 50 connected in series with spring 510
8 can have the same spring strength as spring 510 or less spring strength than spring 510, but advantageously has a greater spring strength than spring 510. Spring 5
The spring strength of 09 may also be the same as, or greater than or less than that of spring 508.

In the energy storage device 507 shown in FIG. 10, springs 509a and 510 arranged coaxially with each other.
Are springs 508, 50 which are likewise arranged coaxially to one another.
9 is connected in series. Springs 509a and 510
The mode of operation described in connection with it can, however, also be used for an energy store consisting of two springs which are arranged coaxially with respect to each other and with respect to each other. This means the following. That is, in FIG. 10, the coil spring 510
If it extends over the entire length of the energy store 507, the inner spring 509a must be adapted accordingly in its length and spring characteristics. That is, in such an energy store, the outer spring is the length of the spring 510 and the spring 5
It will have an angular extension or length corresponding to the sum of the length of 08 and the length of the intermediate member 530.
In such a case, the spring 509a must likewise be made longer.

In the illustrated embodiment described above, only two springs are provided, which are arranged respectively inside and outside each other. For some applications, however, it may be advantageous to provide three or possibly four springs arranged in and out of one another. In this case, these springs are preferably fixed to one another in the circumferential direction, as already mentioned. For example, the spring 409 shown in FIG.
It is possible to provide another spring inside the housing, in which case this further spring can be received in another additional part connected to the additional part 432 of the spring mount 430. This additional addendum can be configured, for example, similar to the addendum for the spring 209 shown in FIG.

The structure according to the present invention has the following advantages. That is, with the structure of the present invention, as described above, the support member or the spring base is prevented from slipping off from the spring end portion assigned to the support member or the spring base, and as a result, the spring is always properly operated. Load is ensured and, if the springs are arranged in series, a satisfactory mutual support of the springs is ensured. The slipping-off of the support member can occur especially when using long springs with a relatively large diameter and a relatively small spring strength. This is because the centrifugal force acting on the spring during rotation of the flywheel 1, as described, for example, in DE-A 37 21 711 and DE-A 37 21 712, After compression of the spring, for example due to a load shock, the spring cannot at least completely relax due to the high friction between the spring and the area supporting it. The resulting spring is
This is because it will have a shortened length with respect to the fully relaxed state. If the support member is not fixed as in the present invention, the support member may slip out of the end region of the corresponding spring and swivel or rotate in the chamber 21 or the annular chamber 22. In this case, it is not guaranteed that the additional part of the intermediate member will always enter the associated spring or the corresponding spring end at the time of a new tightening or loading of the spring, so that the intermediate member is destroyed. There is.

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a rotary vibration damper according to the present invention.

FIG. 2 shows a rotary vibration damper according to the present invention as II-I in FIG.
It is a figure which shows a cross section and a partial view along line I.

FIG. 3 is a cross-sectional view showing an embodiment of a spring base.

4 is a front view showing a spring end of a coil spring assigned to the spring base shown in FIG.

5 is a side view showing a spring end portion shown in FIG. 4. FIG.

FIG. 6 is a cross-sectional view showing another embodiment of a spring stand.

FIG. 7 is a sectional view showing a spring base and associated coil springs according to another embodiment.

FIG. 8 is a sectional view showing a spring base and associated coil springs according to still another embodiment.

9 is a sectional view showing a modified embodiment of the spring base shown in FIG. 8 and a coil spring belonging to the spring base.

FIG. 10 is a diagram showing an energy accumulator including a plurality of coil springs.

[Explanation of symbols] 1 flywheel, 2 primary inertial body, 3 secondary inertial body,
4 bearings, 5 holes, 6 shock absorbers, 7,507
Energy storage device, 8, 9, 10, 208, 209, 3
08,309,310,409,508,509a, 5
10, coil spring, 8a winding, 11, 12 length, 13 values, 14, 15, 16 load range, 1
7,18 Metal thin plate member, 19 Rivets, 20
Load member, 21 ring-shaped chamber, 22 annular range, 23, 24 curved portion, 25 anti-wear body, 26
Boss, 27, 28, 29 End winding, 30, 13
0,230,330,430,530 Intermediate member (supporting member), 31 Ring-shaped range, 32,132,1
32a, 232, 432 Projection part (additional part), 33 Notch, 34, 434 Groove (integrally molded part), 35 outer diameter part, 36 inner diameter part, 37 end section, 38, 53
8 spring axis line, 39 inner width, 234, 234a groove

Front Page Continuation (72) Inventor Johann Jeckel Germany Baden-Baden Sponheimer Strasse 10 (72) Inventor Arlbert Birck Germany Buhl-Wimbuch am Iceweier 1

Claims (26)

[Claims] 1. A rotary vibration damper comprising at least two members rotatable against the resistance of at least one energy store, said members being formed by at least one coil spring. A load range for tightening the force device, at least one of the ends of the coil spring being angularly rotatable with respect to said member and supporting a corresponding spring end Of a type adapted to co-operate with a spring bed which serves to form a support area for the adjacent spring end windings and to be joined with the end area so as not to be lost. Rotational vibration damper characterized by being 2. The rotary vibration damper as claimed in claim 1, wherein the spring mount has a one-piece molding which, when viewed in the direction of the longitudinal axis of the spring, intersects the adjacent end regions of the spring. 3. The spring base is fixedly connected to the coil spring via a shape connection so as not to be lost.
The described rotational vibration damper. 4. The shape-coupling portion is provided between the spring base and at least the end winding of the coil spring adjacent to the spring base, and the shape coupling portion is provided. Rotational vibration damper. 5. A snap-fitting portion having a form-fitting connection is provided between the spring base and the coil spring.
The rotary vibration damper according to any one of items 1 to 7. 6. The rotary vibration damper according to claim 1, wherein a coupling portion for preventing loss is provided between the coil spring and the integrally molded portion of the spring base. 7. The spring base has a ring-shaped area which serves to support adjacent spring end turns, from which point the spring inner chamber is limited by the corresponding spring turns. An extension extending through, and between the addition and at least one section of spring winding,
Holding that prevents the spring base from being lost against the spring,
The rotary vibration damper according to any one of claims 1 to 6. 8. A rotary vibration damper according to claim 1, wherein the free end section of the spring winding adjacent to the spring base serves for holding the spring base against the spring. 9. Spring according to claim 1, wherein the spring mount has a radial groove in which at least one section of the spring winding is form-lockingly engageable. The rotary vibration damper according to item 1. 10. The free end range of the end turns of the spring is
Rotational vibration damper according to any one of the preceding claims, which radially engages a groove of a spring bed assigned to the end region. 11. In the relaxed state of the coil spring, the end windings adjacent to the spring base are provided between the end windings except for the end region engaging with the groove of the spring base. The rotary vibration damper according to claim 9 or 10, having the same pitch angle as that of. 12. The end section of the corresponding end winding extends parallel to the bearing surface of the spring mount for the coil spring, at least in the relaxed state of the coil spring. The rotary vibration damper according to claim 1. 13. The end area of the end turns of the coil spring adjacent to the spring base is offset radially with respect to the other turns toward the longitudinal axis of the coil spring. The rotary vibration damper according to any one of 1 to 12. 14. An energy store is formed by at least one outer coil spring and at least one inner spring received in a hollow space defined by the windings of the outer spring, the energy store comprising: At least one of a force machine
14. A rotary vibration according to any one of claims 1 to 13, wherein a spring base is provided at one end, and the spring base has a coupling part for preventing loss with the outer spring. damper. 15. An energy store is formed by at least one outer coil spring and at least one inner spring received in a hollow space defined by the windings of the outer spring, the energy store comprising: At least one of a force machine
15. Rotational vibration according to any one of claims 1 to 14, characterized in that a spring base is provided at one end, the spring base having a connection to prevent loss with the inner spring. damper. 16. An energy store is formed by at least one outer coil spring and at least one inner spring received in a hollow chamber defined by the windings of the outer spring, the energy store comprising: At least one of a force machine
16. A spring bed is provided at one end, the spring bed having a connection preventing loss between the outer spring and the inner spring. Rotational vibration damper. 17. The energy store is formed by at least two coil springs arranged in series between the load ranges of the relatively rotatable members, the coil springs facing each other. 2. A spring base is provided between the ranges, the spring base being held against the at least one coil spring in a secure manner.
The rotary vibration damper according to any one of 6 to 6. 18. At least one of both springs forms an outer spring, the outer spring receiving an inner spring, the inner spring extending over at least a partial range of the length of the outer spring. The rotary vibration damper according to claim 17, wherein 19. At least one spring pair formed by an outer spring and an inner spring is provided, the inner spring being constructed shorter than the outer spring.
The rotary vibration damper according to any one of claims 1 to 18. 20. At least one spring pair formed by one outer spring and one inner spring is provided, both springs having the same length. The rotary vibration damper according to any one of claims 1. 21. An energy store is formed by at least two springs arranged in series between the load ranges of the relatively rotatable member, the load range of the member and the energy store. Between the adjacent spring ends of the vessel,
21. The spring bed is not provided, and the spring bed is provided between the facing end areas of the springs connected in series with one another.
The rotary vibration damper described in the item. 22. Rotational vibration according to claim 1, wherein at least one of the coil springs forming the energy store has a precurved shape in the relaxed state. damper. 23. The rotary vibration damper according to claim 1, wherein the energy accumulator formed by a coil spring has a large length / outer diameter ratio. 24. Between the relatively rotatable members,
24. A rotary vibration damper as claimed in any one of claims 1 to 23, in which at most three energy stores arranged in the same diameter range are provided. 25. An energy store allows a rotation angle of at least 30 ° in both directions of rotation between the relatively rotatable members between which the energy store is located. The rotary vibration damper according to any one of claims 1 to 24. 26. The rotary vibration damper is a component of a flywheel comprising a plurality of inertial bodies or forms the flywheel itself.
The rotary vibration damper described in the item.