ITMI960196A1 - DAMPER OF TORSIONAL OSCILLATIONS WITH AT LEAST TWO ROTATING COMPONENTS OVERCOMING THE RESISTANCE OF AT LEAST ONE ACCUMULATOR OF - Google Patents

Abstract

A torsional oscillation damper with at least two rotating components is described, overcoming the resistances of at least one energy accumulator.

Description

DESCRIPTION

The invention relates to a torsional oscillation damper with at least two rotatable components, overcoming the resistance of at least one energy accumulator, which have stress zones for the compression of the energy accumulator formed by at least one helical spring, where the helical spring with at least one of its two ends it interacts with an angularly displaceable spring base or rotatable with respect to both components and which serves to support the corresponding spring end.

From the patent publication DE-OS 3610127, an oscillation damping clutch, elastic with rotation, has become known, which is performed as a two-mass flywheel, where between the primary flywheel mass, connectable to a drive motor, and the secondary flywheel mass, connectable with the transmission by means of a clutch, elastic elements in rotation are interposed, respectively damping the vibrations, which make possible a relative rotation between the two flywheel masses. The rotating elastic elements are formed in this case by energy accumulators which have helical springs. These energy accumulators, in the event of a relative rotation between the two flywheel masses, are compressed by means of the stress zones provided on them. In this case, cover plates can be provided between the stress zones and the helical springs, on which the respective helical spring is supported. Furthermore, it has been proposed by means of this publication to use long force accumulators in a so-called mass flywheel, which consist of springs arranged one behind the other or in series in a chamber. Wedge-shaped intermediate pieces are provided between the springs inserted in a chamber. Further design features regarding the intermediate pieces are not to be noted from this publication.

From the patent publications DE-OS 3721711 and DE-OS 3721712, elastic cups or support pieces for the end areas of long springs have also become known, which have a shoulder, which is made in such a way that this, even in the case of a coming out of the end zone of the corresponding spring, it can be inserted again in this end zone. In fact, similar elastic cups can be used in the case of housings substantially closed in cross section respectively adapted to the external diameter of the springs, in the case of use in connection with spring housing chambers, which are not adapted to the external perimeter of the springs and / or not are substantially closed in cross-section, but even similar elastic cups can rotate or lock in such a way that their insertion into the corresponding springs can no longer take place, so that the function of the damper or the two-mass flywheel is at least disturbed or even occurs destruction of at least the elastic cups and / or springs.

At the base of the present invention there is the task of realizing elastic cups or a spring base which makes possible a perfect support of the ends of springs interacting with it in all the operating conditions that arise and which can also be used in the most disparate cases of use and constructive executions of torsional oscillation dampers. In addition, it must be ensured that particularly simple assembly as well as economical manufacture of torsional vibration dampers is possible. The embodiment of a torsional oscillation damper according to the invention must also make possible a plurality of variation possibilities or adaptation possibilities to the respective case of use of the torque characteristic curve or resistance characteristic curve to rotation, present between the two components rotatable relative to each other, which is generated by the energy accumulator, which opposes a rotation of the two elements, respectively by helical springs. Therefore, both very gentle resistance to rotation characteristics curves, having therefore a reduced index and / or multistage resistance to rotation characteristics, must be achievable.

According to the invention, this is achieved by the fact that the spring base according to the invention or the intermediate piece according to the invention is connected in a non-losing way with the neighboring end region of at least one spring. By this it can be ensured that the spring base always maintains an optimum position for the spring stress. The spring base or the intermediate piece may have, for positioning and / or for securing, at least one part conformed with it or forming, which - considered in the direction of the longitudinal axis of the spring - intersects respectively overlaps the area end of the at least one spring. Advantageously, the molding can be formed by a projection or a shoulder of the spring base or of the intermediate piece, which engages in the formed space or is surrounded by the corresponding spring coils. With the fixing on at least one spring, the bases or the supporting components can have formations or zones, which extend from the outside at least on an end coil or on the end zone of a spring and ensure a fixing with respect to at least one spring .

The fastening according to the invention of spring shoes or support components for helical springs of torsional oscillation dampers can be used particularly advantageously when energy accumulators are used, which consist of several helical springs acting in series and provided practically directly one after the other. Such spring bases or supporting components can be advantageously provided between the end regions or end turns facing each other of the springs acting in series. This ensures perfect support between the springs connected in series and, if necessary, in addition, in at least one of the helical springs connected in series, an internal helical spring can be arranged, which can also be stressed by means of the at least one base. effective as a component of intermediate support.

Further advantageous possibilities of designing, arranging and fixing spring shoes or intermediate supporting components according to the invention as well as helical spring arrangements are indicated in claims 2 to 23.

Further characteristics and advantages of the invention result from the following description of the figures. In this case:

Figure 1 shows a section of a damping device according to the invention,

Figure 2 shows a section partially represented along the lines II / II of Figure 1,

Figure 3 shows a section of a spring base,

figure 4 shows the end of a spring, associated with the base according to figure 3, in view,

figure 5 shows a view according to the arrow V of figure 4,

Figures 6 to 9 show further possibilities of producing spring bases according to the invention, respectively further possibilities of arranging helical springs, interacting with corresponding spring bases, and

Figure 10 shows an energy accumulator consisting of several helical springs.

The torsional oscillation damper, partially shown in Figures 1 and 2, has a split flywheel 1, which has a first flywheel mass or primary flywheel 2, which can be fixed on a drive shaft, not shown, of a heat engine, as well as a second flywheel mass or secondary flywheel 3. On the second flywheel mass 3 a friction clutch with interposition of a friction disc can be fixed, by means of which an input shaft of a transmission, also not shown, can be engaged and disengaged. The flywheel masses 2 and 3 are rotatably supported relative to each other by means of a support 4, which in the embodiment example and shown is arranged radially outside the holes 5 for the passage of fastening screws for mounting the first mass. flywheel 2 on the drive shaft of a heat engine. Between the two flywheel masses 2 and 3 a damping device 6 is effective, which comprises energy accumulators 7, of which at least one is formed by helical compression springs 8, 9, 10. As can be seen in particular from Figure 2, the helical compression spring 9 is housed in the space formed by the coils 8a of the spring 8, or in other words, the two helical springs 8 and 9 are boxed into each other, considered on their longitudinal extension. In the exemplary embodiment shown, the extension respectively angular length 11, considered in the peripheral direction of the internal helical spring 9, is smaller than the extension 13 of the external helical spring 8. In this case it may be appropriate for the internal spring 9 to be shorter by one measure 13 than the external spring 8, which is of the order of magnitude between 1 and 5 angular degrees. However, the differential length or the differential angle 13 can also be greater. Furthermore, the springs 8, 9 can have the same length or the same angular section. The helical spring 10 is operatively connected in series with the two helical springs 8, 9 acting in parallel. Even if no internal spring is provided in the embodiment shown according to Figure 2, for some application cases such an internal spring could be of advantage. This is then housed in a similar way in the spring 10 as the internal spring 9 in the external spring 8. Furthermore, for some application cases it may be suitable if only the external spring 8 is provided, therefore the internal spring 9 is missing.

The two flywheel masses 2 and 3 have stress zones 14, 15 respectively 16 for the energy accumulators 7. In the embodiment shown, the stress zones 14, 15 are formed by coining made in the sheet metal parts 17, 18, which form the first flywheel mass 2. The stress zones 16, axially provided between the stress zones 14, 15, are formed by at least one stress component 20 connected to the flange no 'with the secondary flywheel mass 3, for example by means of rivets 19. This component 20 serves as a torque transmission element between the energy accumulators 7 and the flywheel mass 3. The stress zones 16 are formed by arms respectively radial arms 16, provided on the outer perimeter of the stress means 20 a as a flange. The component 13, manufactured by cold deformation of sheet metal material, serves to fasten the first flywheel mass 2 or the entire flywheel 1 divided on the drive shaft of a heat engine. The component 17 is radially externally connected with the component 18, which is also made of sheet metal. The two components 17 and 18 form an annular space 21, which has a torus-like area 22. The annular space 21 or the torus-like zone 22 is at least partially filled with a viscous medium, such as for example grease. Considered in the perimeter direction between the moldings respectively the stress zones 14, 15, the components 17, 18 form recesses 23, 24, which delimit the zone 22 like a torus and house the energy accumulator 7 as well as guide it both in the direction radial and also in the axial direction. At least in the case of a rotating device 1, the coils of the springs 8 and 10 are supported on the area of the component 17 and / or 18, radially delimiting the area 22 externally as a torus. In the illustrated embodiment example, a wear protection 25 is provided, consisting of at least one intermediate layer of hardened sheet metal or a sheet metal insert, on which the springs 8 and 10 are radially supported. The wear protection 25 extends in perimeter direction advantageously at least over the entire length or angular extension of the discharged energy accumulators 7. As a consequence of the support according to the centrifugal force of the coils of the springs 8 and 10, between these coils and the components, which are in frictional engagement therewith, a speed-dependent friction damping is generated in the event of a change in length, respectively. compression of the energy accumulators 7 of the force accumulators 8 and 10 respectively.

Radially internally, the radially extending component 17 carries an intermediate part respectively a hub 26, which houses respectively carries the inner bearing ring of the ball bearing 4. The outer bearing ring of the ball bearing 4 carries the flywheel 3.

As can be seen in particular from Figure 1, the stress zones 16 from the angular point of view are made smaller than the stress zones 14, 15, so that starting from the rest position or the theoretical starting position, represented in Figure 2, is a small rotation in both directions of rotation of the flywheel masses 2 and 3 with respect to each other is possible without spring effect. A piece is provided between the end coils 27, 28 facing each other respectively close, on one side, and 29, on the other side, of the springs 8, 9 and 10, as can be seen from Figure 2, a piece is provided intermediate 30, which can be referred to as the spring base or spring seat and serves to support the end coils 27, 28, 29 respectively of the end areas of the springs 8, 9 and 10. In the example of embodiment shown in the figure 2, the intermediate piece or the spring support piece 30 has an annular-shaped area 31, on which the springs 8, 9 and 10 are supported in the perimeter direction, as well as a shoulder respectively a protrusion 32, extending perpendicularly to the area 31 of annular shape, which extends into the cavity delimited by the coils 10a, that is, in the first end region of the spring 10. In the embodiment shown, the supporting component 30 is hollow, therefore it has a recess a 33. As can be seen from Figure 2, the energy accumulators 7 respectively the helical springs 8, 9, 10 that form them, at their end areas facing the stress areas 14, 15, 16 do not have supporting components or sockets of spring. However, at least at one of the ends of the energy accumulators 7 a support component or a spring base could be provided.

The support component 30 is permanently connected to the helical compression spring 10. For this purpose, a form coupling is present between the support component 30 and the spring 10, which in the case of the embodiment shown, as will be described even more in detail in relation to Figures 3 and 4, is performed as a snap connection.

As can be seen from Figure 3, the spring base or the support component 30 has a molding or recess formed by an annular-shaped groove 34, which is provided in the axial shoulder 32, immediately adjacent to the annular-shaped area 31. The outer diameter 35 of the shoulder 32 corresponds at least approximately to the inner diameter 36 of the spring coils 10a of the spring 10 (Figure 4). Preferably, the external diameter 35 is somewhat smaller than the internal diameter 36, which is present at least in the region of the spring end facing the support component 30.

As can be seen from Figure 4, the free end section 37 of the end coil 29, close to the support component 30, is offset respectively bent radially towards the spring axis 38 with respect to the remaining areas of the spring end coil 29 respectively with respect to the coils of spring 10a. With this, a free width 39 is obtained, which is smaller than the internal diameter 36 of the end coil 29 and the coils 10a respectively than the external diameter 35 of the shoulder 32. When assembling the spring 10 and the support component 30, the shoulder 32 it is inserted in the end region of the corresponding spring 10, whereby first of all the end turn 29 is widened, so that the distance 29 first of all becomes greater. Then the end section 37 is moved or pushed radially outward.

As soon as the end section or the end region 37 of the turn 29 reaches the height of the groove respectively of the molding 34, the end turn 29 can spring back, so that then the distance 29 becomes smaller again and therefore the end area 37 engages respectively snaps radially into the groove 34, so that the support component 30 is held in a non-losing way with respect to the spring 10. The shoulder 32 has at its free end a taper or a chamfer 39a, which facilitates the forced insertion respectively the compression of this shoulder 32 in the end region of the spring 10 facing it. The end region 37 can be displaced radially outwards by means of the tapering 39a.

As can be seen in connection with Figure 5, the end turn 29, apart from the end region 37 engaging radially in the groove 34, has the same inclination or the same turn angle as the turns 10a, provided between the end turns of the spring 10. The end section 37 of the spring 10 extends, at least in the unloaded state of the spring 10, parallel to the supporting surface 31a (Figure 3) of the annular-shaped zone 31 respectively of the supporting component 30. For this purpose the zone end 37, as can be seen from Figure 5, from the position 37a shown in dashed line it is folded into the solid line position of the end region 37 in the direction of the longitudinal axis 38 of the spring 10.

At its end 39b, close to the stress zones 14, 15, 16, of the spring 10, the last coil - in a per se known manner - is applied and ground on the penultimate coil by deformation in the direction of the spring axis 38, so that it forms a stress surface extending at least approximately perpendicular to the spring axis 38. A similar embodiment of the end coil has been proposed for example by DE-OS 4229416. The two coil springs 8 and 9 possess on their two end regions also a correspondingly flattened end turn, so that perfect loading of these springs is ensured by the stressing regions 14, 15, 16 as well as perfect support of these springs 8, 9 on the annular-shaped regions 31 of the workpiece intermediate respectively of the support component 30.

The helical springs 8 and 10 can have the same spring stiffness or different spring stiffnesses. Furthermore, the length ratio between the springs 8 respectively 9 and the spring 10 is to be adapted to the respective case of use, where this length ratio can be of the order of magnitude between 0.5: 1 and 3: 1, preferably of order of magnitude between 1: 1 and 2: 1.

The use of a support component 30 has the following advantages: - springs with a large ratio between spring length and spring diameter can be connected in series, where it is always ensured that perfect stress occurs on the facing end areas of these springs and furthermore an escape or a detachment of the support component 30 from the corresponding spring is prevented. The intermediate piece is therefore always stressed perfectly and, as a consequence of an oblique position between the corresponding end regions of the springs 8, 10, cannot be destroyed by them.

If at least one internal spring 9 is used, this can be made shorter, since for its compression this does not necessarily have to extend over at least a partial length of the overall length of the spring 10.

- Furthermore, the intermediate piece 30 makes it possible to use internal springs different in length and / or in stiffness. Therefore, also within the spring 10 at least one internal spring can be provided, where this can have the same length as the spring 10 or can be shorter or longer.

In some application cases it can also be advantageous when, as shown in Figure 6, the intermediate piece 130 has an annular support area 131, from which a shoulder 132 starts in both axial directions or perimeter directions of the device 1, 132a. In the case of such an embodiment of the intermediate piece 130, not only the spring 10 - viewed in the axial direction 38 of an energy storage 7 - can have a fixed connection with the intermediate piece, but also the spring 8, so that both springs 8 and 10 - considered in the perimeter direction of device 1 - are coupled together in a fixed manner. In the case of such an embodiment, with respect to the embodiment shown in Figure 2, the internal spring 9 must be performed shorter at least than the length or the extension of the shoulder 132a.

Furthermore, the shoulder 132a according to Figure 6 can also be made in such a way that it is also adapted to the internal spring 9, so that at least the spring 9 is then connected to the spring 10.

Moreover, as shown in Figure 7, the intermediate piece 230 can also be made in such a way that it has a stepped shoulder 232a, where each step has a groove respectively 234, 234a, into which the respective end turn of the springs 208, 209 at least with a partial zone. Thanks to such an execution, it is also obtained that the internal spring 209 with respect to the external spring 208 practically cannot slip or the internal spring 209 does not slip out of the external spring 208. The intermediate piece 230, as indicated by dashed line in figure 7, can also have for the spring 10 according to Figure 2, a shoulder 232, which is connected in a non-losing way to the spring 10. When using an internal spring, arranged within the spring, the shoulder 232 can also be formed corresponding to the shoulder 232a, so that then also the second internal spring is connected with the intermediate piece 230.

In the exemplary embodiment shown in Figure 8, in which two external springs 308, 310 are connected in series with the interposition of the support component 330, and an internal spring 309, 109a is respectively provided, arranged within the springs 308, 310, the intermediate piece 330 is hung only in the internal spring 309 respectively it is connected in a non-losing way with the internal spring 309.

A plurality of variations is therefore possible with regard to the coupling or fixing of an intermediate piece 30, 130, 230, 330 with the springs close to this intermediate piece, where the intermediate piece is connected in a non-losing way with at least one of these springs. . However, the corresponding intermediate piece can also have a connection with several springs or even with all these neighboring springs.

In the embodiment according to Figure 9, the spring base 430, connected with a spring 409, has a shoulder 432 with a thread-like molding 434, applied on the outer perimeter. The end coils 409a of the spring 409 are wound in such a way that they can be screwed onto the forming 434 as a thread, where advantageously the end coils 409a with respect to their internal diameter are arranged in such a way that these rest with radial preload on shoulder 432, whereby unscrewing of the spring base or of the support component from the end region of the spring 409 can be avoided.

In the embodiment shown according to FIG. 2, only two springs or groups of springs are connected in series. However, three or more springs or groups of springs can also be connected in series, where between the ends of the springs or groups of springs, opposite each other, a support component according to the invention can be provided respectively.

The supporting components, provided according to the invention so that they cannot be lost at least one end of the spring, can also be provided at the end areas, facing the stress areas 14, 15, 16, of the corresponding springs. Thus for example in Figure 2 the springs 8 and 10 could be made in one piece, thus forming a single spring, and the support component 30 could be provided at the end of the spring 39b of the spring 10. In the case of an execution in a single piece of the springs 8 and 10, also in the end zone 39a of the spring 8 could also be provided on a support component made according to figures 7, 8 or 9. In case of execution of a single piece of the springs 8 and 10 , therefore, in case of use of a continuous external spring between the stress zones 14, 15, 16 associated with this spring, the spring base or the support component 30, shown in Figure 2, is missing.

At least one end coil, anchored with the spring base, of a helical spring - considered in the longitudinal direction of the corresponding helical spring - can also be applied and ground on the penultimate coil by deformation in the direction of the longitudinal axis of the spring 38. For this purpose, reference has already been made to the patent publication DE-OS 4229416. Advantageously, an end turn made in this way has, compared to the remaining turns, a smaller internal diameter, so that it can snap into a groove of the corresponding base. A similar design of an end coil of spring 208a is shown in figure 7. Thanks to a similar design of the end region of a spring it is ensured that in the event of compression of the spring between it and the base there is a greater bearing surface. , so that the force generated as a result of a compression of the spring can be distributed over a larger supporting surface of the base.

The energy accumulator 507, shown in Figure 10, differs from the energy accumulator 7 according to Figure 2 substantially in that a helical spring 509a is housed within the helical spring 510. The spring 509a is fixedly connected with the spring support part 530 at least in the peripheral direction respectively in the axial direction 538 of the energy accumulator 507.

Similarly as in Figure 2, there are an external spring 508 and an internal spring 509 provided therein, which are connected in series with the springs 510, 509a.

The inner spring 509a has a substantially higher stiffness than the outer spring 510. Also the length of the internal spring 509a, considered in the perimeter direction respectively in the direction of the longitudinal axis of the spring 538, is substantially shorter than that of the external spring 510.

The length respectively angular section of the untensioned rigid inner spring 509a is chosen such that a sufficient torsion angle of the more compliant outer spring 510, hence having a lower spring stiffness, is ensured before the inner spring 509a is compressed.

As can be seen from Figure 10, due to the distance between two neighboring coils, the internal spring 509a, considered in the direction of the axis 538 of the energy accumulator 507, has a smaller pitch than the external spring 510. In the exemplary embodiment shown , the spring 509a with respect to the spring 510 is made in such a way that, in the event of a torsion between the two flywheel masses 2, 3 according to Figure 1, the coils of the internal spring 509a go into block, before the coils of the external spring 510 can go into lockout, so that overstressing of the external spring 510 can be avoided.

However, the inner spring 509a can also be arranged in relation to the spring 510 in such a way that, already due to the high stiffness or the high stiffness index of the inner spring 509a, the torque generated in the event of large oscillation amplitudes, which can be substantially higher than the nominal torque delivered by the heat engine, is absorbed mainly elastically by the internal spring 509a, so that the external spring 510, which is more sensitive with regard to the locking stress, must absorb only a part of this torque. If the internal spring 509a damps or resiliently absorbs the shocks of the twisting moment to a sufficient degree, a blocking stress of the external spring 510 can occur or can also be considered.

As a modification of the embodiment shown in Figure 10, the internal spring 509a, considered in the axial direction 538 of the energy accumulator 507, can also have a greater inclination of the coils than the external spring 510.

It is advantageous if the inclination of the coils of the internal spring 509a is directed opposite to that of the coils of the external spring 510. Considered in the same axial direction or perimeter of the energy accumulator 507, this therefore means that the coils of the first spring are wound clockwise with a corresponding pitch, while the coils of the other spring are wound counterclockwise with a corresponding pitch.

The angle of torsion between the two flywheel masses 2, 3 by which the two springs 509a and 510 are connected in parallel can be of the order of magnitude between 5 and 20 ". This angle, however, depending on the application , it can be even greater and in extreme cases the internal spring 509a can be even only slightly shorter than the external spring 510, as for example in the case in figure 2 for the springs 8, 9. Preferably, however, the internal spring 509a must avoid overstressing of the coils of the external spring 510 with the blocking of at least one of the two springs 509a, 510. The external spring 510 can have a stiffness index such as to generate, between the constructive groups 2, 3 rotatable each other with respect to the other, a resistance to torsion which is of the order of magnitude from 0.5 to 4 Nm / *. The resistance to torsion generated by the spring 509a can be of the order of magnitude between 20 and 80 Nm /. These values can however be even minor or major however, the internal spring 509a will have a stiffness, which between the two constructive groups 2,3 generates a resistance to torsion of the order of magnitude from 20 to 50 Nm / *.

The spring 508, connected in series with the spring 510, can have a stiffness that is equal to, less than or preferably greater than that of the spring 510. The stiffness of the spring 509 can in turn be the same, greater or less than that of the spring 508. .

In the case of the energy accumulator 507, represented in figure 10, the springs 509a, 510, arranged coaxially with respect to each other, are connected in series with the springs 508, 509, also arranged coaxially with respect to each other. to the other. The operation described in relation to the springs 509a and 510 can, however, also be used for energy accumulators which consist only of two springs arranged coaxially and boxed into each other. This therefore means that in FIG. 10 the helical spring 510 would extend over the entire length of the energy accumulator 507, wherein the internal spring 509a with respect to its length and spring characteristics must then be adapted accordingly. In the case of such an energy accumulator, therefore, the external spring would have an angular extension respectively a length which would correspond to the sum of the extensions of the spring 510, of the spring 508 and of the intermediate piece 530. The spring 509a must therefore also be made longer. .

In the embodiment examples shown, only two box springs are provided in each other. For some application cases, however, it may be advantageous for three or possibly even four box springs to be present in each other, where these springs are advantageously secured relative to each other in the perimeter direction, as already described. Thus, for example, a further spring could be provided within the spring 409 according to FIG. 9, which can be accommodated on a further shoulder joining the shoulder 432 of the spring base 430. This additional shoulder can be carried out, for example, in a similar manner to the shoulder of the spring 209 according to figure 7.

The embodiment according to the invention has the advantage that, as mentioned, the supporting components or the spring shoes cannot slide out of the respective spring ends associated with them, so that perfect stress of the springs is always ensured and, in case of series arrangement of springs, also a perfect mortgage spring support. Such slipping or slipping of the support components can occur in particular when using long springs with a correspondingly large diameter and a relatively low stiffness index, since, as described for example in the patent publications DE-OS 3721 71 1 and DE -OS 37 21 712, in the case of a rotating device 1, the centrifugal force acting on the springs can become so great that after a compression of the springs, for example as a result of a load impact, these, as a consequence of the high friction present between the coils of the spring and the areas which support them, at least can no longer be completely unloaded, so that they have a shortened length with respect to the completely unloaded state. Without the belaying according to the invention of the support components, these could fall out or slide out of the end zone of the spring respectively of the corresponding springs, and could orient themselves respectively in the chambers 21 respectively in the space 22 like a torus. . In the case of a new compression or stress of the corresponding springs then it is not always ensured that the shoulder or the shoulders of the intermediate pieces can be inserted into the associated springs or into the corresponding spring ends, whereby a destruction of the intermediate pieces can take place.

The patent claims filed with the application are proposed for formulation without prejudice to obtaining further patent protection. The Applicant reserves the right to claim still further characteristics, published so far only in the description and / or in the drawings.

References used in sub-claims refer to the further implementation of the subject matter of the main claim by means of the characteristics of the respective sub-claim; they are not to be understood as a renunciation of obtaining autonomous, objective protection for the characteristics of the sub-claims.

However, the objects of these sub-claims also form autonomous inventions, which also have a configuration independent of the objects of the previous sub-claims.

Furthermore, the invention is not limited to the exemplary embodiments of the description. On the other hand, numerous variants and modifications are possible within the scope of the invention, in particular those elements, variants and combinations and / or materials, which for example by combining or modifying individual characteristics or elements or process steps, described in connection with the description general and the embodiments as well as the claims, are inventive and by means of combinable characteristics lead to a new object and to new process steps or sequences of process steps, also with regard to manufacturing, testing and working processes.

Claims (26)

CLAIMS 1. Torsional oscillation damper with at least two rotating components overcoming the resistance of at least one energy accumulator, which possess stress zones for the compression of the energy accumulator formed by at least one helical spring, where the helical spring with at least one of its two ends interacts with a spring socket, angularly rotatable with respect to both components and which serves to support the corresponding spring end, which socket forms a support zone for the neighboring spring end coil and is connected so not lost with the extremity zone. 2. Torsional oscillation damper according to claim 1, characterized in that the spring base has a molding which - considered in the direction of the longitudinal axis of the spring - intersects the neighboring end region of the spring. Torsional oscillation damper according to claim 1 or 2, characterized in that the base is permanently connected to the coil spring by means of a form coupling. Torsional oscillation damper according to one of claims 1 to 3, characterized in that a shape fit is present between the base and at least the near end turn of the helical spring. Torsional vibration damper according to one of claims 1 to 4, characterized in that there is a form-fitting snap connection between the base and the coil spring. 6. Torsional oscillation damper according to one of claims 1 to 5, characterized in that there is a non-losing connection between the helical spring and the base molding. 7. Torsional oscillation damper according to one of claims 1 to 6, characterized in that the base has an annular-shaped area, which serves to support the nearby spring end coil, from which a shoulder extends into the internal space of spring delimited by the coils of the corresponding spring, where between the shoulder and at least one section of a coil of spring the base is retained in a non-losing way with respect to the spring. 8. Torsional oscillation damper according to at least one of the preceding claims, characterized in that the free end section of the spring coil, close to the base, serves to retain the base with respect to the spring. 9. Torsional oscillation damper according to at least one of the preceding claims, characterized in that the base has a radial groove, in which at least one section of a spring coil can be coupled formally. 10. Torsional oscillation damper according to at least one of the preceding claims, characterized in that the free end region of an end coil of the spring engages radially in a groove of the base associated with this end region. 11. Torsional oscillation damper according to one of claims 9, 10, characterized in that - in the unloaded state of the helical spring - the end coil, close to the base, apart from the end region engaging in the groove of the base, has the same turn angle of the turns provided between the end turns. Torsional oscillation damper according to at least one of the preceding claims, characterized in that the end section of the corresponding end coil, at least in the unloaded state of the helical spring, extends parallel to the supporting surface of the base for the helical spring. 13. Torsional oscillation damper according to one of the preceding claims, characterized in that the end region of the end coil, close to the base, of the helical spring, with respect to the other coils is offset radially in the direction of the longitudinal axis of the helical spring. 14. Torsional oscillation damper according to at least one of the preceding claims, in which the energy accumulator is formed by at least one external helical spring and at least one internal spring housed in a cavity delimited by the coils of the external spring, where on at least one end of the The energy accumulator is provided with a base which has a non-losing connection with the external spring. 15. Torsional oscillation damper according to at least one of the preceding claims, in which the energy accumulator is formed by at least one external helical spring and at least one internal spring housed in the cavity delimited by the coils of the external spring, and on at least one end of the energy accumulator, a socket is provided, which has a non-losing connection with the internal spring. 16. Torsional oscillation damper according to at least one of the preceding claims, in which the energy accumulator is formed by at least one external helical spring and at least one internal spring housed in the cavity delimited by the coils of the external spring, and on at least one end of the an energy accumulator is provided with a base, which has a non-losing connection both with the external spring and with the internal spring. 17. Torsional oscillation damper according to at least one of the preceding claims, where the energy accumulator is formed by at least two helical springs, provided in series arrangement between stress zones of the rotating components with respect to each other, where between the opposite end regions of the helical springs, a base is provided, which is retained in a non-losing way at least with respect to one of the springs. 18. Torsional oscillation damper according to claim 17, characterized in that at least one of the two springs forms an external spring, which houses an internal spring, and the internal spring extends at least over a partial area of the longitudinal section of the external spring. 19. Torsional oscillation damper according to at least one of the preceding claims, characterized in that at least in the case of a pair of springs consisting of an external spring and an internal spring, the internal spring is shorter than the external spring. Torsional oscillation damper according to one of the preceding claims, characterized in that at least in the case of a pair of springs, which is formed by an external spring and an internal spring, both springs have the same length. 21. Torsional oscillation damper, in which the energy accumulator is formed by at least two springs arranged in series between the stress zone of the rotating components with respect to each other, where between the stress zones of the components and the end of neighboring springs of the energy accumulator there is no base, however between the opposite end regions of the springs connected in series there is a base. 22. Torsional oscillation damper according to at least one of the preceding claims, characterized in that at least one of the helical springs forming the energy accumulator, in the discharged state has a pre-curved shape. 23. Torsional oscillation damper according to at least one of the preceding claims, characterized in that the energy accumulators formed by the helical springs have a large length-to-external diameter ratio. 24. Torsional oscillation damper according to at least one of the preceding claims, characterized in that a maximum of three energy accumulators, arranged on the same diameter zone, are provided between the components which rotate relative to each other. 25. Torsional oscillation damper according to at least one of the preceding claims, characterized in that the energy accumulators between the rotatable components relative to each other, between which they are provided, make possible a torsion angle of 30 ° in both directions of rotation. 26. Torsional oscillation damper according to one of the preceding claims, characterized in that it is in each case a component of a flywheel consisting of several masses.