DE3545857C1 - Device for reducing engine-induced vibrations in a drive line - Google Patents

Abstract

The two flywheel parts (1, 2) can be twisted relative to one another against springs (3) arranged between abutment parts (40; 50, 51) in the form of annular discs. One abutment part (40) is coupled frictionally, via a clutch (41) to one flywheel part (2) and can be twisted to only a limited extent relative to this flywheel part (2). The other abutment part (50, 51) is connected to the other flywheel part via another clutch (53), the frictional engagement of which is greater than in the case of the abovementioned clutch (41) and which can be twisted to an unlimited extent relative to this flywheel part (1). <IMAGE>

Description

The invention relates to a device for Reduction of vibrations excited on the motor side a drive train, especially a split one Flywheel, with two coaxial arranged, by means of suspension with each other drive-coupled device or Flywheel elements, one with the engine and the other of which is connected to the drive train or is connectable, the one device or flywheel element associated abutment Suspension is arranged on an abutment part, which with this device or flywheel element non-positive without limitation of the twist speed is connected in terms of drive relative to one another, and wherein the strength of the adhesion is greater than is the maximum torque of the engine.  

Such a device or a corresponding one Flywheel is the subject of the earlier patent 35 05 069. The advantage of an appropriate arrangement is in that good comfort can be achieved.

The drive system is tuned so that the Resonance frequency if possible slightly below the Engine idling speed. Accordingly the resonance frequency can practically only when starting of the engine. This is equivalent so that the driving operation in the so-called supercritical Area occurs, i.e. the frequency of the driving Vibrations that occur are generally considerable higher than the resonance frequency. Accordingly occur only relatively little while driving Vibration amplitudes between the devices or flywheel elements, with a transmission the vibrations from the engine to the drive train or in the opposite direction by the suspension is prevented between the flywheel parts. If the resonance range of the Device or flywheel is passed through, so guide the device or flywheel parts relatively large stroke movements relatively to each other, which is effectively dampened be because of the suspension between the Device or flywheel elements transmitted Forces exceed the strength of the adhesion, so that the non-positive with the one device or flywheel element connected abutment part slipped towards the named element.  

As long as the between the device or Flywheel parts transmitted by means of the suspension Forces - such as one while driving Motor vehicle - less than the strength of the Are frictional, it can not dampen anything Have an effect. While this is relative with the small-stroke vibrations, such as those in supercritical Area occur, quite desirable. However there there are situations where outside of the Larger resonance frequency of the drive train Relative movements between the device or Flywheel elements can occur. This is for example when changing loads between thrust and Train operation of a vehicle the case. But since the forces occurring in such a load change often less than the strength of the adhesion are a damping of the with the load change associated vibrations not easily possible.

Therefore, it is an object of the invention, the device or the flywheel of the type specified at the beginning to be designed in such a way that between the device or Relative movements occurring in flywheel elements are effectively dampened even if the with these relative movements between the devices and flywheel elements forces weaker than the maximum engine torque, but stronger than one are to be specified threshold.

This problem is solved in that the other Device or flywheel element assigned Abutment of the suspension on another abutment part is arranged, which with the other device or Flywheel element non-positive, but with limited  Rotation relative to the device or flywheel element is connected, and the strength of this force has a smaller value than that Frictional connection between the one device or Flywheel element and the aforementioned Abutment part.

Because of the invention, one of the abutments parts even at comparably low torques give way or break free and accordingly relative movements between the device or flywheel dampen elements comparatively early. Only at; only when very strong torques or extremely high Vibration amplitudes of the relative movements between the device or flywheel elements are also there the other abutment with appropriate damping effect after.

The invention thus provides progressive damping the relative movements of the device or flywheel elements guaranteed, i.e. the damping takes increasing relative movements.

According to a preferred embodiment of the invention Progressiveness can be improved by each abutment part with the assigned and / or each other device or flywheel part over one or more playful couplings non-positive is connected, the couplings differing in each case Lich play, so that with a correspondingly strong Relative movement of the device or flywheel elements the effects of the clutches one after the other appropriate increase in the respective adhesion between Abutment part and device or flywheel element deploy.  

A particularly preferred embodiment of the Invention is characterized in that as Abutment washers radially overlapping each other with in the overlap area in the circumferential direction stretched, intersecting cutouts or windows are arranged, which in circumference take up directionally arranged compression springs, their ends - in the axial view of the screws compression springs seen - each of the disc levels enforce, and that the one abutment forming washers in the area of their inner circumference by means of clutch plates with one device or flywheel element and the other abutment forming washers in the area of their outer circumference by means of clutch plates with the other device or flywheel element are non-positively connected. This is a space-saving and easy to assemble Construction achieved.

It is useful if the one abutment forming washers on their inner circumference - e.g. radial - have protrusions, which with play in Circumferential direction with counter protrusions on one Device or flywheel element or one Hub part of it cooperate abruptly, or if they form the other abutment Corresponding washers on their outer circumference Have projections, which with play in scope direction with counter projections together act on the other device or Flywheel element or a circumferential ring of the same are arranged. In this way you can be very simple measures the limited mobility of a the abutment parts compared to the associated Ensure device or flywheel element.  The features of further preferred embodiments are the subject of the subclaims and are in the remaining explained below with reference to the drawing, shown in the preferred variants of the invention are. Show

Fig. 1 to 6 are schematic illustrations of various embodiments of a divided flywheel according to the invention,

Fig. 7 is a diagram for explaining the dependence of the force acting between the flywheel parts of the embodiment of FIG. 5 and to be overcome torques (M) in dependence on the relative displacement (φ) of the flywheel parts against each other, and

FIGS. 8 and 9 according to the invention Axialschnittbilder flywheels according to the example shown in Fig. 5 construction scheme.

In Fig. 1, the two flywheel parts 1 and 2 are shown schematically as heavy bodies, which are supported or coupled to one another by means of a suspension 3 . The suspension 3 is clamped between two abutments 4 , 5 , which are each non-positively connected to the respectively assigned flywheel part 1 or 2 by means of a slip clutch 6 or 7 . The slip clutches 6 and 7 are thus arranged in series with the suspension 3 . The slip clutches 6 and 7 work with different frictional engagement, ie the slip clutch 6 breaks even at relatively low torques, while the slip clutch 7 only yields at torques that are greater than the maximum torque of the motor. The abutment 4 is arranged with respect to the flywheel part 2 with limited mobility, which is predetermined by stops 8 or their spacing. The abutment 5, on the other hand, can in principle move indefinitely when the slip clutch 7 breaks away from the flywheel part 1 .

During driving operation, the flywheel parts 1 and 2 perform relative movements against one another, which are shown in FIG. 1 as the approximation or distance of the flywheel parts 1 and 2 from one another or from one another.

If only small relative movements, ie vibrations with a small amplitude, occur between the flywheel parts 1 and 2 , none of the slip clutches 6 and 7 will break loose, so that the flywheel parts 1 and 2 can move against one another practically undamped.

With stronger vibration amplitudes and correspondingly higher torques acting between the flywheel parts 1 and 2 , the slip clutch 6 breaks loose, ie the abutment 4 moves relative to the flywheel part 2 . Accordingly, the relative movement between the flywheel parts 1 and 2 along a more or less long path is dampened by the frictional engagement of the slip clutch 6 .

In the case of even stronger vibration amplitudes, the path available to the abutment 4 between the stops 8 is consumed, ie the abutment 4 abuts one of the stops 8 . With appropriate dimensioning of the frictional connection of the slip clutch 7 , the same will now break loose and limit the maximum torque transmitted between the flywheel parts 1 and 2 while damping the relative movements of the flywheel parts 1 and 2 .

1 The arrangement of Fig. 2 differs from that of FIG. Only in that between the abutments 4 and 5, coupling a lost motion slide 9 is arranged, which will only become effective, respectively, when the abutment 5 is available to him between stops 10 standing Game has consumed. The slip clutch 9 thus acts in the sense of stiffening the suspension 3 when the abutments 4 and 5 are deflected to a greater extent relative to one another in one direction or the other.

Appropriately, the distances between the stops 8 and 10 and the frictional engagement of the slip clutches 6 and 9 are dimensioned such that the wheel parts 1 and 2 break apart one after the other with a correspondingly strong relative movement of the momentum.

The embodiment of FIG. 3 differs from that of FIG. 1 only in that the abutment 5 is also non-positively coupled to the flywheel part 2 via a slip clutch 11 with play, the slip clutch 11 only becoming effective when the abutment 5 between stops 12 given space of movement is consumed.

In the embodiment of FIG. 4 in addition, it is provided that the abutment 4 in relation to Fig. 3 is additionally connected non-positively by means of a with play slip clutch 13 to the flywheel part 1, wherein the effect of the slip clutch 13 occurs only after the abutment 4 is a between stops 14 remaining movement space has consumed.

The distances between the various stops 8 , 12 and 14 and the torques that can be transmitted from the respective slip clutches 6 , 11 and 13 are expediently dimensioned such that, with a correspondingly greater deflection of the flywheel parts 1 and 2 relative to one another, the mentioned slip clutches only break apart one after the other in order to achieve a corresponding to achieve progressive damping of the relative movements of the flywheel parts 1 and 2 .

The embodiment according to FIG. 5 differs from the previous embodiments in that the abutments 4 and 5 are additionally non-positively coupled to the respectively assigned flywheel parts 1 and 2 by means of slip clutches 22 and 15 , respectively, which are each only consumed by stops 16 and 16 respectively 17 the respective abutments 4 or 5 predetermined movement play. Here, too, the arrangement is expediently coordinated such that the slip clutches break apart one after the other with a correspondingly strong deflection of the flywheel parts 1 and 2 until all the slip clutches 6 , 7 , 22 and 15 slip through with very large relative movements.

From Fig. 6 is seen that 5 have the arrangements of FIGS. 4 and also be combined. If necessary, an arrangement according to FIG. 2 is even additionally possible. For reasons of clarity, however, this is not shown in FIG. 6.

The diagram in FIG. 7 shows the mode of operation of the flywheel shown in FIG. 5 in detail. The torque M effective or transmitted between the flywheel parts 1 and 2 is shown as a function of the adjustment or rotation ϕ of the flywheel parts 1 and 2 relative to one another.

The flywheel may initially be in the central position shown in FIG. 5.

If now the flywheel parts 1 and 2 - in the illustration of FIG. 5, for example in the sense of an approximation to one another - are to be rotated against one another, then only the resistance of the suspension 3 has to be overcome, which increases the relative rotation of the flywheel parts 1 and 2 according to the curve section A opposes an increasing counter torque. Then the slip clutch 6 breaks loose and slips through a curve section B until the game available to the abutment 4 between the stops 16 is exhausted. Now, with further rotation, the suspension 3 is increasingly tensioned in accordance with the curve section C until the slip clutch 22 also slips in accordance with the curve section D. As soon as the abutment 4 between the stops 8 available game is exhausted, the suspension 3 is in turn increasingly tensioned according to the curve section E until the maximum torque that can be transmitted by the slip clutch 7 acts between the flywheel parts 1 and 2 and the slip clutch 7 accordingly slips through the curve section F. As soon as the game available to the abutment 5 between the stops 17 is exhausted, the suspension 3 is again increasingly tensioned according to the curve section G until the resistance of the slip clutch 15 according to the curve section H is overcome.

As soon as the relative movement between the flywheel parts 1 and 2 has come to a standstill in the specified direction, the suspension 3 can relax again in accordance with the curve section I. If necessary, the previously described sequence of movements can now proceed in the opposite direction. It should be noted that the abutments 4 and 5 between the stops 8 , 16 and 17 each assume an end position and accordingly can be adjusted in the opposite direction along relatively large paths B ', D' and F ' . Otherwise, the same described relationship applies mutatis mutandis to the adjustment of the flywheel parts 1 and 2 in the opposite relative direction. When the movement is reversed again, the abutments 4 and 5 can of course in turn move along the relatively large paths B '', D '' etc., which have the same length as the paths A ', B' etc., between the stops 8 , 16 and 17 .

Fig. 8 now shows an axial section of an embodiment of the flywheel according to the invention according to the construction principle shown in Fig. 5.

The flywheel part 1 is drivingly connected to the motor, not shown. The flywheel part 2 is rotatably supported by means of a bearing arrangement 18 on the flywheel part 1 and or the like by means of a clutch (not shown) with the input shaft of a drive train or a vehicle transmission (also not shown). drive connected. Between the flywheel parts 1 and 2 there remains an annular space 19 , which is used to accommodate the suspension 3 and its abutments, which are each non-positively connected to a flywheel part 1 or 2 , as will be shown below.

One abutment is formed by an annular disk 40 , which has radial projections or recesses on its inner circumference, the corresponding projections or recesses interact on a hub part 21 which is fixedly connected to the flywheel part 2 by bolts 20 . The recesses or projections on the hub part 21 or the ring disk 40 are arranged with sufficient play such that the ring disk 40 can be rotated to a limited extent with respect to the flywheel part 2 , for example by an angle of 20 °. These projections or recesses correspond to the stops 8 of the flywheel part 2 which cooperate with the abutment part 4 in FIGS. 1 to 6.

In the area of its inner circumference, the annular disk 40 is non-positively connected to the flywheel part 2 or the hub part 21 by means of a clutch arrangement 41 . The clutch arrangement 41 is designed to be progressive, ie the strength of the frictional connection increases with increased deflection of the ring disk 40 from a central position relative to the flywheel part 2 . For this purpose, it is provided that the annular disk 40 is non-positively connected to the friction plates 42, which are fixed relative to the flywheel part 2 . The friction plates 42 set an adjustment of the annular disc 40 relative to the flywheel part 2 and the boss portion 21 always has a predetermined resistance against.

Furthermore, the annular disk 40 is positively connected to an annular lamella 43 , but with play, which is less than the play of the annular disk 40 relative to the hub part 21 or the flywheel part 2 . To this end has the annular lamella 43 at its outer circumference angled portions 43 'which engage in lateral recesses of the annular disk 40th The recesses on the washer 40 have a greater extent in the circumferential direction than the bends 43 'to give the ring plate 43 the desired game against the washer 40 . The ring plate 43 interacts with further friction plates 44 , which produce a non-positive connection between the flywheel part 2 or the hub part 21 and the ring plate 43 .

If the annular disk 40 is adjusted relative to the flywheel part 2 , then only the frictional connection which is generated by the friction plates 42 must first be overcome. At larger deflection angles, the frictional connection between the ring plate 43 and the hub part 21 or the momentum wheel part 2 must then be overcome.

Near the outer circumference, the annular disk 40 has windows 45 which extend in the circumferential direction and in which 3 helical compression springs with or without pretension are used as the suspension.

At the side of the window area of the ring disk 40 , ring webs 51 are arranged, which in turn - or the like - by means of bolts. - Are attached to an annular disc 50 , which in turn is arranged concentrically to the annular disc 40 . Windows 52 corresponding to the windows 45 of the annular disk 40 are arranged in the ring webs 51 , which receive areas of the helical compression spring 3 .

In a central position of the washers 40 and 50 , the windows 45 and 52 lie flush with one another, so that the two ends of each helical compression spring 3 each abut the radial edges of the windows 45 and 52 . If the washers 40 and 50 are deflected from their central position relative to one another, the windows 45 and 52 can only partially overlap, with the result that the helical compression springs are increasingly compressed, with one end of each helical compression spring only at one radial edge of the Window 45 and the other end only abuts the radial edges of the window 52 . Thus, the helical compression springs 3 are increasingly tensioned when the washers 40 and 50 are deflected more or less far in one direction or the other.

At its radially outer edge, the ring disk 50 is only non-positively connected to the flywheel part 1 by means of a clutch arrangement 53 , ie when the frictional connection is overcome, the ring disk 50 can be rotated as far as desired relative to the flywheel part 1 .

The clutch arrangement 53 is in turn designed to be progressive, ie with small deflection angles between the ring disk 50 and the flywheel part 1 , a lower frictional connection is effective than with larger deflection angles. For this purpose, the washer 50 is permanently coupled to the flywheel part 1 , ie, independently of the adjustment angle, by friction plates 54 and 57 . This frictional connection is therefore effective with each relative adjustment between the ring disk 50 and the flywheel part 1 .

In addition, a ring plate 55 is positively connected to the flywheel part 1 by angling 55 'on the outer circumference of the ring plate 55 in recesses on the flywheel part 1 axially displaceable, but engage without play in the circumferential direction. In addition, the washer 50 is positively connected, but with play with another ring lamella 56 , which has circumferentially extending windows in the region of its inner circumference, in which the bolts 20 'or their heads are received with play in the circumferential direction.

The ring plate 56 interacts with other friction plates 57 , so that an additional frictional engagement between the flywheel part 1 and the ring plate 50 occurs after the movement of the ring plate 56 has been consumed relative to the ring plate 50 .

In the arrangement shown, the clutch assembly 41 has an overall frictional connection, which is less than the maximum torque of the engine, while the clutch assembly 53 , after the game between the bolt 20 'and the annular plate 56 is used up, can only be rotated further if that acting torque exceeds the maximum engine torque.

The embodiment according to FIG. 9 differs from that according to FIG. 8 primarily in that the flywheel parts 1 and 2 are coupled directly to one another via a clutch 60 with play. For this purpose, an annular lamella 61 with the flywheel part 2 is positively connected in the circumferential direction, but with play, by arranging radial projections or recesses on the outer circumference of the annular lamella 61 , which cooperate with recesses or projections on the flywheel part 2 and ensure the desired play. The ring plate 61 is in turn arranged between friction plates 62 , which are held on the flywheel part 1 . The clutch 60 thus gives the flywheel part 2 a free movement space corresponding to the play between the ring plate 1 and the flywheel part relative to the flywheel part 1 . As soon as the game in one direction or the other is exhausted, the - relatively weak - frictional engagement of the clutch 60 is effective between the flywheel parts 1 and 2 .

In the example of FIG. 9, the clutch 41 acts between the radially outer area of the ring disk 40 and the flywheel part 1 . The annular disc 40 is axially displaceable on the flywheel part 1 and rotatable relative to the flywheel part 1 between friction plates 42 , one of which directly adjoins the flywheel part 1 , while the other friction plate is adjoined by an annular plate 47 which is movable on the flywheel part 1 in the axial direction thereof, however is rotatably supported. Between two further friction plates 42 , which in turn are arranged between the ring plate 47 and a ring disk 48 , the ring plate 43 is arranged, which engages with bends 43 'on its inner circumference in openings of the ring disk 40 . The openings of the ring disk 40 are dimensioned in the circumferential direction such that the bends mentioned have a play in the circumferential direction. The entire arrangement described is pressed together in the axial direction of the flywheel by means of a spring ring 49 , which has an S-like cross section and is tensioned with its radially inner region against the radially inner region of the ring disk 48 .

As long as the play of the bends on the ring lamella 43 in the cutouts or openings in the ring disk 40 has not yet been consumed, the ring disk 40 can be rotated relative to the flywheel part 1 with sufficient torques without the ring lamella 43 also being rotated. As soon as the game between the ring lamella 43 and the ring disk 40 is then consumed, the ring disk 40 can only be rotated further when an increased force is applied to the flywheel part 1 . The frictional connection is expediently such that it exceeds the maximum torque of the motor.

The ring disk 50 and the ring webs 51 are axially displaceable with their inner circumference and movable with play in the circumferential direction on the flywheel part 2 . The play in the circumferential direction is limited by recesses arranged on the inner circumference of the ring disk 50 or the ring webs 51 , which cooperate with the bolts 20 in a stop-like manner. Friction plates 54 are arranged on both sides of the ring webs 51 , which interact on the one hand with one of the ring webs 51 and on the other hand with a ring part 58 or a ring plate 55 . The ring part 58 is non-rotatably connected to the flywheel part 2 by means of the screw bolts 20 , while the ring plate 55 is arranged to be axially displaceable, but is immovable in the circumferential direction because it engages around the screw bolts 20 by means of recesses on its inner circumference. An annular plate 55 'is arranged between two further friction plates. This ring lamella 55 'has on its outer circumference projections which engage around a bolt 20 ' on one of the ring webs 51 with play in the circumferential direction, so that the ring lamella 55 'can be rotated by a limited path relative to the ring webs 51 . The movement play between the ring plate 55 'and the ring webs 51 is less than the movement game of the ring webs 51 with respect to the flywheel part 2 . This is followed by a further ring plate 56 , which is designed and arranged in the same way as the ring plate 55 , towards the flywheel part 2 . The entire clutch 53 is axially pressed together by means of a spring washer 63 . As long as the movement between the ring webs 51 on the one hand and the ring plate 55 'is not yet consumed, the ring webs 51 can , as far as the movement play relative to the flywheel part 2 , rotate without simultaneous movement of the ringla melle 55 ' relative to the flywheel part 2 . After depletion of the game between the ring webs 51 and the ring lamella 55 ', an increased resistance must be overcome if the ring webs are to rotate relative to the flywheel part 2 . The maximum frictional engagement of the clutch 53 is dimensioned such that the ring webs 51 are already adjusted relative to the flywheel part 2 upon the action of torques which are less than the maximum torque of the engine.

If necessary, the arrangement described can also be modified by the annular disk 40 , for example on its outer circumference, having projections or recesses which cooperate with recesses or projections on the flywheel part 1 in such a way that the annular disk 40 is only able to rotate to a limited extent relative to the flywheel part 1 . The design of this game is made such that the ring disc 40 against the flywheel body 1 available to game is greater than the play of the angled portions 43 'of the ring blade 43 in the recesses or openings of the annular disk 40th

If the annular disc 40 in the described manner is only limited rotation relative to the flywheel member 1 about the annular disk 50 and the annular webs 51 against the flywheel body 2 are also arranged indefinitely rotatable, ie at the annular disc 50 and the annular webs 51 are on the inner circumference no recesses or Projections or the like arranged, which could cooperate in the sense of a rotation limit with the bolts 20 or other elements.

Incidentally, in the case of the last-described embodiment, the frictional engagement of the clutch arrangement 53 is generally larger than the maximum torque of the engine, while the maximum frictional engagement of the clutch 41 is less than the maximum engine torque.

Claims (7)

1.Device for reducing engine-side vibrations of a drive train, in particular a divided flywheel, with two device or flywheel elements, which are arranged coaxially with one another and are coupled to one another in terms of drive by means of suspension, one of which is or can be connected to the engine and the other to the drive train. wherein the one device or flywheel element associated abutment of the suspension is arranged on an abutment part which is non-positively connected to this device or flywheel element without limiting the rotatability relative to each other, and the strength of the force fit greater than the maximum torque the engine is, preferably with an effective between the device or flywheel elements, playful non-positive clutch, according to patent 35 05 069, characterized in that the other device or flywheel element ( 2 ) assigned W iderlager ( 4 ) of the suspension ( 3 ) is arranged on a further abutment part ( 40 ) which is non-positively connected to the other device or flywheel element ( 2 ), but with limited rotatability, and that the strength of this frictional connection is less than that Non-positive connection between the one device or flywheel element ( 1 ) and the first abutment part ( 50 ). 2. Device or flywheel according to claim 1, characterized in that one or - preferably - both abutment parts ( 4 , 5 ; 40 , 50 ) each with at least one device or flywheel part ( 1 , 2 ) are progressively non-positively connected. 3. Device or flywheel according to one of claims 1 or 2, characterized in that the abutment parts ( 4 , 5 ; 40 , 50 ) are non-positively connected to each other via a clutch ( 9 ) with play. 4. Device or flywheel according to one of claims 1 to 3, characterized in that each abutment part ( 4 , 5 ; 40 , 50 ) with the associated and / or the respective other device or flywheel part ( 1 , 2 ) over a clutch with play ( 11 , 13 , 22 , 15 ) is non-positively connected. 5. Device or flywheel according to one of claims 1 to 4, characterized in that as abutment ( 4 , 5 ) radially overlapping annular discs ( 40 , 50 , 51 ) with in the overlap area in the circumferential direction, each other over intersecting cutouts or windows ( 45, 52 ) are arranged, which receive helical compression springs ( 3 ) arranged in the circumferential direction, the front ends of which - seen in the axial view of the helical compression springs - each penetrate the disk planes, and that the annular disks ( 40 ) forming an abutment ( 4 ) in the area of their Inner circumference by means of clutch plates ( 41 ) with the one device or flywheel element ( 2 ) and the ring disks ( 50, 51 ) forming the other abutment ( 5 ) in the area of their outer circumference by means of clutch plates ( 53 ) with the other device or flywheel element ( 1 ) are non-positively connected. 6. Device or flywheel according to one of claims 1 to 5, characterized in that the abutment ( 4 ) forming annular discs ( 40 ) on their inner circumference - for example radial - have projections which with play in the circumferential direction with counter-projections on one Device or flywheel element ( 2 ) or a hub part ( 21 ) of the same cooperate abutly, or that the other abutments ( 5 ) forming ring discs ( 50, 51 ) have corresponding projections on their outer circumference, which with play in the circumferential direction with abutting projections cooperate, which are arranged on the other device or flywheel part ( 1 ) or a circumferential rim thereof. 7. Device or flywheel according to one of claims 1 to 6, characterized in that the device or flywheel elements ( 1 , 2 ) are coupled directly by means of a clutch ( 60 ) with play.