DE8717797U1 - Device for damping torsional vibrations - Google Patents

Description

LuK discs and Kupplungsbau GmbH Industriestraße 3

7580 Bühl / Baden 0535/32

Device for damping torsional vibrations

The invention relates to a device for damping torsional vibrations, for example in the drive train of a vehicle, wherein the device has at least two flywheel masses mounted opposite one another by means of a rolling bearing, one of which can be connected to an engine and the other to a transmission via a coupling, such as a friction clutch, and at least one of the flywheel masses has a chamber that can be at least partially filled with a viscous or pasty medium and sealed to the outside by at least one seal, in which a damping device is accommodated that resists relative rotation between the flywheel masses.

Such devices have already been proposed, but due to their structural design they are relatively complex to manufacture and assemble, as they require auxiliary holes for assembly, among other things, which lead into the chamber filled with viscous medium. In order to seal these holes after assembly, Additional sealing elements are required for the construction of the flywheel masses.

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The aim of the present invention was to create a device of the type mentioned above that can be assembled in a particularly simple and quick manner. Furthermore, the inexpensive manufacture of such a device should be made possible by design measures that allow simplification while simultaneously improving the sealing of the chamber filled with viscous medium. In addition, the service life of such a device should be extended and wear should be avoided. A further aim of the invention is to improve the function or mode of operation compared to the previously known devices of the type mentioned above.

According to the invention, this is achieved in that the assembly of the device is carried out by two pre-assembled sub-units being designed in such a way that they can be joined axially and connected to one another via a connecting means and the sub-units have at least two of the following features:

- a sealing element is fixed to one of the sub-units which, after assembly, is fixed to a counter provided on the other unit sealing surface,

- the rolling bearing is positively fixed to one of the sub-units and can be pushed onto a seat in the other sub-unit during assembly,

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one of the subunits carries the one component having a profile <j

part of a plug connection and the other unit is the counter profile of a plug connection that couples the two units in a rotationally locked manner.

Such a structure of the device enables pre-assembly in two assemblies, namely the primary side assembly that can be connected to the engine and the secondary side assembly that can be connected to the drive train or gearbox via a coupling, whereby both the sealing of the chamber and the rotary connection and the bearing between the assemblies or units are created by simply pushing them together axially. All that is left to do is to create the axial cohesion of the two units, which can be done easily by axially fixing the rolling bearing to the seat onto which it is pushed when the units are assembled. Such a structure of the device also enables the device to be easily dismantled, so that any repairs that may be required, such as replacing the sealing element or the rolling bearing, can be carried out particularly easily.

For the design and service life of the device, it can be particularly advantageous if the flywheel mass connectable to the motor has the chamber fillable with viscous medium and the damping device and thus represents one pre-assembled unit, while the other pre-assembled unit contains the flywheel mass connectable to the gearbox.

By designing the device in this way, the thermal load on the viscous medium can be reduced considerably. This is due to

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This is due to the fact that the flywheel mass, which can be connected to the transmission via a friction clutch, essentially absorbs and dissipates the frictional heat that occurs when the clutch is actuated, so that this frictional heat only has a small thermal effect on the viscous medium.

It can be particularly advantageous if an output part of the damping device has profiles that can be brought into engagement with counter-profiles provided on one of the units, and furthermore one of the units carries the sealing element that comes into sealing contact with a surface of the other unit when the two units are put together.

A particularly advantageous design of the device can be made possible by the seal created by assembling the two units, which seals or closes the chamber at least partially filled with viscous medium against an annular gap located axially between the chamber and one of the flywheels, which can be open to the outside. This annular gap expediently extends as far radially inwards as possible and is provided between the flywheel carrying the friction clutch and a side wall delimiting the chamber, whereby the heat effect on the damping device or the viscous medium can be reduced even further. A further improvement in the insulation of the chamber containing the damping device and the viscous medium can be achieved by ventilation openings provided in the flywheel carrying the friction clutch and

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be connected to the annular gap which is open radially outwards, so that air can circulate between the two flywheel masses, which is guided past the aforementioned side wall of the chamber.

It can be advantageous if the damping device comprises force accumulators that act in the circumferential direction and the output part is a flange-like component that interacts with these and has a central recess whose circumferential contour limits the profiling. The counter-profilings that interact with these profiles can be molded directly onto the flywheel that holds the friction clutch or can also be provided on a component connected to this flywheel. For the manufacture of the device, it can be particularly useful if these counter-profilings are molded onto the outer circumference of a ring-disk-like component that is connected to the other flywheel. Such a ring-disk-like component can be axially fixed in a simple manner on an end face of the flywheel that carries the friction clutch and faces the motor-side flywheel.

The assembly of the device can be made easier by mounting the roller bearing on the flywheel that can be connected to the gearbox before axially connecting the units or flywheels. To fix the bearing, it can be accommodated in a central recess of one of the flywheels and clamped axially between a shoulder of this flywheel and the ring-disk-like component. The assembly of the device can also be made easier by the flywheel on the motor side having a central axial attachment that

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After assembling the two flywheel masses, the bearing-receiving recess of the other flywheel mass protrudes axially and has a seat for the inner ring of the rolling bearing.

The axial cohesion of the two flywheel masses can be achieved in a simple manner by axially securing the inner roller bearing ring after the two flywheel masses have been axially connected by a ring disk which at least partially overlaps it radially and is axially fixed on the front side of the axial attachment and represents the connecting means. The inner roller bearing ring can advantageously be clamped between this ring disk and a shoulder of the axial attachment.

In order to prevent the grease filling from escaping from the bearing and/or to ensure that the chamber is properly sealed, it can be particularly advantageous if a seal is provided on the side of the bearing facing away from the chamber, which seal acts between the radially outer and radially inner bearing rings, which can be rotationally fixed to one of the bearing rings and clamped against the other. It can be particularly useful if the seal is designed like a ring disk and is rotationally fixed to the radially outer bearing ring and rests against the radially inner bearing ring under axial preload .

Furthermore, it can be advantageous for the function of the device if a seal is provided on the side of the bearing facing the chamber, sealing the chamber against the bearing , so that in the chamber and in the

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Bearings can be used with various viscous media or greases that are tailored to the specific functions they are intended to perform. This seal can also be designed and arranged in such a way that it is effective between the two bearing rings. 5

For the design of the device, it can be particularly advantageous if the sealing element, which becomes effective when the two flywheel masses are pushed together axially, can be pre-assembled on one of the flywheel masses or units. For the functioning of the sealing element, it can be appropriate if this sealing element can be pre-assembled on the unit containing the flywheel mass on the gearbox side.

To prevent the viscous medium from escaping from the chamber, it may also be appropriate to install a spacer between at least one of the bearings rings and the component supporting them. Such a seal can be arranged in a particularly simple manner between the radially inner bearing ring and the pin-like projection that surrounds it, the flywheel that is firmly connected to the crankshaft. A groove can be easily cut into the pin to accommodate the seal. like approach in the area of the axial extension of the bearing ring. Such a seal can be formed in a simple manner by an O-ring.

The sealing element that seals the chamber after the two units have been assembled advantageously has at least one ring-disk-like sealing part. It can be useful if the ring-disk-

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like sealing part is axially resilient so that after the flywheel units are put together, it is elastically deformed to create a perfect seal. Such a sealing part can be carried by the flywheel unit that can be connected to the engine so that after the two flywheel units are put together, it rests with pre-tension on a contact surface of the unit that accommodates the friction clutch.

To facilitate assembly of the device, it may be useful if the inner diameter of the sealing element sealing the chamber towards the annular gap is larger than the outer diameter of the counter-profiling of the plug connection. This allows the sealing element to be guided axially over the counter-profiling during assembly of the device, which is particularly advantageous if the flange-like output part of the damping device has a central recess, the peripheral contour of which limits the profiles of the plug connection and that the ring-disk-like component with counter-profiling on the outer circumference is axially fixed on an end face of the gearbox-side flywheel unit facing the engine-side flywheel unit.

A perfect seal of the chamber and a perfect structure of the device can be achieved by the sealing element with its radially outer edge area axially resting on a radial wall delimiting the chamber, which is axially arranged between the disk-like output part of the damping device and the second flywheel mass or

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unit is provided. This radial wall is expediently adjacent to the annular gap provided between the two flywheel masses or units. It can be advantageous if the radially outer edge area of the sealing element is axially fixed to the radial wall. For the function of the sealing element, it can also be appropriate if it is axially clamped in the outer edge area. Such a clamping, which can be axially springy, enables the sealing element to pivot around the clamping area, similar to a disc spring. The contact surface provided on the other flywheel mass or unit for the sealing element can be formed in a simple manner by a circular ring-shaped component that is clamped axially between the front face of this other flywheel mass and the component with the counter-profiling and extends radially outwards further than the counter-profiling. This circular ring-shaped component can be radially outwards be offset or dished in the direction away from the component provided with the counter-profiling.

For the structural design and assembly of the device, it can be particularly advantageous if the introduction of the viscous medium in the chamber before assembling or plugging the two Such at least partial filling of the chamber not only enables better handling of the flywheel mass unit containing this chamber, but also the introduction of the viscous medium through those areas of the chamber which are

Putting it together

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plugs of the flywheel units. The latter has the particular advantage that no additional filling opening or closure or sealing agent is required.

It can be particularly advantageous if the chamber is filled with the viscous medium, which can be a pasty medium such as lubricant, grease or the like, while rotating. The rotational speed or rpm can be set in such a way that the centrifugal force acting on the viscous medium causes a distribution of this viscous Medium. In particular, a method can be advantageously suitable for producing a device according to the invention, according to which at least the flywheel mass or unit comprising the chamber is adjusted to a position which determines the distribution of the viscous medium after or during the filling of the chamber, which has taken place only partially, before the balancing process. Odium. This spin speed can advantageously be considerably higher than the balancing speed. This type of process ensures that when the chamber is filled with a pasty medium which shows as little or no change in state as possible over the temperature ranges occurring, so at least there is no significant change in toughness, a uniform distribution over the circumference or a uniform filling height over the circumference, so that a very precise balancing of the device is possible. The high speeds before balancing also prevent the individual components from being damaged. Air pockets remain in the free spaces, as these are displaced* due to the high centrifugal force acting on the viscous medium.

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This ensures that after a long period of operation of the device no imbalance occurs as a result of air pockets subsequently being filled by the viscous medium.

In order to enable precise balancing and to avoid the subsequent occurrence of additional imbalance, it is advantageous if the speed to which at least the flywheel mass or unit having the chamber is brought before balancing is in the order of the speeds up to which the internal combustion engines in which devices according to the invention are used can be operated. It can be advantageous if the spin speeds are between 4000 and 7000 revolutions per minute, preferably in the order of approximately 5000 to 6000 revolutions per minute.

For some applications, it may be advantageous if the unit containing the chamber is balanced before it is assembled with the other unit. The other unit can also be balanced on its own, so that the device is balanced after the two units are assembled. For other applications, however, it may also be useful if balancing is carried out after the two units have been assembled.

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The invention is explained in more detail with reference to Figures 1 to 4.

It shows:

Figure 1 shows a section through a device according to the invention, Figure la shows the detail "X" of Figure 1 on an enlarged scale,

Figure 2 is a view of the device according to Figure 1 in the direction of arrow II without coupling and with cutouts,

Figure 3 shows a section through another embodiment,

Figure 4 shows a partially shown section along the line IV-IV of Figure 3,

The torque transmission device 1 shown in Figures 1, 1a and 2 for compensating rotary shocks has a flywheel 2 which is divided into two flywheel elements 3 and 4. The flywheel element 3 is attached to a crankshaft 5 of an internal combustion engine (not shown in detail) via fastening screws 6. A switchable friction clutch 7 is attached to the flywheel element 4. Between the pressure plate 8 of the friction clutch 7 and the flywheel element 4, a clutch disk 9 is provided which is accommodated on the input shaft 10 of a transmission (not shown in detail). The pressure plate 8 of the friction clutch 7 is pushed in the direction of the flywheel element 4 by a

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. on the clutch cover 11, a disk spring 12 is pivotally supported. By operating the friction clutch 7, the flywheel element 4 and thus also the flywheel 2 or the internal combustion engine of the transmission input shaft 10 can be coupled and uncoupled. Between the flywheel element 3 and the flywheel element 4, a first, radially outer damper 13 and a second, radially inner damper 14 connected in parallel with it are provided, which enable a relative rotation between the two flywheel elements 3 and 4.

The two flywheel elements 3 and 4 are mounted so that they can rotate relative to one another via a bearing 15. The bearing 15 comprises a roller bearing in the form of a single-row ball bearing 16. The outer bearing ring 17 of the roller bearing 16 is in a recess 18 of the flywheel element 4 and the inner bearing ring 19 of the roller bearing 16 is on a central, axially The flywheel element 3 is arranged on a cylindrical pin 20 extending away from the crankshaft 5 and projecting into the recess 18.

The inner bearing ring 19 is received on the pin 20 by means of a press fit and is clamped between a shoulder 21 of the pin 20 or the flywheel element 3 and a locking washer 22 which is fastened to the front side of the pin 20 by means of rivets 22a.

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As can be seen in particular from Figure 1a, the bearing 16 is axially secured relative to the flywheel element 4 by being clamped axially between a shoulder 25 of the flywheel element 4 and an annular disk 27 which is firmly connected to the second flywheel element 4 by means of rivets 26, by interposing two rings 23, 24 with an L-shaped cross section.

The two rings 23, 24 form a thermal insulation that interrupts or at least reduces the heat flow from the friction surface 4a of the flywheel element 4, which interacts with the clutch disc 9, to the bearing 16.

The radially inward-pointing legs 23a, 24a of the rings 23, 24 extend partially radially over the inner bearing ring 19 and are supported axially on it, whereby they simultaneously serve as a seal for the bearing 16. In order to ensure a perfect seal for the bearing 16, the radially extending legs 23a, 24a are each axially loaded in the direction of the end faces of the inner bearing ring 19 by a force accumulator in the form of a disc spring 28, 29.

Between the inner bearing ring 19 and the projection 20a of the flywheel element 3, a sealing ring 37 is provided, which is received in a radial annular groove 37a of the projection 20a .

From Figure 1 it can be seen that the flywheel element 3 forms a housing which defines an annular chamber 30 in which the dampers 13, 14 are accommodated. The flywheel element 3, which has an annular chamber 30,

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ment 3 consists essentially of two housing parts 31, 32. The two housing parts 31, 32 that delimit the annular chamber 30 are designed as cast parts. The housing part 32 has an axial cylindrical projection 32a on its circumference, via the inner surface 35 of which the housing part 32 is centered on an outer surface 34 of the housing part. The axial securing of the two cast housing parts 31, 32 is carried out by means of radial pins 38 that are inserted in the area of the centering surfaces 34, 35. The housing part 32 carries a starter ring gear 40 on a shoulder 39 that axially overlaps the pins 38 so that they cannot move radially. To seal the annular chamber 30 from the outside, a sealing ring 36 is provided, which is arranged in the area between the two pins 38 and the chamber 30.

If a low moment of inertia of the first flywheel element 3 is desired, at least one of the housing parts 31, 32 can be made from a light metal alloy, such as cast aluminum. Such light metal castings have the advantage that they can be produced by a pressure or pressing process and can be used without major rework. 20

The two dampers 13, 14 have a common output part in the form of a radial flange 41, which is arranged axially between the two housing halves 31, 32. The flange 41 is, as can be seen in particular from Figure 2, connected in a rotationally fixed manner with its radially inner regions to the annular disk part 27 via an axial plug connection 42.

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which is fastened to the front side of the axial projection 43 of the flywheel element 4 pointing in the direction of the crankshaft .5 via the rivet 26.

The flange 41 has radial arms 44 on its outer circumference, which form the application areas for the energy storage devices in the form of coil springs 45 of the outer damper 13. Radially within the cutouts 46 for the coil springs 45 between the arms 44 - viewed in the circumferential direction - the flange 41 has arched windows 47 in which the energy storage devices in the form of coil springs 48 of the inner damper 14 are accommodated. Radially between the cutouts and the windows 47, the flange 41 forms webs 49 running in the circumferential direction, which connect the radial arms 44 or the radial areas 50 of the flange present in the circumferential direction between the windows 47. The radial areas 50 form the application areas of the flange 41 for the coil springs 48.

The annular chamber 30 forms a ring-channel-like or torus-like receptacle 51 radially on the outside, into which the arms 44 of the guide engage radially.

The ring-channel-like receptacle 51 for the energy storage device 45 is essentially formed by axial recesses 52, 53 extending over the circumference, which are introduced into the radial areas of the housing parts 31, 32 and into which the projections protruding on both sides of the flange 41 are inserted.

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range of the energy accumulator 45. Radially inwards, the ring-channel-like receptacle 51 is closed by the webs 49 of the flange 41, apart from a small gap 54.

As can be seen from Figure 1, the axial indentations 52, 53 are designed in cross-section in such a way that their arc-like course is at least approximately adapted to the circumference of the cross-section of the energy storage devices 45. The indentations 52, 53 thus form contact areas or guide areas for the energy storage devices 45, on which the energy storage devices 45 are located. can support. By adjusting the contact areas formed by the indentations 52,53 to the outer circumference of the energy storage 45, the wear that occurs due to the friction of the windings of the energy storage 45 on the boundary surfaces of the indentations 52,53 can be significantly reduced, since the support surface between the springs 45 and the indentations bays 52,53 is enlarged.

To prevent or reduce wear on the radial support areas of the ring-channel-like receptacle 51 for the springs 45, a highly hard steel strip 81 is provided, which extends over the The steel strip 81 is cylindrical and is accommodated in a recess 82 which is formed by a radial recess or a radial recess. When the device 1 rotates, the springs 45 are supported by their windings as a result of the centrifugal force acting on them. on the steel band 81.

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To actuate the energy storage device 45, circumferential stops 55,55a are inserted into the recesses 52,53 on both sides of the boom 44, which

circumferential direction form support areas for the energy storage devices 45. The Circumferential stops 55, 55a are formed by components adapted to the indentations 52, 53, such as forged parts or pressed parts, which are firmly connected to the housing parts 31, 32 by means of integrally formed rivets 58. The end areas of the circumferential stops 55, 55a viewed in the circumferential direction are flattened for better loading of the energy storage device 45.

As can be seen from Figure 2, the stops 55, 55a provided on both sides of an arm 44 of the flange 41 have a greater extension in the circumferential direction than the arms 44, whereby in the embodiment shown in the rest position of the device shown in Figure 2 the arms 44 are arranged centrally relative to the stops 55, 55a, Has means that the stops 55,55a project beyond the booms 44 on both sides by the same amount.

Radially within the ring-channel-shaped receptacle 51, the housing halves 31, 32 have areas 60, 61 facing each other, forming annular surfaces, between which an annular passage 62 for the flange 41 is present.

In the embodiment according to Figures 1 and 2, the width of this circular passage 62 is somewhat larger than the areas of the flange 41 contained therein, so that a gap 54 is present on at least one side of the flange 41.

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Radially within the circular passage 62, the housing parts or housing halves 31,32 have further axial indentations 63,64, into which the areas of the inner coil springs 48 projecting on both sides of the flange 41 are at least partially immersed .

As can be seen from Figure 1, the axial indentations 63, 64 are designed in cross-section such that their arc-like course is at least in the radially outer region adapted to the circumference of the cross-section of the coil springs 48, so that the springs 48 are held or guided at least in the axial direction by the indentations 63, 64.

Similar to the outer indentations 52,53, the inner indentations 63,64 also extend over the entire circumference of the device. This is advantageous because the pre-cast indentations 52,53 and 63,64 can then be machined by a turning operation, for example. To act on the energy accumulators or coil springs 48, circumferential stops 65,66 are introduced into the indentations 63,64, which form support areas for the coil springs 48 in the circumferential direction. These circumferential stops 65,66 are designed similarly to the circumferential stops 55,55a and are also riveted to the housing parts 31,32. The circumferential stops 65, 66, which are arranged on both sides of the radial regions 50 of the flange 41, have a greater extent in the circumferential direction than the regions 50 which serve to act on the springs 48. The arrangement |

the stops 65,66 in relation to the radial areas 50 is such that the circumferential stops 65,66 protrude on one side relative to the areas 50 in the rest position of the device 1, whereas

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on the other hand, the stops 65, 66 and the radial areas 50 can be flush. Furthermore, the offset of the stops 65, 66 in relation to the radial areas 50 is such that two stops 65 and 66 which follow one another in the circumferential direction are offset in the opposite direction of rotation relative to the radial areas 50 of the flange assigned to them. Due to this structure, the inner springs 48 form two spring groups, namely 48a and 48b, which come into effect in stages.

The webs 49 of the flange 41 are dimensioned in relation to the inner recesses 63, 64 in such a way that the coil springs 48 are supported radially on the webs 49, at least under the influence of centrifugal force.

This is advantageous because the flange can be made of steel that is at least surface hardened, thereby reducing wear on the radial support areas for the springs 48.

As can be seen from Figure 2, spring cups 59, the circumference of which is adapted to the cross section of the ring-channel-like receptacles 51, are provided between the arms 44 or the circumferential stops 55, 55a and the ends of the springs 45 facing them.

The spring cups 59 have a slightly conical pin 59a that projects axially into the springs 45. The end 59b of the pin 59a is conical in the embodiment shown, but could also be designed like a dome. By designing the spring cups 59 in this way , if a cup protrudes from the end of the spring during operation ,

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slips, when the cup is re-loaded or the spring is relaxed, it automatically threads itself into the spring, so that the spring or the cup are not damaged. Spring cups 59 can escape if the outer springs 45 are compressed and the device 1 rotates at a relatively high speed. In this operating state, the friction between the spring coils of the springs 45 and the radial support areas of the housing halves 31, 32 for these springs can be so high that the springs 45 cannot at least fully relax in the event of a sudden load change shock. Due to the displacement of viscous medium caused by the radial arms 44 during the load change shock, which is distributed outside again under the influence of centrifugal force, spring cups 59 can be forced out of the ends of the non-relaxing springs 45.

Viewed over the circumference of the device 1, four springs 45 and 48 are provided, with the radially outer springs 45 each extending at least approximately over 78 degrees. The radially inner springs 48b extend at least approximately over 74 degrees and in the present case the springs 48e extend at least approximately over 68 degrees of the circumference. The outer springs 45 thus extend over approximately 86 % of the circumference of the device and the inner springs 48 over approximately 79 % of the circumference.

In the unassembled state, the springs 45 and/or the springs 48 - viewed in the axial direction - can be straight, which means that during assembly these springs are bent according to the shape of the recess that accommodates them.

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ings, or the springs 45 and/or the springs 48 can already have a corresponding curvature according to the shape of the recesses that accommodate them. By using pre-curved springs 45,48, the stresses that occur in them during compression can be reduced and assembly can also be made easier.

A viscous medium or a lubricant, such as silicone oil or grease, is provided in the annular chamber 30. The level of the viscous medium or lubricant can - when the device 1 is rotating - reach at least to the middle area or the axis of the outer springs 45 of the damper 13. In the embodiment shown, it is advantageous if this level reaches at least to the outer areas of the windings of the inner coil springs 48, so that at least at least between these windings and the areas which support them radially, in this case the webs 49 of the flange, there is lubrication which reduces wear. In the device 1 shown, it is advantageous if the filling of viscous medium or lubricant extends approximately to the axis ^of the inner coil springs 48.

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By assigning the annular chamber 30, which contains a viscous medium or a lubricant, to the flywheel element 3 connected to the engine and by spatially separating it from the flywheel element 4 carrying the friction clutch 7, the influence of the friction clutch 7 is prevented. The heat generated in connection with the friction clutch on the viscous medium or lubricant is largely eliminated.

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Furthermore, an outwardly open annular channel or annular gap 68 is provided between the annular chamber 30 or the housing part and the flywheel element 4, which in conjunction with ventilation channels 69 further improves the cooling effect. The air channels 69 are provided radially inside the friction surface 4a of the flywheel element 4 for the clutch disc 9.

As can be seen in particular from Figure 2, the flange 41 has a central recess 71, the contour of which forms radial profiles 72, which are in engagement with counter-profilings /3, which are provided on the outer circumference of the annular disk part 27 connected to the flywheel element 4. The profiles 72 and counter-profilings 73 forming the axial plug connection 42 enable a perfect alignment of the flange 41 between the two housing halves 31,32, so that between the annular passage 62 and the flange 41 existing gap 54 can be made very small. The plug connection 42 also makes it possible to expand the axial tolerances between the various contact or support surfaces of the components.

As can be seen in particular from Figure 1a, a seal 74 is provided between the radially inner region of the housing part 32 and the annular disk 27 or the axial projection 43 of the flywheel element 4 to seal the annular chamber 30. The seal 74 comprises an annular, axially resilient disk 75, which with its radial inner area is supported on an annular component 76 attached to the axial extension 43 and with its radially outer area on the radial

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inner area of the housing part 32 is axially fixed. The sealing disk 75, which can be axially deformed like a disc spring, has a coating 75a, 75b on its radially outer and inner areas, such as a plastic coating, which is applied, for example, by injection molding. These coatings 75a, 75b should have a low coefficient of friction and a certain elastic or plastic deformability. The radially outer edge area of the sealing disk 75 is flanged into a ring-shaped carrier 80 in a sealing manner. The flanged area of the outer area of the sealing disk 75 takes place in such a way that the sealing disk 75 can carry out a change in conicity. The areas 80b of the annular carrier 80, which encompass the outer circumference of the sealing disc 75, are accommodated in an axial recess or in an axial recess 77, which is formed on the radially inner area of the housing part 32. For axial fixing of the outer area of the sealing disk 75, the annular carrier 80 has flanged areas 60a, which radially surround the inner edge 32b of the housing part 32. The annular carrier 80 forms a circular ring-like pivot bearing for the sealing disk 75, which can be deformed like a disc spring.

The annular component 76, which eir.j with the sealing disc 75

cooperating sealing surface, has a radially inner disk-shaped area 76a, which is axially clamped between the end face of the axial extension and the disk-like component 27, and an annular outer area 76b, on which the sealing disk 75 with axial preload sealingly.

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The radially outer regions 76b of the annular component 76 are set back in the axial direction from the annular disk-like component having the counter-profilings 73 of the plug connection 42 relative to the radially inner regions 76a. As can be seen from Figure 1, the seal 74 seals the annular chamber 30 towards the annular gap 68 present between the two oscillation wheel elements 3 and 4.

In order to enable the two flywheel elements 3 and 4 to be axially connected, the inner diameter of the sealing disk 75 is larger than the outer diameter of the radial projections or the counter-profilings 73. The areas 76b of the annular component 76 on which the sealing disk 75 is axially supported extend radially outwards further than the counter-profilings 73.

The plug connection 42 and the seal 74 enable a particularly simple assembly of the torque transmission device 1, namely by first pre-assembling the two flywheel elements 3 and 4 and then axially connecting them to one another by axially plugging them together and fastening the locking disk 22 on the front side of the pin 20. To do this, the seal 74 is first pre-assembled on the flywheel element 3 and the roller bearing 16 is positively secured on the flywheel element 4. When assembling the two flywheel elements 3 and 4, the inner roller bearing ring 19 is pushed onto the seat 20a of the axial extension 20 of the housing part 31 and the counter profiles 73 are aligned with the Profilings 72 are brought into engagement. Furthermore, during the pushing together of the two flywheel elements 3 and 4, the radially inner

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area 75b of the sealing disk 75 for contact with the counter sealing surface 76b formed by the component 76, so that the sealing disk 75 is pivoted in itself like a disc spring and rests against the area 76b with pre-tension. The final axial fixing of the two flywheel elements 3 and 4 relative to one another is carried out, as already mentioned, by fastening the disk 22 to the pin 20.

To reduce wear in the contact area between the coils of the springs 45 and 48 and their associated recesses 52, 53 or 63,64 At least in these contact areas, the surfaces of the the parts 31,32 that delimit these indentations have a greater hardness. This can be done, for example, by induction hardening, case hardening, laser hardening or flame hardening these contact areas. In the case of very high stresses, however, it can also be useful s^in, if the parts 31, 32 delimiting the indentations have a coating that reduces abrasion wear, at least in the aforementioned contact areas. Such a coating can be formed, for example, by chemical nickel plating, by chrome plating or by coating with plastic or molybdenum. The applied coating can They can also be subsequently smoothed to achieve a better surface quality for the recesses against which the coils of the springs rub. Such smoothing can be achieved, for example, by a grinding process or by turning.

The operation of the device according to Figures 1, 1a and 2 is now described below.

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When the flywheel element 4 is rotated relative to the flywheel element 3 from the rest position shown in Figure 2, the flange 41 is driven via the plug connection 42, so that initially the inner springs 48b between the circumferential stops 65, 66 and the radial areas 50 are compressed. After passing through the relative angle of rotation 79 in one direction of rotation or 80 in the other direction of rotation, the radial areas 50 come to rest on the ends of the inner springs 48a, so that when there is a further relative rotation between the two flywheel elements 3 and 4, the springs 48a are compressed in addition to the springs 48b. After passing through the relative angle of rotation 79a in one direction of rotation or 90a in the other direction of rotation, the outer springs 45 are acted upon by the radial arms 44, so that with a further relative rotation the springs are compressed between the circumferential stops 55, 55a and the radial arms 44. In the illustrated In the embodiment shown, the angle 79 corresponds to the angle 79a and the angle 90 corresponds to the angle 90a, so that the springs 48a and the springs 45 are effective simultaneously. This results in a two-stage spring characteristic curve in the embodiment shown in Figures 1 and 2. The angles 79,90,79a,90a can, however, also only partially have the same amount or have different values, so that at least a three-stage spring characteristic curve in both directions of rotation or at least a two-stage spring characteristic curve in one direction of rotation and at least a three-stage spring characteristic curve in the other direction of rotation is possible.

- 36 -

- 36 -

Furthermore, the circumferential stops 65, 66, as indicated in Figure 2 by dash-dotted lines with 65a, can be set back relative to the spring ends of the springs 48b held back in the flange, so that then around the zero position of the relative rotation between the two flywheel elements 3 and 4 there is no suspension over a certain angle, and if necessary only hydraulic or viscous damping and/or frictional damping occurs.

In the embodiment shown, the joint compression of the springs 48a, 48b and 45 takes place until at least the inner springs 48a go into block, whereby the relative rotation between the two flywheel elements 3 and 4 is limited. In the case of a relative rotation between the two flywheel elements 3 and 4, frictional damping is generated by friction of the outer springs 45 on the surfaces of the indentations 52, 53 or on the steel band 81 and by friction of the sealing disk on the area 76b. Frictional damping also takes place between the radially inner springs 48 and their radial support areas. The frictional damping occurring between the springs 45, 48 and their radial support areas is speed-dependent, with this damping increasing with increasing speed. Furthermore , damping is generated by turbulence or displacement of the viscous or pasty medium contained in the annular chamber 30. In particular, the viscous medium present in the practically closed ring-channel-like receptacle 51 produces a hydraulic or viscous damping, since the spring cups 59 in the ring-channel-like receptacle act like pistons. When the outer springs 45 are compressed, the springs loaded by the arms 44 are

-Yl-

&bull; t * · J

- 37 -

impact spring cups 59 are moved in the direction of the cups supported on the circumferential stops · 55,35a, so that the viscous medium present in the springs is essentially forced through the gap 54, which acts like a throttle. Another part of the viscous medium is displaced between the spring cups 59 and the walls of the ring-channel-like receptacle 51. The viscous medium initially displaced inwards is again distributed evenly over the circumference as a result of the centrifugal force acting on it. During the relaxation of the outer springs 45, the viscous medium present on the side of the spring cups 59 facing away from the springs 45 is pressed past the spring cups in a similar way and displaced through the gap 54 and fills the springs 45 again as a result of the centrifugal force acting on them. The damping produced by the viscous medium depends on the centrifugal force acting on the medium, which means that the damping increases with increasing speeds.

The areas of the radially inner springs 48 immersed in the viscous medium also generate viscous or hydraulic damping through turbulence.

By introducing axial recesses or cutouts into at least individual cups and by appropriately dimensioning the gap 54 or the outer circumference of the cups, the damping produced by the viscous medium can be changed or adapted to the respective application. Furthermore, the viscous or hydraulic damping can be adapted by providing only some of the springs 45 with cups 59.

- 38 -

· t

- 3C -

Also, spring cups can be provided between the spring ends of at least one inner 48 and the radial regions 50 of the flange 41.

As can be seen in particular from Figure 2, the component 3a of the flywheel element* has radial arms 86 on the outer circumference, in each of which a threaded bore 87 is provided for fastening a friction clutch 7. Some of the arms 86 have bores 88 for receiving pins which ensure precise positioning of the clutch cover on the component 3a during assembly.

The radial arms 86 enable a lighter construction of the flywheel element 4 Furthermore, the radial recesses 86a between the radial arms 86 achieve better cooling of the component 3a and the clutch mounted on it, since air circulation can take place between the cover and the recesses 86a.

The radial arms 86 also make it possible, for a given mass, to make the component 3a thicker in the area of the friction surface 4a, so that overheating in this area can be avoided.

A change in the damping produced by the viscous medium can also be achieved by the ring-channel-like receptacle 51 not having a constant cross-section at least over partial areas of the length of at least ^one spring 45 , so that in the areas of larger cross-section a lower damping is produced and in the areas of smaller cross-section a higher damping is produced* Although this

- 39 -

&bull;t*
■ · *

- 39 -

Since a change in the cross-section of the ring-channel-like receptacle 51 can be provided at any location or even at several locations, it is particularly expedient if such cross-sectional changes or cross-sectional expansions are located in the end sections of the non-compressed springs 45. The cross-sectional changes can be sudden or progressive. It is particularly advantageous if the cross-sectional expansion is provided in the area of the radially inner half of the ring-channel-like receptacle 51. Such an expansion is shown in Figure 2 and marked with 89. This expansion 89 is formed on the flange 41, which limits or closes the ring-channel-like receptacle 51 radially inwards. The expansions can, however, also be formed by appropriate shaping of the indentations 52, 53 limiting the ring-channel-like receptacles 51.

The viscous medium can be introduced into the chamber 30 before assembly or joining the two flywheel elements 3,4. Such at least partial filling of the chamber 30 enables the viscous medium to be introduced through those areas of the chamber that are accessible by joining the flywheel elements 3,4. be closed.

To fill the chamber 30 with the viscous medium, which can be a pasty medium such as lubricant, grease or the like, the flywheel element 3 is brought to a speed which, due to the centrifugal force acting on the viscous medium, ensures a perfect distribution of this viscous medium over the circumference. This type of process ensures that when the chamber 30 is filled with

- 40 -

a pasty medium which, over the temperature ranges occurring, experiences as little or as little change in state as possible, i.e. at least no significant change in viscosity, establishes a uniform distribution or a uniform filling level over the circumference of the chamber 30, so that a very precise balancing of the device *g is then possible.

The spin speed can be between 4000 and 7000 revolutions per minute, preferably in the range of about 5000 to 6000 revolutions per minute.

The flywheel element 3 having the chamber can be balanced before assembly with the other flywheel element 4. The other flywheel element 4 can also be balanced on its own, so that after the two elements 3, 4 are put together, the device 1 is balanced. However, it can also be expedient if the balancing is only carried out after the two elements have been assembled.

The torque transmission device 101 shown in Figures 3 and 4 for compensating rotational shocks has a flywheel 102 which is divided into two flywheel elements 103, 104. The two flywheel elements 103 and 104 are mounted so that they can rotate relative to one another via a bearing 15. The flywheel element 103 forms a housing which delimits an annular chamber 130 in which a damping device 113 is accommodated.

&bull; t 4 ·
* ·

- 41 -

The flywheel element 103, which has the annular chamber 130, consists essentially of two housing parts 131, 132, which are connected to one another radially on the outside. The two housing parts 131, 132 are formed by sheet metal parts, which are connected to one another on their outer circumference by a weld 138. This weld 138 simultaneously seals the annular chamber 130 radially outward. A resistance butt weld or a capacitor discharge weld is advantageously suitable for welding the two sheet metal parts 131, 132, i.e. a weld in which the areas of two components that are in contact and are to be welded are heated to welding temperature by applying an alternating current of high current intensity and low voltage to the components and are joined under pressure.

To carry out such a welding, the two shell-like sheet metal parts 131,132 have front areas or abutting surfaces 134,135, which have a defined area in relation to the current intensity used for the welding. In the area of these abutting surfaces 134,135, the housing parts 131,132 lie axially against one another and are or are welded together. 20

For precise radial positioning of the two housing parts 131,132 during welding, the housing part 131 has an annular projection 131a on the outside, which surrounds a centering surface 135a formed on the outer circumference of the housing part 132. For precise positioning in the circumferential direction during welding, axial countersinks 165,166 are made in the housing parts 131,132.

- 42 -

- 42 -

165,166 can engage pins of the welding device, which hold the two housing parts 131,132 in a precise angular position in relation to each other during welding.

Since a certain axial movement occurs between the two sheet metal shells 131, L>2 during the welding process as a result of the formation of the weld seam, it may be advantageous to provide axial stops between these sheet metal shells which only become effective during the welding process. In Figure 3, a dash-dotted line of this type is shown on the sheet metal shell. The stop formed on the shell 132 is indicated and marked with 167. By using such limit stops 167, one is not so dependent on the current intensity used for welding, which means that one can also work with a higher current intensity, since the axial position of the two housing parts 131,132 is determined by the stops 167. and not by the current intensity and the axial pressure applied to the two housing parts 131,132 during welding.

The output part of the damper 113 is formed by a radial flange 141, which is arranged axially between the two housing parts 131, 132. The flange 141 is connected with its lateral inner region via an axial plug connection 142 to the annular disk part 127, which is fastened via rivets 126 to the front side of the axial projection 143 of the flywheel element 4 pointing in the direction of the motor-side housing part 131.

- 43 -

- 43 -

The flange 141 has radial arms 144 on its outer circumference, which form the loading areas for the force accumulators in the form of coil springs 145 of the damper 113.

The two housing parts 131, 132 form a ring-channel-like or torue-like receptacle 151 on the outside, into which the radial arms 144 of the flange 141 engage. The ring-channel-like receptacle 151 for the energy storage devices 145 is essentially formed by axial indentations or embossments 152, 153 extending over the circumference, which are made in the housing parts 131, 132 made of sheet metal and into which the areas of the energy storage devices 145 protruding on both sides of the flange 141 axially penetrate. The ring-channel-like receptacle 151 is closed radially inwards by an annular area 149 of the flange 141, apart from a small gap 154.

As can be seen from Figure 3, the axial indentations 152, 153 are designed in cross-section such that their arc-like course is at least approximately adapted to the circumference of the cross-section of the energy storage device 145. The outer areas of the indentations 152, 153 can thus form contact areas or guide areas for the energy storage device 145, on which the energy storage device 145 can be supported radially, at least under the influence of centrifugal force.

To reduce the wear on the radial support areas of the ring-channel-like receptacle 151 for the springs 145, a steel strip 181 with a high card is provided in the present case* which extends over

- 44 -

i &igr;

- 44 -

the circumference of the ring-channel-like receptacle 151 and encloses the springs. In the embodiment shown, the steel strip 181 is cylindrical and accommodated in a recess 182, which is formed by a radial recess or a radial recess. When the device 101 rotates, the springs 145 are supported on the steel strip 181 via their windings as a result of the centrifugal force acting on them.

To act on the energy storage device 145, circumferential stops 155, 155a are inserted into the recesses 152, 153 on both sides of the arms 144. In the embodiment shown, the circumferential stops 155, 155a - viewed in the circumferential direction - have the same extent as the radial arms 144 of the flange 141. As can be seen from Figure 4, intermediate parts in the form of spring cups 159 are provided between the arms 144 and the ends of the springs 145 facing them, the circumference of which is adapted to the cross section of the ring-channel-like receptacle 151.

Radially within the ring-channel-like receptacle 151, the housing halves 131, 132 have regions 160, 161 facing one another, forming annular surfaces, between which a ring-shaped passage 162 for the flange 141 is present.

In the illustrated embodiment according to Figures 3 and 4, the width of this circular passage 162 is only slightly larger than the areas of the flange 141 accommodated in it, so that a very small gap 154 is present.

&bull; I · t

- 45 -

As can be seen from Figure 4, four springs 145 are provided over the circumference of the device, each of which extends at least approximately over 82 degrees of the circumference. The springs therefore extend over at least approximately 90 % of the circumference of the device 101. 5

To reduce the stresses occurring in the springs 145 during compression and to facilitate assembly, the springs 145 are pre-curved at least approximately to the radius on which they are arranged.

A viscous medium or a lubricant is provided in the annular chamber 130. The viscous medium should - when the device 101 is rotating - at least fill the annular channel-like receptacle 151.

As can be seen from Figure 4, the flange 141 has a central recess 171, the contour of which forms radial profiles 172 which engage with counter-profiles 173 which are provided on the outer circumference of the annular disk part 127 connected to the flywheel element 4. The counter-profiles 173 are formed by radial projections which engage in correspondingly adapted cutouts 172a of the flange. In the area of the radial projections 173, the rivets which fix the component 127 to the flywheel element 104 are also provided. The profiles 172 and counter-profiles 173 forming the axial plug connection 142 enable the flange 141 to be perfectly aligned between the two housing halves 131, 132, so that the gap 154 between the annular passage 162 and the flange 141 can be made very small.

- 46 -

The plug connection 142 also makes it possible to extend the axial tolerances between the various contact or support surfaces of the components.

To seal the annular chamber 130, a seal 174 is provided between the radially inner region of the housing part 132 and the flywheel element 10α. The seal 174 differs from the seal 74 described in connection with Figure 1a essentially in that the annular axially resilient disk 175 is completely coated and is axially clamped radially on the outside between an annular region 132a of the housing part 132 and an annular disk 180 fastened to the housing part 132 by means of rivet connections 132b.

The annular region 132a of the housing part 132 extends radially inward from the outer diameter of the resilient sealing disk 175, a radial space 132c being formed between the annular region 132a and the sealing disk 175. In this radial space 132c, which is open radially inward, the small amounts of viscous medium which may possibly escape between the inner region of the sealing disk 175 and the non-sealing regions 176b can be collected and, at higher speeds - due to the centrifugal force - pressed back into the annular chamber 130 between the annular region 132a and the sealing disk 175. The contact zones between the inner regions of the sealing disk 175 and the non- sealing regions 176b are provided in the axial extension region of the radial space 132c .

- 47 -

- 47 -

An axial recess or an axial shoulder 191 is formed on the inner region of the housing part 132, the radially outer surface of which axially overlaps the outer regions of the sealing disk 175.

The housing half 131 facing the engine has an axial projection 120 on the inside, on which the roller bearing 16 supporting the two flywheel elements 103 and 104 relative to one another is accommodated in a similar manner to Figure 1a. The sheet metal part 131 is centered on a seat 120b of the projection and is supported axially on a radial surface 120c of the projection 12C provided at the connection to the seat 120b.

The connection between the sheet metal part or housing part 131 and the axial extension 120 can be made by screwing, riveting, welding or caulking.

The assembly of the two flywheel elements 103 and 104 is carried out in a similar manner to that described in connection with Figures 1 and 2, which means that the roller bearing 16 is first pre-assembled on the flywheel element 104 and the sealing disk 175 on the flywheel element 103. When By pushing the roller bearing 16 onto the seat 120a of the projection 120, the plug connection 142 is created and the sealing disk 175 is axially clamped by contact with the counter sealing areas 176b provided on the flywheel element 104. By fastening the locking disk 122, which radially overlaps the inner bearing ring of the roller bearing 16, on the front side of the projection 120, both flywheel elements 103 and 104 are axially

- 48 -

- 48 -

secured to each other. The disk 122 can be attached by riveting, similar to that shown in Figure 1. However, screws can also be used instead of rivets.

The hydraulic or viscous damping by displacement or turbulence of the viscous medium provided in the ring-channel-like receptacle 151 takes place in a similar manner as described in connection with Figures 1 and 2.

To prevent welding of the two sheet metal housing parts

131,132 the components in contact with these - such as in particular the movable components - are welded to the housing parts in places or experience a structural change as a result of local overheating, there is a gap between these components and the sheet metal housing Electrical insulation is provided for the parts 131,132. The components at risk during the welding process are in particular the springs 145 located in the ring-channel-like holder 151, the flange 141 and the spring cups 159.

The insulating coating can be provided on the housing parts 131,132 and/or on the components 145,141,159,155,155a that are in contact with them. The insulating coating can only be applied partially, that is, only in the contact areas between the housing parts and the other components

- 49 -

- 49 -

The insulation can be achieved advantageously by phosphating one of the components. Furthermore, individual components, such as the spring cup 159 and the circumferential stops 155, 155a, can be made of non-conductive material. 5

It is particularly advantageous if at least the sheet metal parts and/or the flange are phosphated for insulation. The springs 145 are preferably painted, but can also be phosphated.

In order to insulate the housing parts 131, 132 from the components in contact with them, ceramic layers, plastic coatings or even grease coatings can also be used. Such coatings can be applied in particular to the housing parts 131, 132.

If the sheet metal parts 131,132 are completely coated during the insulation treatment, such as phosphating, it is advisable if, in the area of the welding zones and in the area for the power supply, the insulating layer previously applied in these areas is covered, for example, by a mechanical processing, so that perfect electrical conductivity is present in these areas.

When selecting the insulating materials, it must always be ensured that they are compatible with the viscous medium introduced into the ring-channel-like receptacle 151.

- 50 -

- 50 -

The use of a phosphate layer as an insulating layer is particularly advantageous as it reduces wear and is self-lubricating.

The housing part 131 also has a seat 139 on the outer circumference, on which a starter ring gear 140 is accommodated. The starter ring gear is connected, at least in places, to the housing part 131 by a weld 140a over the circumference. This is advantageous when the housing part 131 is made of sheet metal, since due to the limited wall thickness of the housing part 131, the seat 139 does not extend over the full width of the ring gear.

As can also be seen from Figure 3, the motor-side housing part 131 has a greater material thickness than the housing part 132.

The circumferential stops 155,155a can be replaced by molded-on features such as pockets embossed into the sheet metal parts 131,132. These pockets can be used advantageously to position the two housing parts 131,132 when welding them together.

The invention is not limited to the embodiments shown and described, but also includes variants that can be formed by combining individual features or elements described in connection with the various embodiments.

Claims (1)

I · · 1 · I LuK slats and
Clutch Construction GmbH
Industriestrasse 3 7580 Bühl / Baden 0535/32 1. Device for damping torsional vibrations, e.g. in the drive train of a vehicle, wherein the device has at least two flywheel masses mounted opposite one another by damping means via a roller bearing, one of which can be connected to an engine and the other to a transmission via a coupling, such as a friction clutch, and at least one of the flywheel masses has a chamber that can be at least partially filled with a viscous or pasty medium and sealed to the outside by at least one seal, in which a damping device is accommodated that resists relative rotation between the flywheel masses, characterized in that the assembly of the device takes place in that two pre-assembled sub-units are designed in such a way that they can be joined axially and connected to one another via a connecting means and the sub-units have at least two of the following features: I · tt did· tie· * * a sealing element is fixed to one of the sub-units, which, after assembly, rests against a counter sealing surface provided on the other unit, - the rolling bearing is positively fixed to one of the sub-units and is mounted on a seat of the other sub-unit during assembly. - one of the sub-units carries one component of a plug connection, which has a profile, and the other unit carries the counter-profile of a plug connection that couples the two units in a rotationally locked manner. 2. Device according to claim 1, characterized in that the flywheel mass connectable to the engine has the chamber and the damping device and thus represents one pre-assembled unit, while the other pre-assembled unit contains the flywheel mass connectable to the transmission. 3. Device according to claim 1 or 2, characterized in that an output part of the damping device has profiles which can be brought into engagement with counter-profiles provided on one of the units, furthermore one of the units carries the sealing element which, when the two units are put together, is surface of the other unit comes into contact with the surface in a sealing manner. ' I , , , I ■ 1 II > 1 > · &igr; «*t*t· · t I I 1 I · · · · 4. Device according to one of claims 1 to 3, characterized in that the seal created by the assembly of the two units seals the chamber at least partially filled with viscous medium towards a space axially between the chamber and a the flywheel masses, which can be open to the outside. 5. Device according to one of claims 1 to 4, characterized in that the damping device in the circumferential direction effective force storage and the output part is a flange-like component which interacts with these and has a central recess whose circumferential contour limits the profiling. 6. Device according to one of claims 1 to 5, characterized in that the counter-profilings are provided on the other flywheel mass. 7. Device according to claim 6, characterized in that the counter-profiling is on the outer circumference of a ring-disk-like, with the other flywheel connected component. 8. Device according to claim 6 or 7, characterized in that ^the ring-disk-like component is axially fixed on a front surface of the other flywheel mass facing the motor-side flywheel mass. is. ·&diams; »■> *· te &Mgr;&igr;* cct i tC 9. Device according to one of claims 1 to 8, characterized in that before the axial assembly of the units, the rolling bearing is provided on the flywheel that can be connected to the gear. 10. Device according to one of claims 1 to 9, characterized in that the bearing is accommodated in a central recess of one of the flywheel masses and is clamped axially between a shoulder of this flywheel mass and the ring-disk-like component. 11. Device according to one of claims 1 to 10, characterized in that the flywheel on the motor side has a central axial projection which projects axially into the recess of the other flywheel and has a seat for receiving the inner ring of the rolling bearing. 12. Device according to one of claims 1 to 11, characterized in that after the axial assembly of the two flywheel masses the inner roller bearing ring is secured by a ring which at least partially radially overlaps it and is arranged on the front side of the axial projection axially fixed ring disk representing the connecting element is axially secured. 13. Device according to claim 12, characterized in that the inner roller bearing ring between the ring disk and a shoulder of the axial len approach is clamped. 14. Device according to one of claims 1 to 13, characterized in that at least on the side of the bearing facing away from the chamber a seal is provided which acts between the radially outer and radially inner bearing ring. 15. Device according to one of claims 1 to 14, characterized in that a seal is provided on the side of the bearing facing the chamber, sealing the chamber against the bearing. 16. Device according to claim 15, characterized in that the seal is effective between the two bearing rings. 17. Device according to claim 15 or 16, characterized in that a sealing element can be pre-assembled on one of the units, which after assembly rests against a counter sealing surface provided on the other unit. 18. Device according to claim 17, characterized in that the sealing element can be pre-assembled on the unit containing the transmission-side flywheel. 19. Device according to one of claims 1 to 18, characterized in that a seal is provided between at least one of the bearing rings and the component supporting it. 20. Device according to one of claims 1 to 19, characterized in that the sealing element is formed by at least one annular disk-like sealing part. 21. Device according to claim 20, characterized in that the annular disk-like sealing part is axially resilient. 22. Device according to one of claims 1 to 21, characterized in that the sealing element is carried by the flywheel on the engine side and, after the flywheels have been put together, rests against the contact surface of the other flywheel with pre-tension. 23. Device according to one of claims 1 to 22, characterized in that the inner diameter of the sealing element sealing the chamber towards the annular gap is larger than the outer diameter of the counter-profilings of the plug connection. 24. Device according to one of claims 1 to 23, characterized in that the sealing element rests axially with its radially outer edge region on a radial wall delimiting the chamber, which is provided axially between the disk-like output part of the damping device and the second flywheel mass. 25. Device according to claim 24, characterized in that the radially outer edge region is axially fixed to the radial wall. -, ' 26. Device according to at least one of the preceding claims. &bull; , characterized in that the on the other of the flywheel masses The intended contact surface for the sealing element is formed by a circular ring-shaped component which is clamped axially between the end face of the other flywheel mass and the component having the counter-profilings and extends radially outwards further than the counter-profilings. 27. Device according to claim 26, characterized in that the circular ring-shaped component extends radially outward in the direction of the The component with the profiles is offset. 28. Device according to one of claims 1 to 27, characterized in that the viscous medium is introduced into the chamber before assembly IS of the units is introduced. 29. Device according to one of claims 1 to 28, characterized in that the viscous medium is introduced through those areas of the chamber which are used during assembly of the flywheel masses. are closed. 30. Device, in particular according to one of claims 30 or 31, characterized in that the unit having the chamber is brought to a spin speed which effects the distribution of the viscous medium.