DE4117580A1 - Divided flywheel structure - Google Patents

Abstract

A divided flywheel comprises a first flywheel mass (2) fixable on an internal combustion engine and a second flywheel mass which can be engaged with or disengaged from a gearbox by a clutch. The flywheel masses are journalled relative to each other by way of a bearing (4). The masses have a damping device between them, housed in a torus (9) which lies around the outer periphery of the flywheel. The second flywheel mass lies partly within the envelope defined by the torus (9) and the torus itself lies outside the friction damdiameter of the clutch. The damping device comprises helical compression springs (9) within the grease-filled torus (9). A wall (17) of the torus is adjoined by a membrane seal (18).

Description

The invention relates to a torque transmission device, as for example by DE-OS 37 21 705 has become known. This has a first one Internal combustion engine attachable and a second one Switchable friction clutch on and off a transmission Bare flywheel, which is relative to a rolling bearing are rotatably mounted to each other and between which one Damping device is provided in the circumferential direction effective energy accumulators, which are made by components of the first flywheel formed annular space added are.

Such torque transmission devices with one split or dual mass flywheel have in the vehicle use generally proven and are so far, especially at Vehicles where the axial space is not so extreme is cramped, as is the case with those with a transverse arrangement Drive unit motor and gearbox is often the case, use Det, namely mainly in vehicles with longitudinal arrangement engine and transmission. For vehicles with very limited  tem installation space for the drive unit, in particular for those with a transverse arrangement of engine and transmission could such two-mass flywheels, precisely because of the limited Space, not in the technically appropriate Enforce wise.

The present invention was based on the object Torque transmission device to create the extreme has small axial dimensions and therefore also for the Use with transversely installed drive units (motor and Gear) is suitable. In addition, a flawless Storage of the flywheels relative to each other and a optimal function and the achievement of optimal torque and damping rates can be guaranteed. Furthermore, the Furniture inexpensive to manufacture and easy to assemble be. Furthermore, the torque transmission device both compared to those generated by the internal combustion engine Torsional vibrations and axial vibrations optimally isolated be.

This is achieved according to the invention in that the ring-shaped space surrounding or delimiting components that the major part of the dynamic or mass inertia can apply momentum from one with the output shaft the internal combustion engine, such as. B. the crankshaft, connectable ren, membrane-like component are worn. The membrane-like Component has a much lower material thickness ke as the components delimiting the annular space. This  enables a particularly compact construction in the axial direction wise because by using a thin membrane that can over relatively wide areas of the radial extent of the torque transmission device, the first Flywheel mass at least radially within the energy accumulator can be kept relatively narrow. Especially before it can be of some benefit if the annular space, the the energy accumulator takes up, is toroidal and radially inwards up to a maximum of half of the radi alen extension of those provided on the second flywheel Extends friction surface for a clutch disc, that means So that the toroidal space is at most up to the middle leren friction diameter of the aforementioned friction surface extends.

For the structure and function of the torque transmission device, it can be particularly advantageous if the radially outer, annular space by two in essential shell-shaped components made of sheet metal can be made, is formed. Particularly advantageous it can be if the membrane is radially outside with the Internal combustion engine, shell-like component fixed connected is. Such a connection can be made using Riveting, welding, caulking or the like respectively.

The membrane can advantageously be disc-shaped and in be resilient or resilient in the axial direction. A such a membrane can e.g. B. made of spring steel.  

An advantageous embodiment of the torque transmission device can be made possible by the membrane axially plate or potted. The membrane can do this have a radially outer annular region which axially in the direction of the internal combustion engine relative to one further radially inward, annular area of the mem bran is offset. This offset of the membrane can also the annular or toroidal space in the direction of Internal combustion engine are offset. It can be useful be if this offset is chosen such that the longitudinal axes of the power spokes received in the toroidal space cher at least approximately at the same axial height as that radially further inward, annular areas of the Membrane come to rest. This allows the second swing be brought very close to the membrane, so that at least radially within the annular or toroidal space a very compact construction in the axial direction is possible.

Radially inside, the membrane can have an axial shoulder, on which the second flywheel rotates via a bearing is included. This axial approach can be a washer shaped member to be attached, the membrane with radial inner areas between an end face of the axial Approach and the disc-shaped component to be clamped can. The disc-shaped component, the radially inner one Areas of the membrane and the approach can, for. B. means Rivet connections, be connected to each other. When screwing on ben the torque transmission device to the output shaft  le of the internal combustion engine, the membrane becomes additional between the disc-shaped component and the axial approach by the axial forces exerted by the screws trapped. It can be special for building the facility be useful if the axial approach on the focal Engine side of the membrane is provided.

It can be particularly useful for building up the torque transmission unit when the second flywheel Torque transmission means carries in the ring or Intervene toroidal space and with the energy stores work together. The torque transmission means can be articulated on the second flywheel. To optima len damping of the occurring torsional vibrations or torque it can be particularly useful if the torque transmission means with the second Flywheel rotatable via another damping device are coupled. For some applications, it can be useful if the additional damping device Slip clutch is. For other applications, however, it can also be advantageous if the further damping device is a spring-loaded, torsionally elastic damper.

A particularly compact construction of the torque transmission According to a development of the invention, the device can be provided by ensuring that the as a torque limiter designed slip clutch immediately radially within the Spring arrangement is provided in the toroidal space. Especially  ders advantageous it can be if this Torque limit clutch radially outside with a clutch disc interacting friction surface of the second flywheel is arranged. It can also be used for setting up the facility be advantageous if the further damping device is axial provided between the membrane and the second flywheel is.

For the design and operation of the fiction moderate torque transmission device it can continue from Be an advantage if between the first and second flywheels a seal or sealing point is provided by the installed in the tensioned, membrane-like component is opened. The seal or the sealing point can be designed in an advantageous manner such that they between arranged two relatively rotatable components is net and due to the axial preload of the membranarti gene component generates a basic friction that is parallel to the Feathers is effective. The membrane can advantageously like component be arranged so that it is the two Flywheels braced in the axial direction. The axial force applied by the membrane-like component the rolling bearings are intercepted. Advantageously can the membrane-like component in such an elastic preloaded condition that it is installed on the components forming an annular or toroidal region exerts an axial force in the direction of the internal combustion engine.  

Further advantageous design features that in Verbin dung with the preamble of claim 1 also for itself can represent independent invention are in the following explained in connection with the drawings.

Referring to Figs. 1 to 4, which enlarged scale sections of the invention Drehmomentübertragungsein directions show the invention will be explained in more detail.

In Fig. 1 a divided flywheel 1 is shown, the one has, on a not-shown crank shaft of an internal combustion engine can be fastened, the first or primary flywheel mass 2 and a second or secondary flywheel mass 3. On the second flywheel 3, a friction clutch 4 is under Zwischenle supply a clutch disc 4 a fixed, over which a flat can not appropriate to-signed gear and be uncoupled. The flywheels 2 and 3 are rotatably mounted to each other via a bearing 6 , which is arranged radially outside of the stanchions 5 for carrying out fastening screws for mounting the first flywheel 2 on the output shaft of the internal combustion engine. Between the two flywheels 2 and 3, the damping device 7 is effective, has the compression coil springs 8, 9 forms a in an annular space 9, the radially outer region of a torus-like, are accommodated. The annular space 9 is at least partially filled with a viscous medium, such as oil or fat.

The on the cross section of the springs 8 essentially nestled toroidal region 9 a is mainly formed by two shell-like housing parts 10 , 11 . The housing parts 10 , 11 consist of sheet metal parts, which are connected radially outside over their circumference by a weld 12 .

The shell-like body 10 , which partially encompasses the circumference of the springs 8 and is provided on the internal combustion engine side, is firmly connected with radially inner regions 12 to a disk-shaped membrane-like component 13 via rivet connections 14 . Radially on the inside, the diaphragm 13 carries an axial projection 15 pointing in the direction of the second flywheel 3 , on which the roller bearing is accommodated in the form of a single-row ball bearing 6 a. The outer ring of the rolling bearing 6 a carries, with the interposition of thermal insulation 16 , the second flywheel 3 . The inner region 17 of the membrane 13 is clamped axially between the shoulder 15 and a disk 18 . For this purpose, the disk 18 and the projection 15 can be axially fixed to one another via rivet connections. These rivet connections can also serve to hold the washer 19 , which secures the bearing 6 a on the axial extension 15 .

The two shell-like bodies 10 and 11 are designed such that they each extend at least approximately over half the axial extent of an energy accumulator 8 . The sheet metal body 11 , which is essentially C-shaped or semicircular in cross-section, extends radially inward, starting from the welded connection 12 . The shell-like or by the two parts body 10, 11 limited toroidal region 9 is a - viewed in the circumferential direction - divided into individual receptacles 20 in which the force storage means are provided. 8 The individual receptacles 20 , viewed in the circumferential direction, are separated from one another by loading areas 21 , 22 for the energy accumulators 8 , which are formed by pockets embossed into the shell-like bodies 10 , 11 designed as sheet metal molded parts. The receptacles 20 for the springs 8 are formed by indentations introduced into the bodies 10 , 11 .

The provided on the second flywheel 3 Beaufschla supply areas for the energy accumulator 8 are formed by at least one attached to this flywheel 3 Beaufschlagungsmit tel 23 , which serves as a torque transmission element between the energy stores 8 and the flywheel 3 . The loading means 23 can be formed by an annular component or else by individual segments distributed over the circumference. When using an annular component 23 , this can have an inner, self-contained, annular region 24 which is connected to the second flywheel 3 , for. B. via blind rivet connections 25 , which is verbun and which supports the radially outer arm 26 , which extend radially between ends of energy stores 8 and in the idle state of the flywheel 1 , that is to say when no torque is transmitted, axially directly between the application areas or pockets 21 , 22 are located.

The arrangement of which cooperate with the clutch disc 4 a, the friction surface 27 of the flywheel 3 , in relation to the design of the transmission element 23 , is such that more than 50% of the radial extent of the friction surface 27 is limited radially within the transmission element 23 , smallest diameter 28 are. This allows the fasteners such. B. the rivets 25 , for fixing the loading agent or the transmission element 23 on the flywheel 3 are attached radially relatively far outside. As a result, the design of the annular space 9 is made possible, which ensures that this space 9 does not extend radially inward beyond the average friction diameter 29 of the friction surface 27 . As a result, the diaphragm 13 adjoining the internal combustion engine and the second flywheel mass 3 can lie directly opposite one another radially within the annular space 9 over a relatively large radial extent, with the formation of an intermediate space or air gap 30 , that is to say they can be directly adjacent, thereby causing one in the axial direction very compact design of the flywheel 1 , clutch 4 and clutch disc 4 a existing unit is made possible. Depending on the application, the space 30 can have an axial width between 0.5 and 6 mm. It is expedient if this intermediate space 30 has a gap width of between 1 and 3 mm over at least 50% of its radial extent.

The thickness of the membrane 13 is significantly less than that of the shell-like components 10 , 11 , which form the toroidal loading region 9 a and are carried by the membrane 13 . The thickness of the membrane 13 can be of the order of 0.5 to 3 mm, and it is expedient in many cases if the thickness of the membrane 13 is of the order of between 0.7 and 1.5 mm. The starting material for forming the two shell-like bodies 10 and 11 can have a thickness which is on the order of 4 to 8 mm. The membrane 13 has a radially inner, annular region 31 and a radially outer, radially narrower annular region 32 , which is axially offset in the direction of the internal combustion engine relative to the inner region 31 , so that the membrane 13 has a potted or plate-like shape. The membrane 13 extends radially outward into the regions of the fastenings or rivet connections 25 .

Advantageously, the intermediate space 30 can be used to cool the flywheel 1 , specifically by passing a cooling air flow through this intermediate space 30 . To generate such a cooling air circulation, the second flywheel 3 has radial openings 33 radially inside the friction surface 27 , which, starting from the side of the flywheel 3 facing the clutch 4 , extend in the direction of the radial region 31 of the motor-side diaphragm 13 and into the Open space 30 so that the air flow flows directly past area 31 or is directed towards this area 31 . In addition or as an alternative to the openings 33 , the radially extending region 31 of the membrane 13 can have axial passages 34 which connect the intermediate space 30 to the side of the membrane 13 facing the motor. In the circumferential direction between the fastening points 25 for the transmission element 23 , the flywheel 3 has in the direction of the friction surface 27 directed axial recesses 35 which serve to generate a radial passage to the outside for the cooling air flow. The radial passages 35 and / or the axial recesses 33, viewed in the circumferential direction, can be elongated and have a fan-like shape to increase the cooling air throughput.

A radially inner and a radially further outer seal 36 , 37 are provided to seal the annular chamber 9 , which is partially filled with viscous medium. The seal 36 is designed like a membrane and is supported axially on the membrane 13 . Radially on the outside, the seal 36 merges into a radially extending region 38 , which is circular and is clamped between the circular region 24 of the flange 23 and, viewed in the circumferential direction, between the ventilation channels 35 on the flywheel 3 , the projections 39 .

The radially outer seal 37 is annular and can be formed by a plastic ring 37 , which is positioned in a receptacle in the form of a groove 40 . It is useful if the sealing ring 37 made of a hit zebesteste material such. B. polyamideimide or Teflon. The receptacle or groove 40 for the sealing ring 37 is introduced into the radially inner regions of the component 11 . The annular region 24 of the flange 23 has a radially outer section 41 which protrudes radially from the contours of the second flywheel 3 and is used for the radial support of the sealing ring 37 . The end of the ring 37 on the area 41 can be done by axially prestressing the membrane 13 . For this purpose, the membrane 13 can be clamped during the assembly of the divided flywheel 1 such that it exerts a force component on the outer components 10 , 11 in the direction away from the second flywheel mass 3 . Alternatively or in addition to the axial force exerted by the membrane 13 , the plate-like spring-like or membrane-like seal 36 can apply the force required for the sealing engagement of the sealing ring 37 by corresponding axial pre-tensioning. The axial bracing forces between the two flywheels 2 and 3 are absorbed by the roller bearing 6 . By the tension of the diaphragm 13 made of spring plate in the direction of the internal combustion engine, the primary swing mass 2 attaches via the seal 37 to the flange 3 connected to the secondary swing mass 23 , so that the sealing stel le effective in parallel to the action of the springs 8 Basic friction can be generated. At the same time, the sealing point or the sealing ring 37 takes over the axial guidance of the first centrifugal mass 2 relative to the second centrifugal mass 3 .

The design and arrangement of the seals 36 , 37 ensures that the free space or air gap 30 , which is provided directly between the two flywheels 2 and 3 , has a relatively large radial extent, whereby the cooling of the flywheel 27 having the friction surface 3 can be significantly improved.

To reduce the heat transfer from the flywheel 3 to the annular space 9 between the can with the Kraftspei Chern 8 cooperating flange 23 and the flywheel 3, an intermediate layer of a thermally insulating material such. B. from a heat-resistant plastic material can be seen before. Instead of an intermediate layer, the seal 36 can also be produced from a material which has a low thermal conductivity. As a result, the radial regions 38 of the seal 36 , which are clamped axially between the flywheel 3 and the flange body 23 , act as thermal insulation.

The shell-type body 11 carries a starter ring 42 which is connected via a welded connection to the shell body. 11 The starter ring gear 42 extends axially and encompasses the outermost contours of the flywheel 3 in the circumferential direction.

Together with the clutch unit, consisting of the clutch 4 and the clutch disc 4 a, the two-mass flywheel shown in FIG. 1 1 forms a structural unit A, which is pre-assembled as such, are so shipped and stored and easier on the crankshaft of an internal combustion engine in particular and can be screwed on rationally. This Bauein unit also has already integrated the bearing 6 a, which is attached to the neck 15 , which in turn is provided on the first flywheel 2 . In the bores 5 of the disks 18 , 19 , the membrane 13 and the extension 15 , fastening screws 43 can also already be preassembled or contained, in the form of Allen screws. The screw heads are in the non-screwed state axially in such a position between the tongues 44 a of the plate spring 44 of the clutch 4 and the disk 19 , and the threaded areas 43 a are dimensioned and, as described below, held so that they are axial do not protrude beyond the contour 45 of the first flywheel mass 2 , that is to say the contour facing the motor. The screws 43 are held in this position and captive in the unit or unit A, z. B. by compliant elements that hold the screws 43 in such a position that the threaded areas 43 a do not protrude beyond the disc 18 . These elements are dimensioned such that their holding force is overcome when the screws 43 are tightened.

The clutch plate 4 a is the second flywheel 3 is clamped and in a pre-centered with the rotational axis of the crankshaft position between the pressure plate 4 b and friction surface 27 moreover in such a position that provided for the passage of the screw heads 43 of the screws 43 b in the clutch disc 4 a Openings 46 are in such a position that these heads 43 b can be moved during the assembly process of the unit on the crankshaft of the internal combustion engine. Openings 48 are also provided in the plate spring 44 in the region of their tongues 44 for the passage of a screwing tool. The openings 48 in the plate spring 44 , 46 in the clutch disc 4 a and 5 in the flywheel 2 overlap each other in the axial direction in such a way that an assembly tool, such as an Allen wrench, pass perfectly through the openings 48 , 46 and into the Recesses of the heads 43 b of the screws 43 can engage.

The flywheel 101 shown in FIG. 2 has a damper 107 with effective in the circumferential direction of the coil springs 108, a relative rotation between the two flywheel masses 102, resist 103, and in a toroidal chamber 109 a are added up. The toroidal space 109 a is divided in a similar manner, as described in connection with FIG. 1, into individual, segment-shaped receptacles for the springs 108 , wherein exposure areas for the springs 108 are provided between the individual receptacles. The components 110 , 111 delimiting the toroidal space 109a are designed in a similar manner to that described in connection with the components 10 , 11 of FIG. 1 and are connected to the output shaft via a flexible, disc-shaped membrane 113 in the axial direction Internal combustion engine connectable. On the radially inner regions of the membrane 113 , an axial extension 115 is fastened, on which a roller bearing 106 a for the rotatable mounting of the second flywheel 103 is received. The flywheel 103 that can be connected to the input shaft of a transmission is divided into two disk-shaped components 103 a, 103 b, which are firmly connected to one another via rivet connections 125 . The outer bearing ring 150 is received in a central recess 151 of the disk-like component 103 b having the friction surface 127 . To axially secure the bearing 106 a, the two disk-like components 103 a and 103 b overlap the radially outer bearing ring 150 on both sides with a radial section 152 , 153 . Axially between the roller bearing 106 a and the membrane 113 , a friction device 154 is provided which, arranged one behind the other in the axial direction, has a plate spring 154 a, a pressure plate 154 b and a friction ring 154 c. The control or rotation of the friction ring takes place via the disk-like component 103 a directly adjacent to the membrane 113 .

The output part of the torsionally elastic damper 107 is formed by an annular component 123 which engages with its radially outwardly directed arms 126 in the toroidal space 109 a, namely, viewed in the circumferential direction, between the springs 108 . The flange-shaped, ring-shaped component 123 is part of a slip clutch 155 , which serves to limit the transmissible torque and is arranged radially directly inside the springs 108 . To form the slip clutch 155 , the inner ring region 124 of the flange 123 is axially clamped axially between a radial collar 156 provided on the outer circumference of the disk-shaped component 103 a and a pressure ring 157 provided on the other side of the flange 124 , with the interposition of friction rings 158 . For radial guidance or centering of the flange 124 and the pressure ring 157 , the disk-shaped component 103 a has a radial support shoulder 159 radially on the outside, which can form a cylindrical surface. The radial collar 156 extends between the component 110 delimiting the toroidal space 109 a and the flange 123 . The pressure ring 157 is acted upon by a plate spring 160 , which is arranged axially between the outer regions of the disk-shaped component 103 b and the bowl-shaped component 111 , which delimits the toroidal space 109 a. The component 103 b of the second flywheel 103 carries a starter ring gear 142 on the outside, on which the plate spring 160 is supported axially with its radially outer regions. By the axial force of the plate spring 160, the ring gear is clamped between the Tellerfe 142 160 and on the other side of the ring gear 142 on the member 103 b integrally formed shoulder 161st The resulting frictional engagement between the starter gear 142 and the second flywheel mass 103 is sufficiently large to ensure an annealing so that a shrinking of the ring gear 142 can be omitted. The plate spring 160 is supported on the pressure ring 157 radially on the inside. For this purpose, the pressure ring 157 has axial cams 157 a, which are acted upon by arms 160 a formed on the inner circumference of the plate spring 160 . The cams 157 a and bracket 160 a are, viewed over the circumference, evenly distributed and engage in recesses or recesses 161 of the disk-shaped component 103 b. As a result, both the plate spring 160 and the pressure ring 157 are secured against rotation with respect to the second flywheel 103 .

As is apparent from Fig. 2, both the torsionally elastic dampers 107 and 155 are provided radially directly within this rotationally elastic damper 107 provided outside the slip clutch friction surface 127 of the second flywheel mass 103.

The slip clutch 124 also serves to seal the space which is at least partially filled with a viscous medium, such as grease or oil. Another seal 137 , which can be designed similarly to the seal 37 according to FIG. 1, is provided between the outer regions of the pressure ring 157 and the inner regions of the shell-shaped sheet metal body 111 . The sealing ring 137 has a rectangular cross section and is accommodated in appropriately adapted incisions or grooves in the pressure ring 157 and the component 111 . The membrane 113 causes, in a similar manner, as described in connection with FIG. 1, an axial loading of the sealing ring 137 .

For cooling the torque transmission unit 103 a, 103 b air guide channels 162 are provided in the area of the parting plane between the two secondary flywheel mass construction, which are distributed over the circumference of the second flywheel mass 103 . The radially extending air duct channels 162 are formed by axial recesses in the component 103 a adjacent to the membrane 113 . These air ducts 162 open radially on the inside into axial openings 163 of the component 103 b having the friction surface 127 . These openings 163 are open radially within the friction surface 127 towards the clutch side. The air entering through the openings 163 on the clutch side is guided radially outward via the channels 162 and flows radially outward in the area of the plate spring 160 between the two flywheels 102 , 103 . The openings 163 and the channels 162 can be elongated in cross-section in the circumferential direction. Through the cooling measures or ventilation measures 162 , 163 , although the annular component 103 a is in communication with the annular space 109 a containing a viscous medium, it is ensured that an excessive temperature in the space 109 a is avoided. This is due to the fact that the air flowing through the openings 163 , 162 results in effective cooling of the disk-shaped component 103 a and in particular of the disk-shaped component 103 b having the friction surface 127 . The construction according to FIG. 2 also has the advantage that the torque limiting clutch or slip clutch 155 is relatively far away from the friction surface 127 for the clutch disc, as a result of which a negative thermal influence is largely avoided. The ventilation channels 162 and the openings 163 can be dimensioned such that they act as a thermal barrier or that the webs remaining between these channels 162 or through openings 163 are so small in cross section that they act like a throttle, which means that they only a very small amount of the heat energy generated on the occasion of a clutch operation can be transferred from the secondary component 103 b into the secondary component 103 a. As a result, a negative thermal influence on component 103 a is largely avoided.

In the torque transmission device 201 shown in FIG. 3, similar to the device according to FIG. 2, a torsionally elastic damper 207 is provided radially on the outside and a slip clutch 255 is provided radially further inside. The springs 208 of the damper 207 are accommodated in a similar manner in the shell-like housing parts 210 , 211 , as was described for the springs 8 in connection with FIG. 1.

The flange-like component 223 forming the output part of the damper 207 also forms the input part for the slip clutch 255 . The flange-like component 223 is clamped axially between two radially offset support regions 256 , 257 . The radially inner support region 256 is formed by an outer ring region of a ring-like or disk-shaped component 265 , which is connected via a radially inner fastening region via rivet connections 266 to the transmission-side flywheel element 203 . Component 265 is supported on the end face of an axial extension 267 of flywheel 203 . On the axial extension 267 , the resilient, flange-like component 223 is received and centered. A friction ring 258 is provided axially between the support region 256 and the resilient component 223 . The radially outer support 257 is formed by a disk-shaped component which is supported on the flywheel element 203 . For this purpose, the flywheel element 203 has an axial recess which forms a radial support shoulder 268 on which the disk-like component 257 is received. The disk-like component 257 is secured against rotation with respect to the flywheel element 203 . For this purpose, the disc-like element 257 formations, z. B. on the radially inner edge Ausle ger, own, in appropriately adapted formations, such as. B. recesses on the flywheel element 203 , engage. Between the disc-like support part 257 and the areas of the plate spring-like flange 223 that are supported thereon, a friction ring 258 a, which bears directly on the resilient flange 223, is provided.

The structure shown in FIG. 3 also allows an in particular axially compact design of the torque-transmitting means 201. In the radial area of the slip clutch 255 in particular, the torque transmission device 201 requires a small axial installation space.

To seal the chamber 209 , a sealing ring 237 is provided between the flange 223 and the shell-like component 211 , which is arranged and is similar to the sealing ring 37 according to FIG. 1.

Further, the chamber 209 which extends radially between the diaphragm 213 and the flange 223 into the area of storage 206 is also used for sealing the flange 223. Sealing takes place between the axially clamped or frictionally engaged components 265 , 258 and 223 . Due to the construction according to the invention, the shell-like housing part 211 , which serves both to form a part of the toroidal space 209 a and to guide and act upon the springs 208 , can be made relatively small.

The housing part 211 has a shoulder 261 formed thereon, on which a starter ring gear 242 is received.

To cool the two-mass flywheel 201 , the second flywheel 203 has radial recesses 263 axially within the friction surface 227 , which, starting from the friction surface side of the flywheel side 203 , axially widening up to that between the flange 223 and the back of the flywheel mass 203 existing air gap or free space 262 extend. The annular free space 262 extends radially outwards to ventilation channels 235 , which are formed by recesses 235 introduced into the rear side of the flywheel 203 . The ventilation channels 235 are open radially outwards and open into a provided between the schalenför-shaped component 211 and the second flywheel 203 NEN air gap or clearance 262 a, the area of the ring gear in the area between the outer contours of the flywheel 203 and the inner jacket 242 opens. The radial ventilation channels 235 are axially covered by the disk-shaped component 257 .

Due to the cooling air circulating through the free spaces 262 and 262 a, it is avoided that both the axially tensioned flange 223 axially between the support regions 257 and 256 and the viscous medium, such as oil or fat, present in the toroidal region 209 a, of an impermissibly high temperature get abandoned.

Radially within the rivet connections 266 , a friction device 254 is provided, which is constructed and arranged similarly to the friction device 154 according to FIG. 2. The control of the friction ring of the friction device 254 takes place via the inner regions of the disk-like component 265 . For this purpose, the disc-like member 265 has radially inner recesses which engage in the radial arm of the friction ring.

The four-mass flywheel 301 shown in FIG. 4 differs from the embodiment according to FIG. 3 essentially in that the flange-like component 323 is firmly connected to the flywheel 303 radially within the friction surface 327 of the flywheel 303 via riveted connections 366 . The second flywheel 303 in turn has axial passages 363 which open into radially extending channels 335 which are formed by depressions in the rear of the second flywheel 303 . The radial channels 335 and the axial passages 363 are closed in the axial direction by the flange-like component 323 , so that the air is forced through the radial channels 335 . The first flywheel 302 is connected in a similar manner as described in connection with FIG. 1, via a membrane 313 with the output shaft of an internal combustion engine.

The membranes 213 and 313 are also axially preloaded, so that the seals 237 , 337 are pressed axially against the respective flange 223 , 323 .

In the embodiments according to FIGS. 1 to 4, a wear protection is provided between the helical springs and the regions of the first flywheel supporting the helical springs, which partially surrounds the radially outer regions of the springs. This wear protection is identified by 68 in FIG. 1. This wear protection can be formed by individual, in the energy storage receptacles, circular arc-shaped sheet metal parts. In one embodiment, e.g. Wherein the membrane is mounted on the side facing the output part of the damper 207 and the flange 223 side of the cup-like member 210 213 example of FIG. 3, in an advantageous manner, the membrane could be 213 extended radially outwardly and the springs 208 enveloping Have a shape so that the wear protection 268 is formed in one piece with the membrane 213 .

The inventive design of a torque The transmission device can be flexible, that is to say bend compliant arrangement of a dual mass flywheel on the Output shaft of an engine can be achieved because the with the Internal combustion engine connectable flywheel or the one toroid-like receiving space for the components forming the springs over a relatively thin membrane but axially fixed compliant with the output shaft, like the crankshaft one Internal combustion engine, is or are and continue to be the via a switchable friction clutch with the input shaft of a transmission connectable secondary flywheel, which over a roller bearing is rotatably mounted, due to which, if only very small, internal axial and / or small wobble can perform vibrations, namely against the spring wire kung the membrane. This makes the overall unit of axial and Bending vibrations of the output shaft, such as the crankshaft an internal combustion engine, decoupled.

The invention is not illustrated and described on the NEN embodiments limited, but includes in particular other variants, which by combining individual, in Described connection with the various embodiments ben features or elements can be formed.

Claims (20)

1. Torque transmission device with a first, attachable to the internal combustion engine, and a second flywheel that can be switched on and off via a clutch, which are rotatably supported by a rolling bearing relative to each other and between which a damping device is provided with effective energy stores in the circumferential direction which are accommodated in an annular space formed by components of the first flywheel, characterized in that the components delimiting the annular space are carried by a membrane-like component which can be connected to the output shaft of the internal combustion engine. 2. Torque transmission device according to claim 1, characterized in that the radially outer annular space by two, essentially bowls shaped components is formed. 3. Torque transmission device according to claim 2, characterized in that the membrane radially outside with  the shell-like facing the internal combustion engine Component is firmly connected. 4. Torque transmission device according to one of the An Proverbs 1 to 3, characterized in that the membrane axially plate or potted. 5. Torque transmission unit according to one of claims 1 to 4, characterized in that the membrane has a has radially outer, annular region, the axial towards one of the internal combustion engines radially inner annular area of the membrane is offset. 6. Torque transmission device according to one of the An Proverbs 1 to 5, characterized in that the membrane radially inside carries an axial approach on which the second flywheel rotatably received on a bearing men is. 7. Torque transmission device according to claim 6, characterized in that at the axial approach disk-shaped component is attached and the membrane with radially inner areas between an end face the axial approach and the disc-shaped component is jammed. 8. Torque transmission device according to claim 6 or 7,  characterized in that the axial approach on the The side of the membrane facing away from the internal combustion engine hen is. 9. Torque transmission unit according to one of claims 1 to 8, characterized in that the second flywheel se carries torque transmission means in the Intervene in an annular space and use the energy accumulators work together. 10. Torque transmission unit according to one of claims 1 to 9, characterized in that the torque transfer means articulated on the second flywheel are. 11. Torque transmission unit according to one of claims 1 to 9, characterized in that the torque transfer with the second flywheel over a further damping device are rotatably coupled. 12. Torque transmission device according to claim 11, characterized in that the further damping device tion is a slip clutch. 13. Torque transmission device according to claim 11, characterized in that the further damping device a spring-loaded, torsionally elastic damper is.   14. Torque transmission device, in particular after one of claims 1 to 13, characterized in that that a slipping clutch designed as a torque limiter immediately radially within the spring arrangement in annular space is provided. 15. Torque transmission device according to claim 14, characterized in that the torque limitation clutch radially outside with a clutch disc interacting friction surface of the second flywheel is provided. 16. Torque transmission device according to one of the An Proverbs 11 to 15, characterized in that the additional damping device axially between the membrane and the second flywheel is provided. 17. Torque transmission device according to one of the claims che 1 to 16, characterized in that between the first and a second flywheel is provided with a seal, by the preload of the membrane-like component is applied. 18. Torque transmission device according to one of the claims che 1 to 17, characterized in that by the axial preload of the membrane-like component Basic friction is generated.   19. Torque transmission device according to one of the claims che 1 to 18, characterized in that the membrane the two flywheels in the axial direction tense. 20. Torque transmission device according to one of the claims che 1 to 19, characterized in that the of the membrane-like component applied axial force the rolling bearing is intercepted.