DE4420927A1 - Torque transmission device - Google Patents

Abstract

The invention relates to a torque transmission device with at least two flywheel masses which can be rotated relative to one another by way of a bearing counter to the action of a damping device with energy storage means acting in the circumferential direction. Of these masses, the first can be connected to the output shaft of an internal combustion engine and the second can be connected via a friction clutch to the input shaft of a gearbox.

Description

The invention relates to a torque transmission establishment with at least two against the effect of one Damping device with acting in the circumferential direction Energy storage can be rotated relative to one another via a bearing Inertia, of which one - first - with the Ab drive shaft of an internal combustion engine and another - second - via a friction clutch with the drive shaft a transmission is connectable.

The present invention was based on the object Torque transmission devices that create themselves due to a small space requirement in both axial and Mark in the radial direction. Furthermore, it should Open up the possibility of a given installation space largest possible effective friction diameter of the friction to realize coupling or if necessary Friction diameter the dimensions of the overall unit compact to keep. Furthermore, it is an object of the invention Lifetime of such torque transmission devices increase and thereby their reliable use, for example to enable wise in motor vehicles.  

This is achieved according to the invention in that the Lift mechanism radially within the friction surface of the friction coupling in an at least substantially closed, arranged in the circumferentially extending chamber are.

Another object of the invention is based therein, the torque transmission device as a unit the output shaft of the internal combustion engine as possible simple way to attach. In addition, a inexpensive and economical manufacture and a the same assembly of such torque transmission facilities may be possible.

Furthermore, the invention was based on the object Reduce number of individual components and continue over the least possible use of materials and one possible low material waste also natural resources protect and by reducing machining processes the environment both through energy saving and through a reduction in processing additives used to date spare.

Another object of the invention is based therein the components of the torque transmission device to protect them from excessive moments and thereby a transfer of these overtorques into that of the torque transmission device downstream transmission  other.

In a torque transmission according to the invention direction, it can be advantageous if the chamber has the Energy storage at least in the radially outer area closes.

Furthermore, it can be useful if the chamber at least in the radially outer area to the contour of the energy accumulator nestled.

As advantageous for the formation of an inventive Torque transmission device it may turn out if the chamber is formed from at least two walls, at least one with the second flywheel connected is.

In general, it can be useful if at least one of the Chamber walls carries the second flywheel.

For a torque transmission device according to the invention it can be advantageous if, for. B. depending on the Requirements, the storage as a plain bearing or else, in other cases, as rolling bearings.

It can be advantageous if the energy storage under Ver Coil springs are formed, the  Use of leg springs can be useful.

In a torque transmission device according to the Invention may prove advantageous if the Chamber essentially sealed at least radially on the inside and at least partially with dry lubricants such as For example, graphite powder, is filled, where purpose can be moderate if the chamber has a labyrinth tung, so z. B. is dustproof, sealed.

A torque transmission device according to the invention can advantageously be constructed such that the chamber at least essentially sealed and with a viscous / pasty medium is at least partially filled, whereby a fat space formed by the chamber radially within the Friction surfaces of the friction clutch is arranged.

Furthermore, it may prove useful to store to be placed inside the chamber, thereby reducing storage Has lubricant contact, or within the grease room is arranged.

In general, it can be advantageous if the bearing is radial is arranged within the energy accumulator.

An advantageous embodiment of an inventive Torque transmission device can provide that the cover plate forming the second chamber wall radially outside the  Lift mechanism with the one that forms a chamber wall Cover plate, for example by welding or Flanging is firmly connected, which in turn is useful can be the connection using an O-ring to seal between the chamber walls.

A torque transmission device according to the invention can be characterized in that the chamber walls forming cover plates for the application areas Have energy storage, the expediently Areas of application by directed towards each other axial impressions can be formed, the axially in Zwi spaces protrude between the energy stores.

It can be particularly advantageous if at a torque ment transmission device according to the invention the deck sheets are connected to the second flywheel, whereby it can prove to be useful if the cover plates the side of the second Schw are articulated, i.e. the counter pressure plate behind to grab.

The cover plates can be shaped with the second flywheel connected conclusively or frictionally or non-positively his.

In general, it can be with a torque transmission device tion can be of particular advantage when limiting torque  tion organ or a slip clutch in such a way in the power transmission supply path is provided that the torque flow - from the engine Seen here - from the first flywheel over an in immersing the chamber, loading the energy accumulator Flange part, to the lift mechanism, from there to the Chamber walls, from there to the radially outside of the Energy storage provided, but radially within the or only slightly in the radially further out Friction area of the friction clutch immersing the friction surface of the Torque limiting device and from there to the second swing mass is done.

Furthermore, it can be advantageous if the frictional Connection is axially biased, with a plate spring Apply the axial force required for the axial preload can.

It can be useful if this axial force by actuation supply of the plate spring is changeable, it being advantageous can be if the actuation of the plate spring by the first flywheel mass. The actuator for this can be made in one piece with the first flywheel his.

It can prove to be advantageous if a Torque transmission device according to the invention Cover plates with the second flywheel under the intermediate layer of friction material are connected, the friction material  can also form thermal insulation.

It can also be advantageous if a chamber wall-forming cover plate is supported by the bearing, or can be supported on the storage.

It can be particularly advantageous for an inventive one Torque transmission device when the force on the other hand, support the storage at the application areas, the flange (s) protruding into the chamber are arranged, the radially within the energy accumulator is / are connected to the first flywheel, whereby it can be useful if the connection of the flanges or the flange with the first flywheel using fastening screws that are used for Connection of the first flywheel or the Torque transmission device with the output shaft of Serve internal combustion engine.

An expedient embodiment of a torque transmission The supply device according to the invention can have two flanges provide that firmly in the area of their outer diameter are connected.

It can also be advantageous if the two flanges in the Area of attachment of the device to the crank Shaft-serving screws lie against each other.  

It can also prove useful if the two Flanges in the radial area between the fasteners supply screws and their outer diameter axially from each other are spaced.

In general for torque transmission devices it can be of particular advantage if the application areas associated with the first flywheel Flanges or the flange connected to it on force accumulators formed by coil springs are adapted, the spring end turns are essentially equal to their spring center turns are formed. The Spring ends are therefore neither created nor attached grind, but only cut off or "chopped off".

It may also be useful to apply the areas of the flange or flanges for graded internal and external springs graded.

It can also be advantageous if the cover plates are graduated te application areas for interlocking interior and Have external springs, these areas of application expediently be formed by a double feed can.

In a torque transmission according to the invention direction, it can prove to be advantageous if the first flywheel and a flange to each other directly  are centered over a seat.

It can also be beneficial if a flange has a zen Trier seat for centering the torque transmission direction on the output shaft of the internal combustion engine having.

For example, to set up a torque transmission device according to the invention it may be appropriate if a flange supports the bearing.

It can be particularly advantageous if an invention torque transmission device according to two flanges Acting on the energy accumulator, one of which for fastening the torque transmission device to the Output shaft of the internal combustion engine, for centering it the output shaft, to accommodate the bearing and Centering the first flywheel serves.

An advantageous embodiment of a torque transmission supply device according to the invention can be a radially inside horizontal chamber sealing by means of a plate spring Have like component, the one hand with a Chamber wall forming cover plate or a ver with this bound component and on the other hand with this adj beard flange or a component connected to it cooperates.

Appropriately z. B. for a manufactured as a pre-assembled module  Torque transmission device can be, if with a flange-connected component that is connected to the diaphragm spring interacts like a seal to fix the fastener screws.

It can be advantageous if a cover plate is off Take the passage of the mounting screws or Passage of a tool for actuating the fasteners supply screws, which in turn may be appropriate can, if the recesses are surrounded by a collar, the interact with one of the cup spring type seals can.

The cup-spring-type seals can also tear represent damping device, the inexpensive is feasible.

An advantageous embodiment of a torque transmission supply device according to the invention can thereby distinguish that the energy accumulator or the chamber and the friction surface of the Rei arranged on the second flywheel Exercise clutch in the same axial area, that is, each other axially overlapping are arranged.

Furthermore, it can, for example, favor compactness of the overall unit can be advantageous if the storage and the heads of the mounting screws in the same axial Area are arranged.  

Particularly advantageous for a torque according to the invention It can be a transmission device if the energy accumulator (or the chamber) in the radial direction between the heads of the Fastening screws and the on the second flywheel arranged friction surface of the friction clutch are arranged (or is).

It may be appropriate for a torque transmission device according to the invention a wall on the Heads of the fastening screws facing the side of the Chamber.

In general, it can be a particularly advantageous one Embodiment of a torque transmission device by the radial order of at least four of the seven mark the following components:

• - Profile of the gear shaft
• - storage
• - Heads of the fastening screws
• - Radially inner chamber wall
• - Lift mechanism
• - Radially outer chamber wall
• - friction surface of the second flywheel,

the arrangement of the components on different Diameter ranges that do not overlap can.

It may also be useful if the (at least  four) components are arranged in the same axial region.

In a torque transmission according to the invention direction, it can prove to be particularly advantageous if the storage is radial within the heads of the fastener supply screws is arranged.

An arrangement of the heads of the mounting screws between Storage and energy storage can also be advantageous like a structure of a torque transmission device, at which the lift mechanism and the heads of the fastening screw ben adjacent and arranged in the same axial area are.

Furthermore, it can be useful if the chamber (with) forming wall radially between the energy stores and the heads of the fastening screws is arranged.

For some applications it can be an advantage if the storage radially outside the heads of the attachment screws is arranged.

In a torque transmission according to the invention direction, it can be particularly beneficial if the force store the damping device a ratio of length to have diameters in the range from 4 to 10, ie a have a large length-diameter ratio.  

Furthermore, it can be beneficial if the strength memory over an area of the circumference that between 70% and 95%, preferably around 80% to 90%, lies.

It can prove useful if at least an energy accumulator extends over a sector of the circumference, which is greater than 140 °.

In a torque transmission device according to the Invention, it can be particularly advantageous if the Lift mechanism at least approximately to that radius are curved, which corresponds to the installed state.

A torque transmission device according to the invention can in various embodiments, a plurality of springs have levels.

In general with torque transmission devices it can turn out to be particularly advantageous when using power spit chern in the form of coil springs whose end spring turns in essentially their intervening spring turns ent speak, so neither sanded nor applied, but only in the area of a plane approximately perpendicular to the wire cross section are cut or "chopped off".

A torque transmission device according to the invention can expediently wear protection between the  Energy storage and the radially outer chamber wall have, on which the energy storage at least below Support centrifugal force.

In a torque transmission according to the invention direction, it may prove useful to use the lid the friction clutch on the second flywheel wear.

Furthermore, it can be advantageous if the lid of the Friction clutch engages axially around the second flywheel, the cover of the friction clutch on the second Flywheel with its axially extending and the swing mass-encompassing area can be centered.

In a torque transmission device according to the Invention, it may be appropriate if the lid with the second flywheel via a welded joint, so is inseparable or inseparable.

However, it can be useful for further embodiments be, the cover with the second flywheel separable connect, for example using screws or pins.

It can also prove useful to have a torque Form transmission device so that the lid itself is separable, for example similar to that in the German patent application P 42 32 320 is described in order  e.g. B. to be able to replace the clutch disc.

In a torque transmission device according to the In the present invention, it may be advantageous to use the Trä gerblech the clutch disc of the friction clutch at least essentially adapt to the contour of the chamber.

Corresponding torque transmission devices can advantageously also a lubricant deflector and / or a lubricant deflection contour on the carrier plate Clutch disc and / or on the one facing it Chamber wall forming cover plate in the area of the Have recesses in the cover plate.

It may prove useful if the carrier plate the clutch disc recesses for the passage of the Fastening screws or for the passage of a tool for actuating the fastening screws.

In a torque transmission device in which the Pressure plate of the friction clutch by an annular plate spring with base body and tongues is beatable, it can be advantageous if the contour of the Disc spring to that of the clutch plate support plate at least in the position, in the plate spring and carrier sheet are approximated to each other, at least approximately adapted is, the plate spring is expediently in the area their tongues recesses for the passage of the attachment  screw or for the passage of a tool for actuation the fastening screws.

In general, it can be with torque transmission equipment lines can be particularly advantageous if the disc spring Recesses for the passage of on the pressure plate Has friction clutch arranged pressure plate cams, the recesses in a simple manner by at least partial absence of tongues can be formed.

It can be particularly advantageous for torque transmission facilities to be more general when the leaf springs that turn the pressure plate with the cover of the friction clutch connect firmly, but axially displaceable, on which the Pressure plate facing away from the lid are arranged.

Furthermore, for example with regard to the axial Installation space, be useful if the pressure plate on your the opposite side of the contour of the friction surface Cover-side plate spring mounting is adjusted, so for example, has a recess into which the Tel spring bearing means (wire ring (s) and its (their) Holding means) in disengaged condition of the pressure plate immerse at least partially axially.

It can also be advantageous if the pressure plate and parts of the cover-side plate spring bearing axially and radially in the disengaged position of the friction clutch  cover, so that the plate spring bearing in appropriate Can depressions of the pressure plate.

An advantageous embodiment of an inventive Torque transmission device can be carried out in this way be that the cover-side disc spring bearing by a tabs made in one piece with the lid are formed, the pressure plate expediently on its the friction flat opposite side of the contour of the tabs can be adapted.

Furthermore, it can be particularly advantageous if a torque transmission device according to the invention the first flywheel at least partially to the contour of the its facing areas of the chamber is adapted.

It can be advantageous, for example in terms of costs be when the first flywheel is predominantly made of sheet metal (parts) is manufactured.

It may also prove useful if the first flywheel carries the starter ring gear.

The starter ring gear can advantageously by folded sheet metal part be formed, the walls of one another other concerns, such as this B. in the German patent registration P 43 15 209 is described.  

It may also be appropriate to insert the starter ring gear Execute in pieces with the first flywheel.

It can increase the primary moment of inertia be advantageous if the first flywheel mass of the torque ment transmission device has a ground ring, wherein the earth ring by a casting or by a folded tes sheet metal part can be formed.

Of particular advantage in a torque transmission Direction according to the invention, it can be when the ground ring engages around the axial area of the clutch cover and this at least partially covered in the axial direction.

It can prove beneficial if the damping device of the torque transmission device a load Has friction device, this advantageously radially outside the energy accumulator or radially outside outside the average friction diameter of the friction clutch can be arranged.

In general, it can be with torque transmission equipment lines be advantageous if the load friction device too at least one friction part with two radially spaced friction contains areas.

In addition, the friction part can be the friction connection with the first Have a flywheel.  

It can be useful if the friction part of a Beauf Impact part of the second flywheel is acted upon.

With such friction devices, it can be advantageous if the friction parts and loading parts in circumference direction to have a game.

Here, several friction parts with different play be provided in relation to the loading parts.

An expedient structure of a torque transmission direction can provide that an axially extending area the cover of the friction clutch part of the load row is.

It may also be advantageous to use the first ring Inertia as part of the load friction device to use.

Advantageously, the load friction device in the Be arranged in the area where the ground ring is axial Around the clutch cover.

For example, for the function of the hysteresis device it can be advantageous if the load friction device too has at least one energy store, the force can act in the radial direction.  

It can prove beneficial with a torque Transmission device according to the invention the Lastreibein direction by at least one in the first flywheel arranged to form friction shoe, it being useful can, if the friction shoe is simply clipped on.

It can be advantageous here if the Lastreibeinrich tion has several friction shoes distributed over the circumference.

For example, for defined friction properties it can be from Be advantageous if at least the friction surface (s) of the friction schuhes / the friction shoes made of plastic, such as B. PTFE, PEEK, PA6.6.

For e.g. B. the durability of an inventive Torque transmission device can do it especially be parous if the carrier plate of the clutch disc and / or the disc spring further recesses, in particular for ventilation of the torque transmission device, exhibit.

Furthermore, it can be useful for this purpose, ventilation opening in the axial or radial area of the cover to provide the friction clutch.

It can also be beneficial to have ventilation openings in the first flywheel or also in the second flywheel - there radially outside the chamber - to be provided.  

A torque transmission device according to the invention can advantageously by means of ventilation an air flow through the carrier plate of the clutch disc through, along the chamber wall, through openings in the second flywheel outside the Mark the chamber towards the first flywheel.

To further improve the temperature conditions can a torque transmission device according to the invention Ventilation openings in the first flywheel for one the chamber wall to be directed and on the second swing have mass of air flowing past.

Furthermore, it can be advantageous to have ventilation openings in the first flywheel mass for one on the second flywheel to provide directed airflow.

An advantageous embodiment of a torque transmission supply device can increase surface area for verbs Heat dissipation on the surface facing away from the friction surface Side of the second flywheel or on the friction surface che side facing away from the pressure plate, the for example, through impressions, depressions Annular cutter or the like can be formed.

It can be useful if the surface enlargement and / or ventilation openings like a fan blade forms are.  

A preferred embodiment of a torque transmission supply device according to the invention can be designed in this way be that the torque transmission device with Rei Exercise clutch and clutch disc a pre-assembled Unit forms, as such with the mounting screws from the side facing away from the motor to the output shaft the internal combustion engine can be screwed, the given if necessary, captive fastening screws in the unit may be included.

A torque transmission device according to the invention can advantageously both with a friction clutch so-called pressed clutch, as well as with such be designed as a so-called drawn clutch.

In general, it can be with torque transmission devices be advantageous, the second flywheel, the moment boundary organ / the slip clutch and the circumferential direction to arrange acting energy accumulator in radial alignment, whereby the energy storage in a substantially closed, be arranged in the circumferentially extending chamber can.

An expedient embodiment of an inventive Torque transmission device can by the radial aligned alignment of the storage must be marked.

An advantageous form of torque transmission  direction can be carried out in such a way that the torque boundary element / the slip clutch radially between the forces save and the second flywheel is arranged.

The invention is explained in more detail with reference to the figures:

Show:

Fig. 1 shows a section through a torque transfer device,

Fig. 2 is a partial view of a torque transmitting device according to the invention in the direction of arrow II in Fig. 1,

Fig. 3 shows a possible spring arrangement in view,

Fig. 4 shows the arrangement of a friction device cut in the part,

Fig. 5 is a friction shoe in the other embodiment of the friction device of FIG. 4,

FIGS. 6 to 8 are sections or sub-sections of further devices according to the invention formed torque transmission,

Fig. 9 is a simplified partial view in Rich processing of the arrow, it IX in Fig. 8,

Fig. 10 is a partial sectional view of another fiction, formed in accordance with the torque transmission device,

Fig. 11 is a partial section according to the arrow XI in Fig. 10,

Fig. 12 is a partial section according to arrow XII in Fig. 10,

Fig. 13 and 14 are partial sectional views of further fiction, designed according Drehmomentübertragungseinrichtun gene.

In Fig. 1, a divided flywheel 1 is shown, which has a first or primary flywheel mass 2 that can be fastened to a crankshaft of an internal combustion engine, and a second or secondary flywheel mass 3 . On this second flywheel 3 , a friction clutch 4 is fixed with the interposition of a clutch disc 5 , via which a gear, also not shown, can be closed and uncoupled. This clutch disc 5 is shown rigidly here and serves only as an example. For example, this clutch disc 5 can also comprise further designs which contain friction and / or damping elements or can also be equipped with a pad suspension.

The flywheels 2 and 3 are in this case with interposition of components firmly connected to them via a bearing 6 rotatably mounted to each other, the radially in this example executed within the holes 7 for carrying out fastening screws 8 for the assembly of the first flywheel 2 and the Entire torque transmission device 1 is arranged on the output shaft of an internal combustion engine. The single-row ball bearing 6 shown here has a sealing cap 6 a with a lubricant storage chamber, the sealing cap 6 a also serves as thermal insulation by reducing a heat flow from the second flywheel 3 to the bearing 6 or by preventing a thermal bridge. Between the two centrifugal masses 2 and 3 , a damping device 9 is effective, which in this case has helical compression springs 10 which are arranged in an annular space 11 which forms an approximately toroidal region 12 . The compression springs 10 used and shown here can also be replaced by suitable, differently designed energy storage elements, such as leg springs. The annular space 11 is at least partially filled with a dry lubricant, such as graphite powder or the like, or with a pasty viscous medium, such as oil or fat.

The primary flywheel mass 2 has a component 13 , which can preferably be made or drawn from sheet metal material, this component 13 serving to fasten the first flywheel mass 2 or the entire divided flywheel 1 to the output shaft of an internal combustion engine or a shaft connected to it. The component 13 forms a substantially radial flange-like area 14 , which carries a flange 15 radially on the inside, the areas 15 a extending in the radial direction with the recesses 7 aligned holes or through openings for the fastening screws 8 . The one row rolling bearing 6 is included with its inner ring 16 on an outer surface or support shoulder in the axial end section 15 b of the flange 15 . On the outer ring 17 of the bearing of the bearing 6 , the second flywheel 3 is supported .

The essentially radially extending area 14 merges radially on the outside into an area 18 which is potted axially on the engine side, which in turn merges radially on the outside into a radially extending area which is axially further apart from the engine and forms the starter ring gear 19 . To form the starter ring gear 19 , its material is deformed and folded in the radially outer region of the sheet metal body 13 , so that a leg 20, which in turn is directed radially inward, is formed, which in turn rests with its wall against the radially outer portion of the sheet metal body 13 . The profiling or the teeth of the starter ring gear 19 can be brought into this sheet metal part after folding the sheet. These profiles can be created by machining, such as milling or broaching. The profiles of the starter ring gear 19 can, however, also be formed by stamping, that is, by a flow process in the material. Furthermore, these profiles can be produced by stamping. Another possibility for producing such profiles is to cut them out using high-energy beams, such as laser beams. It can be advantageous if, at least in the area of the profiles or the toothing of the starter ring gear 19, the corresponding sheet metal parts have a greater hardness than in the other areas. Such a partial or partial increase in hardness can be achieved, for example, by induction hardening or case hardening.

To increase the moment of inertia of the dual mass flywheel 1 rotating about its axis of rotation, the primary flywheel mass 2 , which can be coupled to an internal combustion engine, has a mass ring 21 . The earth ring 21 is formed by a sheet metal body which has two legs 22 and 23 pointing in the axial direction and two legs 24 and 25 pointing in the radial direction, so that the earth ring 21 has an approximately L-shaped cross section. The mass ring 21 is made as a sheet metal folding part by appropriately folding over an originally flat sheet metal blank, as described, for example, in German patent application P 43 15 209, which is expressly referred to here also with respect to the starter ring gear 19 and whose content is at least insofar part of the present application is.

In the exemplary embodiment shown here, the two legs 22 and 23 which extend in the axial direction lie directly against one another in the radial direction. The radially outer leg 22 is shorter than the radially inner leg 23 and lies with its radially extending end portion 22 a on the axially extending leg 20 of the starter ring gear 19 . In such a production of the mass ring 21 , its contours can be adapted, for example, to the inner enveloping contours of the housing taking the dual-mass flywheel, such as in particular the transmission bell, so that no contact can take place. For this purpose, in this exemplary embodiment, the ground ring 21 is formed with a flattened portion 22 b formed as a frustoconical surface. The b for attaching the flat portion 22 displaced material was to increase the material thickness of the radially outer leg 22 used.

The radially inner leg 23 points to the internal combustion engine and goes in the axial region of the starter ring gear 19 to form a bend or curvature 23 a in the radially extending leg 25 of the mass ring 21 . The ground ring 21 lies with this curvature 23 a and the radially extending leg 25 on the side of the pot area 18 of the first flywheel 2 facing away from the internal combustion engine. Radially within this Anlagebe rich, the leg 25 has an axially offset in the direction of the secondary flywheel 3 section 25 a, which bears with its wall against the wall of the second leg 24 extending in the radial direction. The leg 24 projects beyond the section 25 a in the radial direction and ends at a radial distance from the axially extending leg 23 . In the field of curvature 23 a of the ground ring 21 is distributed over a plurality of circumferentially arranged in recesses 26 welds 27 fixedly connected to the primary centrifugal mass. 2

The flange 15 is connected to the center of the first flywheel 2 . The centering can take place, for example, via a centering seat 28 which interacts with a corresponding central recess in the sheet metal part 13 . Likewise, the centering and optionally also fixation of the flange 15 on the first flywheel 2 can take place via individual warts 29 which, in the exemplary embodiment shown here, are put through from the side facing away from the internal combustion engine using material of the flange 15 . Furthermore, the flange 15 has a centering seat 30 radially on the inside, which serves to center the dual-mass flywheel 1 , for example on an engine crankshaft.

Radially outside of its radially extending region 15 a, the flange 15 initially extends inclined radially outward away from the engine side, in order to then subsequently extend again in the radial direction in its radially outer region. In this radially outer area, the flange 15 is firmly connected to a second flange 31 . The fixed connection takes place here again using the material of the flange 15 to form connecting lugs 32 . Radially within this connection wart 32 , the flange 31 extends substantially radially inward, wherein it has a light pot 33 away from the engine side. Radially within the pot 33 , the flange 31 merges into an area 31 a that extends axially to the internal combustion engine, which in turn merges into a region 31 b that extends radially inwards. The radial region 31 b bears against the radial section 15 a of the flange 15 and, like this, has recesses for the passage of the fastening screws 8 , the side of the radial region 31 b facing away from the internal combustion engine being able to form a contact for the heads of the fastening screws 8 .

In their radially outer area or in the area of the pot 33 , the flanges 15 and 31 form loading areas 34 and 35 for the energy accumulators in the form of coil springs 10 . The loading areas 34 and 35 , as can be seen in particular in connection with FIG. 3, are formed by radially extending cantilevers 15 c and 31 c, which protrude into spaces between the forces acting in the circumferential direction 10 protrude. Furthermore, it can be seen in particular from FIG. 3 that the point of use, that is to say the start of the application of the energy accumulator 10 , for the inner and outer springs can be carried out both equally and differently, that is to say in a graduated manner. In addition, it can be seen that the cantilevers 31 c and 15 c do not overlap in the axial direction, ie they are not congruent. Rather, the boom 15 c, 31 c or their Beauf impact areas 34 , 35 are formed such that they are adapted to the spring ends of the force 10 cooperating with them.

The acting together with the loading areas 34 and 35 spring ends have only one separation point in the example shown and are neither applied to the previous spring turn, nor in their Endbe richly ground perpendicular to the spring center axis. This means that the spring end turns of the energy accumulator 10 essentially correspond to any other winding within the energy accumulator 10 , that is to say practically the same pitch analogously to, for example, a screw. This makes it possible to use these spring end turns as resilient turns, as a result of which non-resilient turns are eliminated and more suspension capacity or a shorter spring block length can be achieved. Furthermore, with such a configuration of the spring ends, it is advantageous that the spring wire only has to be severed and thus the otherwise required operations, such as the application of the last spring turn to the previous one, and the grinding of the spring end to achieve a flat contact surface, are eliminated.

Such a spring design in connection with suitably adapted application areas is not limited to the example of a dual mass flywheel, but can be used in any other arrangement, for example in dampers. Furthermore, it is possible to replace the two flanges 15 and 31 by a part, for example a sintered part or a forged part, wherein the application areas 34 and 35 for the energy accumulators 10 can in turn be adapted accordingly.

The two flanges 15 and 31, or an irreplaceable this sintered part or a forged part, can also be designed so that they additionally form an anti-rotation device for the power storage 10 in the region of its memory to the motor 10 adapted impingement 34 and 35th Such an anti-rotation device ensures that the energy accumulators are held and guided exactly in their originally intended position, and thus cannot rotate, for example, with respect to their winding axis. This has the advantage that the free spring end turn always comes to lie at the same point in the application areas 34 and 35 and thus ensures that the end turns with their full spring capacity or suspension volume are available for absorbing vibration energy.

The energy accumulator 10 , on the other hand, is supported with the inner spring on the application areas 36 a and 37a and with the outer spring on the application areas 36 b and 37 b. The applied areas 37 a, b and 36 a, b can, viewed in the circumferential direction, be arranged both at the same height or offset. This in turn enables a targeted determination of the start of the force accumulator loading. The energy storage areas 36 a, b are arranged on a first cover plate 38 , which is supported radially on the inside of the bearing 6 or here on the bearing outer ring 17 of the single-row rolling bearing 6 and which carries the secondary flywheel 3 radially on the outside.

For this purpose, the cover plate 38 has in its radially inner region an in the axial direction on the engine to he stretching shoulder 39 , which has an inner diameter that is suitable for receiving the bearing outer ring 17 with the sealing cap 6 a. On its side opposite the internal combustion engine side, this shoulder has a diameter constriction 40 , which serves as an axial stop or as an axial fixation between cover plate 38 and roller bearing 6 . Starting from this cross-sectional constriction 40 , the cover plate 38 extends radially outward inclined away from the internal combustion engine, this section 41 running essentially straight.

The straight section 41 includes passage recesses 42 which are suitable for receiving the heads of the fastening screws 8 and thus fixing the fastening screws 8 in the non-attached or installed state of the torque transmission device 1 in a substantially coaxial position to the axis of rotation of the dual-mass flywheel 1 . The straight cover plate section 41 opens radially outside in a cross-sectional area 43 , which is at least substantially adapted to the outer contour of the force accumulator 10 and at least partially includes this in the axial and radial directions. At the free end of the area 43 to be pointed towards the internal combustion engine, a radially outwardly facing radial section 44 connects, which is firmly connected to a radial section 45 of the second cover plate 46 , which is arranged in the axial direction between the cover plate 38 and the plate part 13 is. The connection of the two cover plates 38 and 46 is sealed radially outwards by means of an O-ring 47 .

The cover plate 46 comprises radially within the Radialab section 45 of the O-ring 47 partially and dips with an axially extending away from the engine side, the area partially axially in the space encompassed by the cover plate 38 . This ensures the sealing of the annular chamber 11 or of the space 12 and, at the same time, the cover plates 38 and 46 are centered with respect to one another. Proceeding from this, the cover plate 46 extends substantially radially inward, whereby it is essentially adapted to the outer contour of the force accumulator 10 , and extends into the axial installation space between the sheet metal part 13 of the first flywheel 2 and the flange 15 .

Radially within the application areas 37 a and 37 b, the cover plate 46 has an axially offset area 48 in the direction of the internal combustion engine, against which a plate spring 49 rests, which has radial contact inside the flange 15 and thus a seal of the chamber 11 radially inward forms. The plate spring 49 can be centered both in the area of the cover plate 46 and on the flange 15 . Another disc spring 50 serves to seal the chamber 11 radially inward between the flange 31 and the cover plate 38 . For this purpose, the plate spring 50 lies with its outer diameter on the bulge 33 of the flange 31 and with its inner diameter in the region of the axially extending section 31 a of the flange 31 on the cover plate 38 . To center the plate spring 50 , the cover plate 38 has a plurality of centering projections 51 distributed over the circumference, which are formed by partially penetrating the material of the flange 38 . Instead of several centering projections 51 distributed over the circumference, it is also possible to provide an annularly closed approach or, on the other hand, to center the plate spring 50 accordingly on the flange 31 .

In the area of their outer diameter, the cover plates 38 and 46 carry the second flywheel mass 3 with their radial areas 44 and 45 . The radial areas 44 and 45 are arranged on the side facing away from the friction surface of the secondary swing 3 , so that in the event of a leak or failure of the O-ring 47, the medium or lubricant contained in the chamber 11 in the direction of the primary flywheel mass 2 is steered and thus can not affect the friction effect on the friction linings of the clutch disc 5 , whereby the friction clutch 4 can continue to transmit the full torque. The Ver bond with the second flywheel 3 is performed in this embodiment, a Bördelblech 52 which abuts with a radially outwardly extending connecting portion 53 reibflächenseitig on the secondary flywheel mass 3, this radially mostly inside covers and from recesses in the radial portions 44 and 45 axially passes through. Furthermore, the flanging plate 52 on the internal combustion engine has tongues 54 which, in the assembled state, also point radially outward and thus fix the two cover plates 38 and 46 to the flywheel 3 . These tongues 54 he stretch in the original state in the axial direction to the internal combustion engine and after positioning and assembly of the secondary flywheel 3 , the flare 52 and the cover plates 38 and 45 plastically deformed such that, as shown in Fig. 1, radially after show outside.

Together with the clutch unit, consisting of clutch 4 and clutch disc 5 , the dual-mass flywheel 1 forms a structural unit which is preassembled as such, is sent, stored and can be mounted on the crankshaft of an internal combustion engine in a particularly simple and rational manner, because by This configuration eliminates various operations, such as the otherwise required centering process for the clutch disc, the operation for inserting the clutch disc, fitting the clutch, inserting the centering mandrel, Zen trier the clutch disc itself, and possibly inserting the screws, and screwing on the coupling and removing the centering mandrel.

The fastening screws 8 can already be pre-assembled or contained in the bores of the flange region 14 and the flange 15 , whereby they are expediently held in a captive position, for example by flexible means which are dimensioned such that their holding force is overcome when the screws 8 are tightened becomes.

The clutch disc 5 is clamped in a position pre-centered with respect to the axis of rotation of the unit between the pressure plate 55 and the friction surface of the secondary flywheel mass 3 and, moreover, in such a position that the openings 56 provided in the clutch disc 5 are in such a positional arrangement that during fastening of the unit or the structural unit on the output shaft of an internal combustion engine, a screwing tool can be moved through. Furthermore, as shown in the illustrated embodiment, the openings 56 may be smaller than the heads of the screws 8, so that also thereby a trouble-free and captive holding of the screw 8 is ensured within the aggregate.

Also in the plate spring 57 of their tongues 57 are a cut-outs or openings provided for the passage of a Verschraubungswerkzeuges, which are not shown in more detail in this figure in the range. These cutouts can form widenings or extensions of the slots that are present between the tongues 57 a. The openings in the plate spring 57 and the openings 56 in the clutch disc 5 overlap one another in the axial direction and thus allow through their axially aligned arrangement the passage of an assembly tool for tightening the screws 8 and thus for fastening the unit to the crankshaft of an internal combustion engine.

The friction clutch 4 , which can be actuated by the plate spring 57, has on the clutch cover 60 on the one hand a pivoting support 58 on the cover side and on the side remote from the cover 60 has a pivoting support 59 . The swivel supports 58 and 59 formed by wire rings are held over tabs 61 distributed around the circumference. The tabs 61 are made in one piece with the cover 60 and are formed from the material thereof by appropriate deformation. On the side facing away from the cover 60, the tabs 61 encompass the pivot position 59 at least partially in the axial and radial directions. The fixation of the swivel support 58 is ensured radially outside of the swivel support 58 by a bead 62 stamped into the cover 60 . Instead of a circumferential, closed bead 62 , several partial beads distributed over the circumference can also be provided. As can be seen from the figure, the pressure plate 55 can be adapted to the contour of the tabs 61 at least in the region and to the contour of the pivot bearing 59 in the other regions. However, in deviation from the example presented, it can also be expedient to leave the adaptation to the tabs 61 constant over the entire circumferential area.

For the transmission of torque and for the lifting movement of the pressure plate 55 , leaf spring elements 63 are provided which - as can be seen in connection with FIG. 2 - are connected on the one hand via rivets 64 to the housing or cover 60 and on the other hand via rivets 65 to the pressure plate 55 . The riveting with the pressure plate 55 takes place in the area of pressure plate cams 66 which in this example protrude radially inwards and are arranged radially within the friction linings of the clutch disc 5 . The pressure plates cam 66 penetrate the plate spring 57 in the axial direction in the region of recesses 67 , so that the leaf spring elements 63 are arranged on the side of the cover 60 facing away from the pressure plate 55 . Such Blattfederanord voltage is not limited to a split flywheel in use, but can also be used in general in connection with other types of couplings. B. use with a conventional flywheel. The erforder union recesses 67 may, in particular, in conjunction with FIG. 2 by omission of parts can be seen, the diaphragm spring fingers 57 a be formed or by elimination of full spring tongues 57 a. The Tellerfe tongues 57 a are adapted to the contour of the carrier plate of the clutch disc 5 and run at Darge presented here clutch type in the disengaged position of the friction clutch 4 at least approximately parallel to this.

In addition to the recesses 42 in the cover sheet 38 and 56 in the clutch disc 5 are further also used to cool the aggregate was serving openings or passages 68 and 69 in the region of the clutch cover 60, 5 a disc in the coupling 5, 70 in the secondary flywheel mass 3 and 71 in the Sheet metal part 13 of the primary flywheel mass 2 is provided. A sufficient cooling of the entire assembly is intended, inter alia, to prevent a pasty medium, such as fat, contained in the toroidal region 12 from heating up inadmissibly, as a result of which the viscosity of the medium can be reduced so that it becomes liquid. Furthermore, an increased thermal load has a negative impact on the overall service life of the assembly. To further improve the heat dissipation, surface enlargements can also be provided in the secondary flywheel mass 3 (at 72 ) and / or in the pressure plate 55 , which, like the passages described, can be designed like a fan blade.

The fixed to the secondary flywheel 3 hitch be cover 60 consists essentially of the axial region 73 , which is substantially hollow cylindrical ausgebil det, and the at least substantially radially extend the section 74 , in the area of the plate spring 57 is pivotally mounted. The axial region 73 axially overlaps the secondary flywheel mass 3 and can be firmly coupled to it via pin connections or also by means of welding both in the axial direction and in the direction of rotation. DE-OS 41 17 584 shows other types of connection options.

Parts of the axial region 73 or axially directed tongues 75 extend in the axial direction beyond the secondary flywheel 3 in the direction of the internal combustion engine. In their axial end region, these tongues 75 protrude into the axial region, which is delimited radially on the inside by the radial region 24 and radially on the outside by the axial region 23 of the inertial body 21 or mass ring. In this space encompassed by the earth ring 21 , a friction device 76 is arranged, which can be controlled via the axial tongues 75 . The friction device 76 includes at least one friction shoe 77 , as is shown, for example, in FIG. 5. The friction shoe 77 consists of a plastic part 78 , which is essentially adapted to the installation space or the installation radius, and one or more energy stores 79 , which can expand the plastic part 78 in the radial direction. The friction shoe 77 is fixed in the axial direction in that it has a snap-in contour 80 on the radial inside, which cooperates with the ground ring 21 . In the example shown here, the latching contour 80 consists of a conical surface, the tip of the cone pointing towards the internal combustion engine, which engages behind a corresponding undercut, that is to say a likewise conical shape, of the radial region 24 .

The friction shoe 177 shown in FIG. 4 has a different design from the friction shoe 77 . Thus, an initially flat plastic part 178 is preloaded radially in that the initially flat plastic part 178 is installed in a deformed manner together with a round wire 179 acting as a leaf spring, which is also initially straight, in the curved space encompassed by the ground ring 21 . From Fig. 4 it further appears that the Axialzungen also a spacing 81 may have on the friction shoe 77 and 177 75, whereby it is possible, the frictional effect only after a certain rotation angle, after which the game or the distance is bridged 81 to be used. In the case of a plurality of friction shoes 77 and 177 distributed around the circumference, it is further possible to design these distances differently, so that there is a graduated friction effect. For example, friction shoes 77 and 177 can be inserted between the respective axial tongues 75 without play. It is also possible to graduate or influence the frictional force by using different materials for the friction shoes 77 , 177 or by installing these friction shoes 77 or 177 with different radial prestresses.

In FIG. 6, components which are similar or similar to previously described components are provided with similar reference numerals, but which are increased by 100.

The divided flywheel 101 is essentially the same structure as the previously described dual-mass flywheel 1 , but in contrast to this, instead of the roller bearing 6, a plain bearing 106 is provided. To form the plain bearing point 106 , 115 plain bearing material, here in the form of a plastic bushing 106 b, is applied to the outer lateral surface or support shoulder in the axial end section 115 b of the flange. The bearing bush 106 b extends from the free end of the axial end section 115 b, against which it rests with a radially inward facing collar 106 c, towards the internal combustion engine and goes into a radially outward region, forming a curvature 106 d, which bears against the support region 115 d of the flange 115 . The initially extending in the axial direction on the engine shoulder 139 of the cover plate 138 , which encloses the bearing shell 106 b with its inner circumference, is at its free, engine-side end 139 a to the course of the bearing shell 106 b or its radially outward pointing section 106 d adapted. Such a configuration ensures that the cover plate 138 and with it the secondary flywheel 103 with the coupling 104 fastened thereon can be supported both in the radial direction and at least in one axial direction. In a departure from the exemplary embodiment shown here, it is possible to provide support for the radial force component and the axial force component with separate bearing shell components.

The connection of the carrier plate of the clutch disk 105 with its hub or its hub flange is not made here as in the exemplary embodiment according to FIG. 1 via rivets, but via a friction weld connection 105 b. Furthermore, this connection can also be made using the material of the hub flange, so that again no additional connecting parts are required. These connections can therefore be made economically with little effort.

FIG. 6a shows a further link 105 c of the carrier plate with the clutch plate 105 with its hub and its hub flange. For this purpose, the carrier plate is deformed in the area of the through openings 156 in such a way that riveting is formed with the hub flange using the material of the carrier plate of the coupling. Here, material of the carrier plate of the clutch disc 105 penetrates the hub flange in the axial direction and is deformed radially outward after the axial passage, based on the through-openings 156 , so as to form an undercut which secures the carrier plate and the hub flange of the clutch disc 105 connects. In this way, a permanent connection with few parts can be formed. Due to the large rivet hole circle and rivet diameter, the thickness of the carrier plate can be reduced.

A further possible embodiment is shown in FIG. 7, similar reference numerals being used for the same or similar parts, but increased by a further hundred.

The two-mass flywheel 201 shown here differs essentially by the connection of the secondary flywheel 203 with the cover plate 246 from the embodiment according to FIG. 1. The cover plate 246 has an elongated radial area 245 which covers the secondary flywheel mass 203 in the radial direction and which its radially outer end merges into an axial region 245 a pointing away from the internal combustion engine. With this axial region 245 a, the cover plate 246 covers the secondary flywheel mass 203 at least partially in the axial direction and is firmly connected with this to the axially extending region 273 of the clutch cover 260 via pins. In the radially inner region of the secondary flywheel mass 203 , the cover plate 246 is initially by tongues 246 a pointing away from the internal combustion engine in the axial direction, which axially penetrate the radial region 244 of the cover plate 238 and which after the assembly of these parts are plastically deformed so that they are on the side the secondary flywheel 203 point radially inwards, with the cover plate 238 a related party. These tongues 246 a are formed directly from the material of the cover plate 246 , so that an additional flare plate, similar to the flare plate 52 in FIG. 1, can be omitted. Another advantage of this construction is that the heat transfer from the secondary flywheel 203 to the two cover plates 238 and 246 and thus the direct action on the lubricant is reduced. Furthermore, in particular for cooling, additional recesses 245 b are used in the radial region 245 of the cover plate 246 .

For the friction device 276 , friction shoes 177 are provided in this embodiment, the embodiment of which is shown in FIG. 4 and which engage behind the leg 224 of the earth ring 221 with a snap-in contour 180 . With a friction shoe 177 designed in this way, the radially outer boundary surface of the leg 224 can remain axially parallel, as a result of which machining steps for producing the conical configuration according to FIG. 1 are omitted and economic production is possible.

In Fig. 8 a further embodiment of a torque transmission device according to the invention is shown, the reference numerals for similar or similar parts or 25391 00070 552 001000280000000200012000285912528000040 0002004420927 00004 25272r again being increased by hundreds.

In contrast to in Fig. 1 illustrated dual mass flywheel 1, the split flywheel 301, whereby it in turn comprising taking a ground ring 321, which has an approximately S-shaped cross-section in a friction device 376 on. In terms of function, arrangement and design, the friction device 376 essentially corresponds to the previously described friction devices.

In contrast to the torque transmission devices described so far, the dual-mass flywheel 301 has a torque limiting element or a slip clutch 381 , which is effectively arranged between the secondary flywheel mass 303 and the cover plates 338 and 346 forming the chamber 311 . The connection of the secondary flywheel mass 303 with the cover plates 338 and 346 takes place via a flanged plate 352 in a similar manner as is described in connection with FIG. 1. Friction material 382 in the form of a friction lining is applied between the secondary flywheel mass 303 and the flanging plate 352 or the cover plate 338 . This covering also serves as thermal insulation in the direction of the chamber 311 containing the lubricant. Between the radial portion 345 of the sheet metal part 313 facing the cover plate 346 and the deformed retention tabs 354 of the flange plate 352 is arranged a plate spring 383, which generates an axial force which clamps the secondary flywheel mass 303 which Bördelblech 352 and the radial portions 344 and 345 zuein other, so that due to the friction occurring on the friction lining 382 a certain torque or a certain force acting in the circumferential direction from the slip clutch 381 and thus can be transmitted from the divided flywheel 301 .

The contact pressure of the plate spring 383 and thus the transferable torque can be influenced in such a way that the transferable torque is reduced in the range of the maximum relative rotation from the primary flywheel mass 302 to the secondary flywheel mass 303 , so that the primary and secondary sides continue to slide against one another when the slip clutch 381 is at least partially open can twist in order to keep harmful overtorques away from other components or to avoid their transmission into the downstream transmission. For this purpose, the plate spring 383, as shown particularly in connection with Fig. 9, it can be seen out of its plane in the direction of the internal combustion engine to be inclined wings 383 a, which may a of the plate member 313 cooperate with correspondingly designed ramps 313.

When the primary flywheel mass 302 and the secondary flywheel mass 303 are rotated relative to one another, the tongues 383 a and the run-up ramps 313 a approach each other, these coming into contact with one another after a certain angle of rotation. When the relative rotation continues in the same direction, the tongues 383 a slide on the run-up ramps 313 a and bring the plate spring 383 axially closer to the sheet metal part 313 of the primary flywheel mass 302 , as a result of which the plate spring force is reduced. Such a reduction in the plate spring force causes the slip clutch 381 to open at least partially, so that the secondary flywheel mass 303 with the clutch 304 attached to it can slip relative to the cover plates 338 and 346 . The slip clutch 381 can act only in one direction of the relative rotation as well as in both directions, whereby it can be executed in both relative directions of rotation both the same, that is to say symmetrically and also differently. The slip clutch or the torque limiting member 381 , which is endwin controlled here, is thus arranged in this exemplary embodiment according to FIG. 8 on the secondary side and in the radial direction (in alignment) between the secondary flywheel mass 303 and the energy stores 310 .

The structure shown in FIG. 10 is again essentially the same as that of FIG. 1, similar reference numerals being used for the same or similar parts in the function, which in turn are increased by one hundred.

In the dual-mass flywheel 401 shown here, the flanges 415 and 431 lie against one another over the entire extent of the flange 431 , that is to say they have no region in which they are axially spaced apart from one another. Furthermore, the sheet metal part 415 of the primary flywheel mass 402 has the centering seat 430 for centering the primary flywheel mass 402 or the entire dual-mass flywheel 401 on the output shaft of an internal combustion engine. The flanges 415 and 431 can also be combined in a single part, which can be out as a casting, forging or sintered part.

The radially inner boundary of the chamber 411 is formed in this embodiment by a separate, wall-forming part 484 , which in this case is made of plastic and which additionally surrounds the heads of the fastening screws 408 with its radially inner region and can be suitably designed to guide them or to prevent the screws 408 from tilting. In its radially outer area, the plastic part 484 surrounds the plate spring 450 which acts as a seal and which, on the other hand, interacts with the cover plate 438 . The passages 442 serving for the passage of a screwing tool or for the passage of the fastening screws 408 are surrounded by an axial shoulder or collar 442 a, which is suitable with its inner circumference to increase the fastening screws 408 in the unmounted state of the dual-mass flywheel 401 , to support and to keep in at least approximately coaxial position to the axis of rotation of the torque transmission device. In the radially outer region of its outer circumference, these lugs or collars 442 a can form an auxiliary centering, for example for the assembly for the diaphragm spring seal 450 .

In the exemplary embodiment shown here, the secondary flywheel mass 403 is connected to the axial region 473 of the clutch cover 460 by means of a plurality of fastening plates 485 distributed over the circumference. As can be seen in particular in connection with FIG. 11, the fastening plates 485 have radial projections which penetrate the axial region 473 of the clutch cover 460 through suitable recesses. The fastening plates 485 are screwed by means of screws 485 a to the secondary flywheel mass 403 on their side facing away from the friction surface, the screws being accessible through openings 485 b in the first flywheel mass 402, which also serve for ventilation. Different radial and axial preload forces can be generated via different shapes of the contact surfaces between mounting plates 485 and secondary swing mass 403 .

The sheet metal part 413 of the primary flywheel mass 402 has further openings 471 and 471 a, which are also used for ventilation and whose radially inner 471 a is arranged approximately in the radial region of the chamber 411 . As a result, an air flow can be generated which passes the chamber 411 directly and thus avoids inadmissible heating of the lubricant contained in the chamber. Furthermore, 10 is known from Fig. Inferred that faces away from the internal combustion engine side is at least adapted to the sheet metal part 413 in the radial region of the chamber 411 at its contour substantially.

In Fig. 12, the arrangement of the application areas 436 a and 436 b is shown as an example, to which the application areas 437 a and 437 b are symmetrical. The application areas 436 a, 436 b, 437 a, 437 b are formed without additional individual parts by the material of the cover plates 438 and 446 being deformed in the axial direction, in such a way that these deformations point axially toward one another. In order to achieve the gradation of the loading areas 436 a and 436 b shown in FIG. 12 in the circumferential direction, these axial deformations can be formed by a so-called double feed.

Although the dual-mass flywheel 401 shown does not have a separate friction device, it can be designed both with a friction device for the idling range and with one for the load range. The carrier plate of the clutch plate 405 is in turn essentially matched to the contour of the cover plate 438 and has ventilation openings for the passage of a cooling air flow both radially in the area of the chamber 411 and radially outside this, which can then sweep along the chamber wall 438 and through ventilation recesses 470 in the secondary flywheel mass 403 , in the direction of the primary flywheel mass 402 , can pass through.

In the dual-mass flywheel 501 shown in FIG. 13, the tasks and functions of the flanges 415 and 431 and of the plastic part 484 are combined in a single flange 515 . This flange 515 can in turn be manufactured as a casting, forging or sintering without finishing part, which for example, has the result that the primary flywheel mass can be placed 502 without mounting rework. A sintered part as a flange 515 can also prove to be economical because another plastic sealing part, similar to the plastic part 484 in FIG. 12, can be omitted and because, for example, the seat 515 b for the bearing 506 and the centering seat 530 for mounting on the Output shaft of an internal combustion engine can be produced without further post-processing.

In FIG. 14, the same reference numerals are used for at least the same or similar components as in the previous figures, but again increased by one hundred, starting with 601.

Fig. 14 shows a divided flywheel or dual mass flywheel 601, the one on a non-shown power take-off shaft of a motor can be fastened first or Primärschwungmas se possesses 602 and a second or secondary flywheel mass 603rd On this second flywheel 603 , a friction clutch 604 is fixed with the interposition of a clutch disc 605 , the hub of which can be received on the drive shaft of a transmission, not shown, or on a shaft connected to the latter. The clutch disc 605 , which is of a rigid design here and serves only as an example, can also comprise further designs and can thus be equipped, for example, with a pad suspension.

The two centrifugal masses 602 and 603 are rotatably mounted to each other, including components that are firmly connected to them, via a bearing 606 , which in this example comprises a rolling bearing, which in this example radially outside the bores 607 for carrying out fastening screws 608 for mounting the torque transmission device 601 on the output shaft an engine is arranged. Between the two flywheels 602 and 603 , a damping device 609 is effective, which has, for example, compression springs 610 or leg springs, which are accommodated in an annular space 611 , the annular space 611 forming an approximately toroidal region 612 in its radially outer region. The annular space 611 can be at least partially filled with a lubricant-like medium.

The primary flywheel mass 602 has a component 613 , which is preferably made or drawn from sheet metal material and is used to fasten the split flywheel 601 to the crankshaft of the engine. The component 613 forms on its inner periphery a flange-like region 614 which extends essentially in the radial direction and which carries a flange 615 radially on the inside, the radial regions 615 a of which have holes for the fastening screws 608 aligned with the recesses 607 . The single-row ball bearing 606 shown here is received with its outer ring 617 in an inner circumferential surface or a support area in the axial end section 615 b of the flange 615 . The second flywheel 603 is supported on the inner ring 616 of the rolling bearing of the bearing 606 .

The essentially radially extending region 614 merges into the starter gear ring 619, which is made in one piece with the primary flywheel mass 602 , after a pot 618 directed axially towards the internal combustion engine side. The starter tooth wreath 619 is here in turn manufactured by a method as described, for example, in connection with FIG. 1 ben. The radially inward leg 620 is welded to the sheet metal part 613 and passes in the area of this welding into an axial area 620 a, which extends away from the engine side and which in turn merges at its free end into a radial section 620 b, which is in Direction to the axis of rotation of the torque transmission device 601 extends.

To increase the moment of inertia of the dual-mass flywheel 601 rotating about its axis of rotation, the primary flywheel mass 602 , which can be coupled to the engine, has a mass ring 621 , which in this example is designed as a cast part. The mass ring 621 lies at least partially on the side of the sheet metal part 613 facing away from the internal combustion engine and borders radially on the outside on the axial section 620 a. The attachment of the mass ring 621 within the primary flywheel mass 602 can be done by flanging the section 620 b, which originally represents an axial extension of the axial section 620 a and, after its plastic deformation, points radially inward, as shown in FIG. 14.

The flange 615 is connected in a centered manner to the primary flywheel mass 602 , the centering being able to take place, for example, via a centering seat 628 which interacts with a corresponding central recess in the sheet metal part 613 . Furthermore, the flange 615 radially on the inside a Zen trier seat 630 , the two-mass flywheel 601 on the shaft driving this tren in the mounted state.

Radially outside of its radial region 15 a, the flange 15 initially extends axially away from the internal combustion engine side (in the exemplary embodiment shown up to the end region of the heads of the fastening screws 608 ), in order to then subsequently extend outward again in the radial direction. In its radially outer region, the flange 615 forms application regions 634 for the screw springs 610 . The application areas 634 are formed by radially extending cantilevers 615 c, which protrude into intermediate spaces between the force accumulators 610 which act in the circumferential direction. The flange 615 or its radially outside the axial end portion 615 b acting areas 634 can also be designed as described in connection with FIG. 1, that is to say in particular adapted to the spring ends.

The energy stores 610, on the other hand, act on the application areas 636 and 637 , which in turn can be divided into different application areas analogously to that described in FIG. 1. The application area 636 is arranged on a first cover plate 638 , which is supported radially inside on the bearing 606 or here on the bearing inner ring 616 of the single-row rolling bearing 606 and which carries the secondary flywheel mass 603 radially outside. The cover plate 638 has on its radially inner region a shoulder 639 which extends in the axial direction towards the motor and which has an outer diameter on which the bearing inner ring 616 is received. Radially inside the bearing 606 , the cover plate 638 runs radially inward at least in the region of the fastening screws 608 distributed around the circumference.

This radial portion 641 includes Durchgangsaus recesses 642, which are suitable for the heads of its mountings fixing screws 608 in non-attached state of the torque transmitting device 601 to be fixed such that they retain their substantially coaxial position to the axis of rotation of the torque transmitting device six hundred and first Radially outside of the bearing 606 , the cover plate 638 forms a chamber wall of the chamber 611 and at least partially includes the energy stores 610 . This is followed by an outward-pointing radial section 644 , which is fixedly connected to a radial section 645 of the second cover plate 646 , which is arranged axially between the cover plate 638 and the cover plate 613 , in the illustrated example via a weld. Between the force accumulators 610 and the radially outer regions of the toroidal space 612 or the annular chamber 611 , wear protection 612 a is provided which, in this example, surrounds the spring ben 610 610 like a shell.

The radial section 644 projects beyond the radial section 645 and is folded over on its outer periphery, similarly as already described, to form a leg 644 a pointing radially inward. The radially outer part of the leg 644 a lies directly against the radial area 644 , while the radially inner, free area of the leg 644 a is at a distance from the radial area 644 . The leg 644 a extends up to close to the radially outer boundary of the annular chamber 611 . A cooling air flow can be guided through the axial distance mentioned, which flows through axial recesses 644 b in the radial region 644 and can be guided radially outwards through the space between the mass ring 621 and the secondary flywheel mass 603 .

Radially within the application area 637 , the cover plate 646 has an area 648 which is offset axially in the direction of the internal combustion engine and against which a plate spring 649 bears, which is in radial contact with the flange 615 and thus seals the chamber 611 radially inward. The centering of the plate spring 649 can take over both the cover plate 646 and the flange 615 . Another disc spring 650 serves to seal the chamber 611 radially inward between the flange 615 and the cover plate 638 . For this purpose, the plate spring 650 is held centered on its outer circumference on the flange 615 and resiliently rests with its inner circumference on the cover plate 638 . In this exemplary embodiment, the plate spring 650 , that is to say the seal from the chamber 611, is arranged radially inward, radially inside the bearing 606 . Such an arrangement makes it possible to fill the annular space 611 with a dry or pasty lubricant in such a way that at least during operation, that is to say when the dual-mass flywheel 601 rotates, the bearing 606 has lubricant contact. The dual-mass flywheel 601 can in turn be designed together with the clutch unit, consisting of clutch 604 and clutch plate 605 , as a structural unit which is preassembled as such, as has already been described. The clutch disc 605 is then clamped in a position centered in relation to the axis of rotation of the unit between the pressure plate 655 and the friction surface of the secondary flywheel mass 603 .

The actuatable via the plate spring 657 friction clutch 604 has on the clutch cover 660 on the cover side a pivoting support 658 and on the side facing away from the cover a pivoting support 659 , which are part of a wear-compensating adjusting device 686 , which can be similar to that in DE-OS 42 39 291 be described. For the transmission of torque and for the lifting movement of the pressure plate 655 , leaf spring elements 663 are provided, which are connected on the one hand via rivets to the housing or the cover 660 and on the other hand via rivets 665 to the pressure plate 655 . The riveting with the pressure plate 655 takes place radially within the friction linings of the clutch disc 605 and radially outside the loading area 666 a, against which the radially outer area of the plate spring 657 bears.

Recesses for the implementation of fastening screws 608 or tools to operate them, as well as Ausnehmun conditions that are used for cooling, can be carried out analogously to the examples described so far in the structure shown here.

The radially outer region of the secondary flywheel mass 603 carries the clutch cover 660 , which is firmly connected to it. The connection of the clutch cover 660 to the secondary flywheel 603 and the radial portion 644 in this case by means of fastening tabs 674 a which extend in the non-assembled state at least approximately in the axial direction and the plastically deformed after pressing and inserting the secondary flywheel 603 are that, as shown, they engage radially inwardly in corresponding recesses in the secondary flywheel mass 603 and thus produce a connection that is firm both in the axial and in the circumferential direction.

The invention is not described and described on the limited exemplary embodiments, but also includes Variants combined by combining individual described with the various embodiments Features or elements can be formed. The The applicant reserves the right to do so far only in the Description disclosed features of essential to the invention Claim meaning.

Claims (136)

1. Torque transmission device with at least two against the action of a damping device with in Energy storage acting over a circumferential direction Bearing rotatable flywheels, from which one - first - with the output shaft one Internal combustion engine and another - second - over a friction clutch with the drive shaft Gear can be connected, the energy accumulator radially within the friction surface of the friction clutch in an at least essentially closed, self arranged in the circumferential direction are. 2. Torque transmission device according to claim 1, characterized in that the chamber the power spit cher encloses at least in the radially outer region. 3. Torque transmission device according to one of the An sayings 1 or 2, characterized in that the Chamber at least in the radially outer area Contour of the lift mechanism is nestled.   4. Torque transmission device according to one of the An sayings 1 to 3, characterized in that the Chamber is formed from at least two walls of at least one with the second flywheel connected is. 5. Torque transmission device after at least one of the preceding claims, characterized records that at least one of the chamber walls second flywheel carries. 6. Torque transmission device according to one of the Claims 1 to 5, characterized in that the Storage is designed as a plain bearing. 7. Torque transmission device according to one of the Claims 1 to 5, characterized in that the Storage is designed as roller bearings. 8. Torque transmission device according to one of the An sayings 1 to 7, characterized in that the Lift mechanism using coil springs are formed. 9. Torque transmission device after at least one of the preceding claims, characterized records that the lift mechanism using Leg springs are formed.   10. Torque transmission device according to one of the An sayings 1 to 9, characterized in that the Abge chamber at least radially inside substantially seals and at least partially with dry lubrication medium filled. 11. Torque transmission device according to claim 10, characterized in that the chamber has a laby rinth seal is sealed. 12. Torque transmission device according to one of the An sayings 1 to 9, characterized in that the Chamber at least essentially sealed and with viscous / pasty medium at least partially filled is. 13. Torque transmission device according to one of the An sayings 1 to 12, characterized in that the Storage is arranged within the chamber. 14. Torque transmission device according to one of the An sayings 1 to 13, characterized in that the Storage arranged radially within the energy accumulator is. 15. Torque transmission device according to one of the An Proverbs 1 to 14, characterized in that the  radially outer cover plate forming the second chamber wall outside the energy storage with the one chamber wall tion forming cover plate is firmly connected. 16. Torque transmission device according to claim 15, characterized in that the connection under Ver use of an O-ring between the chamber walls is sealed. 17. Torque transmission device according to one of the An Proverbs 1 to 16, characterized in that the Cover plates forming chamber walls have areas for the energy storage. 18. Torque transmission device according to claim 17, characterized in that the application area by axially directed towards each other gene are formed, the axially in between spaces the lift mechanisms protrude. 19. Torque transmission device according to one of the preceding claims, characterized in that the cover plates are connected to the second flywheel are. 20. Torque transmission device according to claim 19, characterized in that the cover plates on the Frictional surface facing away from the second flywheel  are articulated. 21. Torque transmission device according to one of the An sayings 1 to 20, characterized in that the Cover plates with the second flywheel form-fitting are connected. 22. Torque transmission device according to one of the An sayings 1 to 20, characterized in that the Cover plates with the second flywheel friction are connected. 23. Torque transmission device, in particular after one of claims 1 to 22, characterized in that that a torque limiter so in force transmission path is provided that the torque flow - seen from the engine - from the first flywheel forth about a force immersed in the chamber flange acting on the force memory, from there to the chamber walls, from there on the radially outside of the energy accumulator ne, but radially within or only slightly fit into the radially outer friction area the friction surface of the friction clutch Torque limiting device and from there to the second Inertia takes place. 24. Torque transmission device according to one of the An  sayings 22 or 23, characterized in that the frictional connection is axially biased. 25. Torque transmission device according to claim 24, characterized in that a disc spring for axial preload required axial force brings. 26. Torque transmission device according to claim 25, characterized in that the axial force by Actuation of the plate spring is changeable. 27. Torque transmission device according to claim 26, characterized in that the operation of the tel Spring made by the first flywheel. 28. Torque transmission device according to claim 27, characterized in that the actuator is made in one piece with the first flywheel. 29. Torque transmission device according to one of the An Proverbs 22 to 28, characterized in that the Cover plates with the second flywheel under intermediate position of friction material are connected. 30. Torque transmission device according to claim 29, characterized in that the friction material a forms thermal insulation.   31. Torque transmission device according to one of the preceding claims, characterized in that a cover plate forming a chamber wall from the Storage is worn. 32. Torque transmission device according to one of the An Proverbs 1 to 31, characterized in that the Lift mechanism, on the other hand, at the application areas support that protrude into the chamber Flange (s) are arranged, the radially in within the lift mechanism with the first flywheel is / are connected. 33. Torque transmission device according to claim 32, characterized in that the connection of the Flan cal or the flange with the first. Inertia using a fastening screw ben takes place to connect the first flywheel se or the torque transmission direction with the output shaft of the internal combustion engine to serve. 34. Torque transmission device according to one of the An sayings 32 or 33, characterized by two flanges cal, which is fixed in the area of their outer diameter are interconnected. 35. Torque transmission device according to one of the An  sayings 32 to 34, characterized in that the two flanges in the area to attach the Device on the crankshaft serving screws abut each other. 36. Torque transmission device according to one of the An sayings 32 to 35, characterized in that the two flanges in the radial area between the feet set screws and their outer diameter axially are spaced from each other. 37. Torque transmission device, in particular after one of claims 1 to 36, characterized in that the areas of exposure to the first Inertia connected flanges or with this connected flange by screw the energy accumulators formed are adapted / whose Spring end turns are essentially the same as their spring medium turns are formed. 38. Torque transmission device according to one of the An Proverbs 1 to 37, characterized in that the Areas of application of the flange respectively the flanges for built-in inside and outside springs are graduated. 39. Torque transmission device according to one of the An sayings 1 to 38, characterized in that the  Cover plates graded loading areas for have internal and external springs built into one another. 40. Torque transmission device according to claim 39, characterized in that the application area che are formed by a double feed. 41. Torque transmission device according to one of the preceding claims, characterized in that the first flywheel and a flange to each other are centered directly on a seat. 42. Torque transmission device according to one of the An Proverbs 1 to 41, characterized in that a Flange a centering seat for centering the torque ment transmission device on the output shaft of Has internal combustion engine. 43. Torque transmission device according to one of the An sayings 1 to 42, characterized in that a Flange supports the bearing. 44. Torque transmission device according to one of the An sayings 1 to 43, characterized by two flanges to act on the lift mechanism, one of which for fastening the torque transmission device on the output shaft of the internal combustion engine, to the Centering on the output shaft to accommodate the  Bearing and centering the first flywheel serves. 45. Torque transmission device according to one of the An Proverbs 1 to 44, characterized by a radial internal chamber sealing by means of one disc spring-like component, on the one hand with a a chamber wall forming a cover plate or one with this connected component and on the other hand with the this adjacent flange or one with this connected component cooperates. 46. Torque transmission device according to one of the preceding claims, characterized in that a component connected to a flange, which with the plate spring-like seal interacts, to fixie tion of the fastening screws. 47. Torque transmission device according to one of the An sayings 1 to 46, characterized in that a Cover plate recesses for the passage of the fastening has screws. 48. Torque transmission device according to one of the An sayings 1 to 46, characterized in that a Cover plate recesses for the passage of a tool for actuating the fastening screws.   49. Torque transmission device according to one of the An sayings 47 or 48, characterized in that the Recesses are surrounded by a federal government. 50. Torque transmission device according to claim 49, characterized in that the covenant with one of the plate spring-like seals cooperates. 51. Torque transmission device according to one of the An sayings 45 to 50, characterized in that the disc spring type seals a friction damping are furnishing. 52. Torque transmission device according to one of the An Proverbs 1 to 51, characterized in that the Lift mechanism and the second flywheel arranged friction surface of the friction clutch in the same Chen axial area are arranged. 53. Torque transmission device according to one of the An Proverbs 1 to 52, characterized in that the Bearing and the heads of the mounting screws in the same axial area are arranged. 54. Torque transmission device according to one of the An Proverbs 1 to 53, characterized by the arrangement the energy accumulator in the radial direction between the Heads of the fastening screws and those on the  second flywheel arranged friction surface of the Friction clutch. 55. Torque transmission device according to one of the An sayings 1 to 54, characterized by a wall facing the heads of the mounting screws th side of the chamber. 56. Torque transmission device, in particular according to one of claims 1 to 55, characterized by the radial sequence of at least four of the seven following components:

• - Profile of the gear shaft
• - storage
• - Heads of the fastening screws
• - Radially inner chamber wall
• - Lift mechanism
• - Radially outer chamber wall
• - The second flywheel's friction surface

57. Torque transmission device according to claim 56, characterized by the arrangement of the components different diameter ranges that are not cover up. 58. Torque transmission device according to one of the An sayings 56 or 57, characterized in that the (at least four) components in the same axial area  are arranged. 59. Torque transmission device according to one of the preceding claims, characterized in that the storage radially inside the heads of the fasteners supply screws is arranged. 60. Torque transmission device according to one of the An Proverbs 1 to 59, characterized by the arrangement the heads of the fastening screws between storage and energy stores. 61. Torque transmission device according to one of the An sayings 1 to 60, characterized in that the Lift mechanism and the heads of the fastening screws adjacent and arranged in the same axial area are. 62. Torque transmission device according to one of the An Proverbs 1 to 61, characterized by a the chamber (with) forming wall radially between the power spit and the heads of the fastening screws. 63. Torque transmission device according to one of the An sayings 1 to 58, characterized in that the Storage radially outside the heads of the attachment screws is arranged.   64. Torque transmission device according to one of the preceding claims, characterized in that the energy storage of the damping device a Ver Ratio from length to diameter in the range from 4 to 10 have. 65. Torque transmission device according to one of the Claims 1 to 64, characterized in that the lift mechanism over a range of the circumference range, which is between 70% and 95%. 66. Torque transmission device according to one of the Claims 1 to 65, characterized in that at least one energy store over a sector of the Extends circumference that is greater than 140 °. 67. Torque transmission device according to one of the Claims 1 to 66, characterized in that the Lift mechanism at least approximately on the one Radius are pre-curved, which corresponds to the installed state speaks. 68. Torque transmission device according to one of the Claims 1 to 67, characterized by a plurality of spring levels. 69. Torque transmission device, in particular after one of claims 1 to 68, characterized in that  that in energy stores in the form of coil springs whose end spring turns are essentially there corresponding spring coils correspond. 70. Torque transmission device according to one of the Claims 1 to 69, characterized by a ver wear protection between the lift mechanism and the radially outer chamber wall on which the Support the energy storage at least under centrifugal force. 71. Torque transmission device according to one of the preceding claims, characterized in that the cover of the friction clutch on the second Centrifugal mass is centered. 72. Torque transmission device according to one of the Claims 1 to 71, characterized in that the Cover the friction clutch the second flywheel encompasses axially. 73. Torque transmission device according to claim 71, characterized in that the cover of the friction clutch on the second flywheel with its axial area and encompassing the flywheel mass is centered. 74. Torque transmission device according to one of the Claims 71 to 73, characterized in that the  Cover with the second flywheel over a sweat connection is connected. 75. Torque transmission device according to one of the Claims 66 to 68, characterized in that the Lid is separably connected to the second flywheel is. 76. Torque transmission device according to one of the Claims 71 to 75, characterized in that the Lid itself is separable. 77. Torque transmission device according to one of the preceding claims, characterized in that the carrier plate of the clutch disc of the friction clutch at least essentially to the contour of the Chamber is adjusted. 78. Torque transmission device according to one of the Claims 1 to 77, characterized by a lubrication middle deflector plate and / or a lubricant deflector contour on the carrier plate of the clutch disc and / or the one facing her, forming a chamber wall Cover plate in the area of the cover plate recesses. 79. Torque transmission device according to one of the Claims 1 to 78, characterized in that the  Carrier plate of the clutch disc recesses for Has passage of the fastening screws. 80. Torque transmission device according to one of the Claims 1 to 78, characterized in that the Carrier plate recesses for the passage of a tool ges for actuating the fastening screws. 81. Torque transmission device according to one of the Claims 1 to 80, wherein the pressure plate Friction clutch through an annular base Body and tongues with cup spring bar, characterized in that the contour of the Disc spring to that of the clutch support plate at least in the position, in the disc spring and carrier sheet are approximated, at least is approximately adapted. 82. Torque transmission device according to claim 81, characterized in that the disc spring in the area their tongues recesses for the passage of the fastener has screws. 83. Torque transmission device according to claim 81, characterized in that the disc spring recess conditions for the passage of a tool for actuating the Has fastening screws.   84. Torque transmission device, in particular after one of the preceding claims, characterized records that the disc spring recesses for through occurs on the pressure plate of the friction clutch arranged pressure plate cams. 85. Torque transmission device according to claim 84, characterized in that the recesses by Omission of tongues are formed. 86. Torque transmission device, in particular after one of the preceding claims, characterized records that the leaf springs that the printing plate with the cover of the friction clutch non-rotatably, but axially connect relocable on the pressure plate abge facing side of the lid are arranged. 87. Torque transmission device according to one of the Claims 1 to 86, characterized in that the Pressure plate on the opposite of the friction surface Side of the contour of the diaphragm spring position on the cover side tion is adjusted. 88. Torque transmission device according to claim 87, characterized in that the pressure plate and Parts of the cover-side plate spring bearing axially and radially in the disengaged position of the friction clutch cover up.   89. Torque transmission device according to one of the preceding claims, characterized in that the cover-side disc spring mounting by one piece tabs executed with the lid is formed. 90. Torque transmission device according to claim 89, characterized in that the pressure plate on their the opposite side of the contour of the friction surface Tabs is adjusted. 91. Torque transmission device according to one of the Claims 1 to 90, characterized in that the first flywheel at least partially to the contour the areas of the chamber facing her are adapted. 92. Torque transmission device according to one of the Claims 1 to 91, characterized in that the first flywheel mainly made of sheet metal (parts) is made. 93. Torque transmission device according to one of the Claims 1 to 92, characterized in that the first flywheel carries the starter ring gear. 94. Torque transmission device according to one of the Claims 1 to 93, characterized in that the Starter ring gear through a folded sheet metal part is formed, the walls of which abut each other.   95. Torque transmission device according to one of the Claims 1 to 94, characterized in that the Starter ring gear in one piece with the first swing mass is executed. 96. Torque transmission device according to one of the Claims 1 to 95, characterized in that the first flywheel has a mass ring. 97. Torque transmission device according to claim 96, characterized in that the ground ring by a Casting is formed. 98. Torque transmission device according to claim 96, characterized in that the ground ring by a folded sheet metal part is formed. 99. Torque transmission device according to one of the Claims 96 to 98, characterized in that the Earth ring the axial area of the clutch cover engages and this at least partially in axial direction covered. 100. Torque transmission device according to one of the preceding claims, characterized in that the damping device is a load friction device having.   101. Torque transmission device according to claim 100, characterized by the arrangement of the load friction device radially outside the energy accumulator. 102. Torque transmission device according to one of the Claims 100 or 101, characterized by the Arrangement of the load friction device radially outside of average friction diameter of the friction clutch. 103. Torque transmission device, in particular after one of claims 100 to 102, characterized in net that the Lastreibeinrichtung at least a friction part with two radially spaced friction surfaces ent holds. 104. Torque transmission device according to one of the Claims 100 to 103, characterized in that the Friction part the friction connection with the first Has a flywheel. 105. Torque transmission device according to one of the Claims 100 to 104, characterized in that the Friction part of one part of the second Inertia can be loaded. 106. Torque transmission device according to one of the Claims 100 to 105, characterized in that the Friction parts and loading parts in the circumferential direction  to have a game. 107. Torque transmission device according to one of the Claims 100 to 106, characterized in that several friction parts with different game against are provided over the application parts. 108. Torque transmission device according to one of the Claims 100 to 107, characterized in that a axially extending area of the cover of the friction clutch is part of the load friction device. 109. Torque transmission device according to one of the Claims 100 to 108, characterized in that the Ground ring of the first flywheel part of the Lastreibeinrichtung is. 110. Torque transmission device according to one of the Claims 100 to 109, characterized in that the Load friction device is arranged in the area in which the mass ring the axial area of the clutch grips cover. 111. Torque transmission device according to one of the preceding claims, characterized in that the load friction device has at least one energy store having.   112. Torque transmission device according to claim 111, characterized in that the energy storage in Radial direction acts. 113. Torque transmission device according to one of the preceding claims, characterized in that the Lastreibeinrichtung by at least one in the first flywheel arranged friction shoe formed is. 114. Torque transmission device according to claim 113, characterized in that the friction shoe clipped is. 115. Torque transmission device according to one of the Claims 113 or 114, characterized in that the load friction device several over the scope distributed friction shoes. 116. Torque transmission device according to one of the Claims 113 to 115, characterized in that at least the friction surface (s) of the friction shoe / Friction shoes made of plastic. 117. Torque transmission device according to one of the preceding claims, characterized in that the carrier plate of the clutch disc and / or the Tel lerfeder further recesses, in particular for  Ventilation of the torque transmission device, exhibit. 118. Torque transmission device according to one of the preceding claims, characterized by ventilation opening in the axial area of the lid Friction clutch. 119. Torque transmission device according to one of the Claims 1 to 118, characterized by ventilation openings in the radial area of the cover of the Rei exercise clutch. 120. Torque transmission device according to one of the Claims 1 to 119, characterized by ventilation openings in the first flywheel. 121. Torque transmission device according to one of the Claims 1 to 120, characterized by ventilation openings in the second flywheel radially outside the chamber. 122. Torque transmission device according to one of the previous claims, characterized by the Ventilation by air flow through the beams through the clutch disc, along the Chamber wall, through openings in the second flywheel outside the chamber  Towards the first flywheel. 123. Torque transmission device according to one of the Claims 1 to 122, characterized by ventilation openings in the first flywheel for one on the Chamber wall facing and on the second Flywheel passing air flow. 124. Torque transmission device according to one of the Claims 1 to 123, characterized by ventilation openings in the first flywheel for one on the second flywheel to direct airflow. 125. Torque transmission device according to one of the Claims 1 to 124, characterized by surfaces enlargements to improve heat dissipation at the the side of the second swing facing away from the friction surface Dimensions. 126. Torque transmission device according to one of the Claims 1 to 125, characterized by surfaces enlargements to improve heat dissipation at the the side of the pressure plate facing away from the friction surface. 127. Torque transmission device according to one of the Claims 117 to 126, characterized in that the Surface enlargements and / or ventilation openings are formed like a fan blade.   128. Torque transmission device according to one of the preceding claims, characterized in that the torque transmission device with friction clutch and clutch disc a pre-assembled Unit forms, as such with the attachment screw on from the side facing away from the motor the output shaft of the internal combustion engine can be screwed on is. 129. Torque transmission device according to claim 128, characterized in that the fastening screws are included in the unit. 130. Torque transmission device according to claim 129, characterized in that the fastening screws are kept captive in the unit. 131. Torque transmission device according to one of the preceding claims, characterized in that the friction clutch as a so-called pressed clutch is executed. 132. Torque transmission device according to one of the Claims 1 to 130, characterized in that the Friction clutch as a so-called drawn clutch is executed. 133. Torque transmission device, in particular after  one of the preceding claims, characterized due to the radially aligned arrangement of the second Flywheel, torque limiter / slip clutch tion and the force acting in the circumferential direction cher. 134. Torque transmission device according to claim 133, characterized in that the energy accumulator in one essentially closed, in the circumferential direction extending chamber are arranged. 135. Torque transmission device according to one of the Claims 133 or 134, characterized by the radially aligned arrangement of the storage. 136. Torque transmission device according to one of the Claims 133 to 135, characterized in that the Torque limiting element / the slip clutch radial between the energy stores and the second swing mass is arranged.