DE4117579B4 - Torque transfer device - Google Patents

Abstract

Torque transmission device with a first (2, 202) on an output shaft of an internal combustion engine fastenable and a second (3, 203), with the input shaft a transmission connectable, a friction surface (32) for a clutch disc (5, 205) having flywheel, which via a bearing (6, 206) rotatably mounted to each other and a damping device (9, 209) drivingly coupled are, wherein the damping device (10, 210) springs, which in a by components (13, 19; 213, 219) of the first flywheel radially outwardly limited ring-like Space (11, 211) recorded and a relative rotation of the flywheel masses are elastically deformable, wherein the first flywheel (2, 202) a sheet metal molding (13, 213), which has a radially extending flange-like portion (14, 214) for attachment to the output shaft the internal combustion engine has, the radially outward in the direction of the second Flywheel (203) axially extending portions (218) carries, the for limiting the annular space (211) radially outward serve and in which also a radially inward ...

Description

The The invention relates to a torque transmission device, such as It has become known for example from DE-OS 37 21 705. These has a first, on an output shaft of an internal combustion engine attachable flywheel and a second, with the input shaft a gear connectable a friction surface for a clutch disc having Flywheel that over a storage rotatably mounted to each other and a attenuator are drivingly coupled, wherein the damping device Having springs in one through components of the first flywheel radially outward limited, ring-like space added and in a relative rotation the flywheels are elastically deformable, the first flywheel a sheet metal part having a radially extending flange Area for attachment to the output shaft of the internal combustion engine own, the radially outside in the direction of the second flywheel axially extending areas wearing, the for limiting the annular space radially outward serve and in which also a radially inwardly extending wall is attached. Such torque transmission devices with a split or dual mass flywheel have in the vehicle use generally proven and are so far in particular in vehicles in which the axial space is not so ex cramped extreme, as with those with transverse arrangement the drive unit engine and transmission in many cases the Case has been used, namely mainly on vehicles with longitudinal arrangement of engine and transmission. For Vehicles with very limited installation space for the drive unit, in particular for such with transverse arrangement of engine and transmission, such dual mass flywheels could even because of limited space do not enforce them in a technically appropriate way.

Of the The present invention was based on the object, a torque transmission device to create, which has small axial dimensions and thereby also for the application with transversely mounted drive units, consisting from engine and transmission, is suitable. In addition, a flawless Storage of the flywheels relative to each other and an optimal Function as well as the achievement of optimal torque and damping rates guaranteed be. Furthermore, the device should have a simple structure as well as inexpensive to produce and easy to assemble.

This is according to the invention achieved in that the annular space predominantly radially outside the outer contours the second flywheel is arranged so that the sheet metal part and the second flywheel radially inwardly of the annular space via a relatively large radial Extension to form a gap-shaped gap immediately are opposite.

Thereby can the two flywheel masses axially closer each moved be, whereby the required space can be reduced.

to Reduction of the required axial space for a torque transmission device according to the beginning mentioned type can also be used a structural design, at the first flywheel - in viewed in the axial direction - one hollow body forms, which at least substantially axially the second flywheel receiving, wherein radially outer contours the second flywheel to close the ring-like space Serve so that the sheet metal part and the second flywheel radially within the annular space over a relatively large radial Extension to form a gap-shaped gap immediately are opposite.

at an embodiment of the invention the usual existing and radially relatively far inwardly extending flange, which acts on the energy storage serves, not present, so that in the axial direction especially crowded Construction allows becomes.

at Torque transmission devices with at least to the atmosphere outward or outward essentially sealed and at least partially with a viscous medium filled, annular Space for storing energy storage, it can be particularly advantageous be if a seal by at least one between one Space forming component of the first flywheel and a component the second flywheel provided seal takes place. It can be useful be there when the seal of one of the space forming components worn.

For the construction the torque transmitting device It may be particularly advantageous if the clutch cover the on the second flywheel mounted clutch the second flywheel envelops. Therefor the clutch cover may have an axially extending section, which axially overlaps the second flywheel and at least with this for torque transmission is attached. The lid can be on the outer contour of the second

Flywheel be secured so that it is centered with respect to this. The securing of the clutch cover on the second flywheel can, for example by means of welding or impressions on the lid, in the corresponding off recesses or grooves of the second flywheel intervene done.

According to one further design feature may be in a torque device, at the annular Space is at least substantially sealed or closed and the second flywheel has a friction surface for between this flywheel and a pressure plate of the friction clutch clamped Clutch disc advantageously the sealed space itself radially inward to a maximum of half of the radial friction surface extent extend. this makes possible a particularly compressed in the axial direction construction, since the energy storage together with their Beaufschlagungsbereichen radially outward can be offset.

Advantageous It may be when the second flywheel at least over the half the radial extent of its friction surface the flange-like area the first flywheel is adjacent at a small distance, preferably directly opposite or adjacent, with the formation of a small gap. The application of the described inventive features allows for many use cases to design the device such that the second flywheel almost over their entire radial extent the radial, flange-like area the first flywheel is adjacent. Furthermore, by application the constructive invention Features the first flywheel radially within its annular space as a hollow body be formed, the second flywheel at least substantially axially receives.

According to one Another design feature, the roller bearing radially inside and at least approximately at the axial height the friction surface lie, that means that the friction surface in the axial Extension of the roller bearing or of the rolling bearing is provided, whereby the axial extent of the second flywheel relatively small can be held.

Of the between the two momentum existing gap can in advantageous manner for carrying out a cooling air flow serve. Appropriately be there when in the radial flange area of the first Flywheel, preferably in the region of the opposite Sections of the two masses, axial openings or Recesses are provided, which communicate with the intermediate space can stand. Furthermore, it may be appropriate if the second flywheel radially within its friction surface or radially outside the rolling bearing axial passages or breakthroughs has, which can also open into the gap. For further improvement the cooling the torque transmitting device the second flywheel mass can have further passages from the intermediate space go out and radially outside the friction surface to connect the connectable with the transmission flywheel. A further optimization of cooling can be achieved in that the radially inner passages and the radially outward lying passages the second flywheel over air slides or ventilation grooves, the provided in at least one of the mutually facing surfaces of the flywheels are interconnected. In an advantageous way, these can air slides turned away on the friction surface Side of the second flywheel be provided, as they then in easier Can be poured. The aforementioned Measures for Generation of a cooling air flow can also be applied individually or in any combination.

According to one Development of the invention, the first flywheel of the torque transmission device a radially extending, disc-shaped area for attachment have on the output shaft of the internal combustion engine, the radial Outside axially directed or extending in the direction of the second flywheel Wearing areas, which the annular Space radially outward Shen limit, and then a radially inward running Wall is provided, the smallest inner diameter is preferably larger as the outer diameter the friction surface the second flywheel. By such a structure can also guaranteed be that the second, with the transmission connectable flywheel in the of the annular Room enveloped immerse the inner space of the first flywheel at least partially axially can. It can be for some use cases be advantageous, although radially outer contours or areas the second flywheel for forming or closing the annular space be used. It may be particularly useful if the outer friction diameter the clutch or the clutch disc, which with the second flywheel interacts smaller than the diameter on which the radially innermost areas of the energy storage are, as a result an at least partial axial and radial integration of the second Flywheel and possibly also the clutch disc or the Friction clutch in the hollow body forming a first flywheel allows becomes.

The radially inwardly extending wall of the first flywheel can embrace in an advantageous manner axially extending portions of the clutch cover.

to Sealing the annular Space radially inward, can be advantageously in the between the two momentum existing gap one Seal be provided. This radially inner seal can the between the two masses existing gap or

gap across from the radially further outside lying annular Seal space and can at least approximately in the radially outer region the friction surface provided connectable to the internal combustion engine flywheel be. This seal can be arranged to be between the first flywheel and the clutch cover is effective.

The supported by the first flywheel radial wall for limiting of the annular Space can be designed such that they are radially from the outside curved inwards or arc-like, where appropriate can, if this wall, which is only about half the diameter the energy accumulator may extend radially inwardly through a sheet metal part is formed.

to cooling the torque transmitting device It may be particularly useful if the radially outward lying passages of second flywheel radially between the outer friction diameter of the friction surface of second flywheel or cooperating with this clutch disc and the clutch cover emerge on the clutch side. Appropriately be it when in the area of the outer mounting edge and / or the axial region of the clutch cover passages or Cutouts are provided which cooperate with those of the second flywheel. For cooling the facility can also in the friction surface carrying swinging mass ventilation ducts provided be on the friction surface Abwärtsten side of this flywheel are arranged.

A further consequences for cooling the torque transmission device, the for alone or in conjunction with the measures already described for cooling the torque transmitting device can be used, that in the area of the friction surface of the second flywheel and / or the pressure plate of the friction clutch, which is supported by the second flywheel, axial, in radial Direction extending, open channel-like depressions provided These wells are advantageously both radially outward towards and radially inward over the extent of the corresponding friction surfaces can extend. The channel-like depressions or grooves can thereby in the circumferential direction run inclined and optionally have a curved or arcuate shape.

Especially It may be advantageous if the flywheels are radially inside of the ring-like space for the springs, forming a gap, each other at least essential opposite radial areas or adjoin one another, preferably over at least 50% of the radial Extension of the second flywheel.

A further cost reduction can result from the fact that the the first flywheel worn starter sprocket in one piece with a the annular space forming portion is formed. This Section may be formed such that the starter ring gear engages the clutch cover, at least approximately in axial region in which the clutch disc, which with the second Flywheel cooperates, is provided. This can also be the sprocket forming component an outer, in Have substantially cylindrical area extending itself axially substantially above the entire outer diameter the energy stored in the ring-like space memory extends.

The for fastening torque transmission devices provided on the output shaft of an internal combustion engine to the first flywheel screw holes can generally provided in an advantageous manner on a diameter be smaller than the inner diameter of the rolling bearing, which rotatably supports the two flywheel masses relative to one another.

For some use cases It may also be advantageous if the screw diameter for fixing the first, connectable to the internal combustion engine Flywheel is radially outside the rolling bearing located. In such a configuration, a relatively small and inexpensive bearings be used.

In torque transmission devices with a first, attachable to the internal combustion engine, and a second, via a clutch transmission to a transmission and turn-off flywheel, which are mounted rotatably relative to each other via a rolling bearing and between which a damping device is provided with circumferentially effective energy storage, it can be particularly advantageous if the one cavity for performing an element, such as a transmission shaft, enveloping roller bearing is provided on an at least substantially smaller diameter than the screw holes for the side facing away from the motor side of the one swing Mass forth screwed to fasten the first flywheel to the output shaft of the internal combustion engine and further provided in the other flywheel at least approximately aligned with the Verschraubungsbohrungen through holes, which are dimensioned at least for the passage of a Verschraubungswerkzeuges. For some applications, it may also be expedient if the size of the through holes allows the axial passage of the fastening screws, in particular the screw heads.

For the construction and the function of the torque transmitting device It may be particularly advantageous if the storage at one of the Flywheels provided axial approach encloses. Advantageous it may be, if this axial approach is integral with the corresponding flywheel. For some use cases but it may also be appropriate if that of the rolling bearing surrounded approach by a at the radially inner regions of the corresponding flywheel attached pipe or sleeve-shaped component is formed. This sleeve-shaped component can at the radially inner regions of the corresponding flywheel, which limit a recess to be attached. In an advantageous manner Way can connectable to the output shaft of the internal combustion engine Flywheel carry such an axial approach. It can, however also for many use cases be expedient if the flywheel connectable to the internal combustion engine the carries axial approach or if both flywheel masses each have at least one axial projection, these then overlap axially and radially between them the rolling bearing is arranged.

at Embodiments, where only one of the flywheels an axial approach it may be particularly advantageous if this is a flywheel also carries the annular space containing a viscous medium.

to Positioning of the two flywheel masses relative to each other can be used in a particularly advantageous manner, a rolling bearing whose inner ring seated on the axial extension or extension of one of the flywheel masses and its outer ring wearing the other flywheel, being the largest diameter of the outer ring smaller than the diameter on which the screw holes are arranged. In very tight spaces, it can also be beneficial be, if at least one of the Abwälzbahnen for the rolling elements is integrally formed with a the flywheels, and it may be particularly useful if such Abwälzbahn is formed on the axial projection of the corresponding flywheel, so that this Approach simultaneously forms a bearing ring. For some applications can it for the function be advantageous if the radially outer bearing ring is in one piece with an approach associated with the first flywheel. Advantageous However, it may also be when the radially inner bearing ring is in one piece with the shoulder carried by the first flywheel and the outer race wearing the second flywheel, this outer bearing ring also one piece can be formed with the second flywheel.

A further inventive step, the one very easy handling and installation and inexpensive Manufacture of such dual mass flywheels is that the split Flywheel together with the hitch be aggregate, consisting of coupling and clutch disc, one on the crankshaft of the internal combustion engine attachable and preassembled unit forms, which expediently Furthermore nor the two inertial masses superimposed bearings includes. Appropriately it will be if the unit continues one at the first flywheel provided support flange for the rolling bearing has, in the holes then the mounting screws for attachment the unit already included on the crankshaft, so pre-assembled could be. It may still be appropriate if these mounting screws held captive in the unit are, this captive formed by compliant means may be, the holding force then during assembly, for. B. by tightening the screws, overcome becomes.

According to a further feature, in this preassembled unit, the clutch disc is already clamped in a position precentered to the axis of rotation of the crankshaft or of the pilot bearing between the second flywheel and the pressure plate of the clutch. It is also advantageous if openings are provided in the clutch disc or in the flange, which are congruent with the Verschraubungsbohrungen for attachment to the engine and if further the clutch disc is clamped between the second flywheel and pressure plate of the clutch, that the Verschraubungsbohrungen and the openings at least overlap each other, which may also be formed in alignment. In addition, openings may be provided in the plate spring of the coupling, expediently between two individual tongues for insertion of a screwing tool, these openings are also overlapping with the openings in the coupling disk and the holes in the second flywheel or in the support flange of the first flywheel. The openings in the plate spring can be aligned with the holes in the flange. However, the holes in the latter are usually provided asymmetrically to each other in order to mount the first flywheel relative to the crankshaft only in a very specific position can. The openings in the plate spring and those in the clutch disc may also be provided in accordance with the pitch of the openings in the support flange and in the crankshaft in uneven distribution. But it is also possible, if the irregularity of the distribution of the holes in the support flange of the first flywheel and in the crankshaft is only slightly to arrange the openings in the plate spring for the passage of a screwing tool symmetrically over the circumference, but they are larger in diameter than the diameter of the screwing tool in such a way that the one or more screwing tools can be placed properly on the screw or screws.

Independent of the distribution of these openings It may be advantageous that the openings in the diaphragm spring are smaller than the heads of the mounting screws. In some cases it may also be appropriate if the openings in the clutch disc are smaller than the heads of the mounting screws, so that this Fixing screws against falling out in the engine or the first flywheel turned away either through the plate spring or secured by the clutch disc. In the latter case can the distribution of the openings be made in the same way as in the clutch disc this is described in connection with the diaphragm spring.

The Position in which the mounting screws are captive in the Unit are held, is suitably such that on the one hand, As already mentioned, the heads are held in the interior of the unit - ie z. B. within the of the plate spring enclosed space - and on the other hand on the On the other hand, the threaded areas are not above the motor-side contour protrude from the first flywheel, which in connection with the already mentioned compliant means can be achieved, which screws in hold, clamp or lock in this position.

Advantageous It can still be, if the first flywheel also the Pilot bearing pre-assembled, wherein the pilot bearing in the space enclosed by the rolling bearing space can be provided. The pilot camp may be in the area of the first shoe worn axial approach are taken in an advantageous manner.

A Such completely pre-assembled unit can, as already mentioned, simple and inexpensively transport and assemble, while possibly required Maintenance work, in particular the replacement of the clutch disc with worn clutch linings, can be done in a known manner, by separating the clutch from the second flywheel can.

According to one further advantageous and inventive embodiment of a torque transmission device of the aforementioned type, the clutch cover a radially outer, at least have a substantially axially or cylindrically extending section, which serves to form the annular space. The axial clutch cover section can thereby at least partially filled with a viscous medium annulus Limit radially inward, so that this annulus practical Completely radially outside provided the clutch cover and the outer clutch cover portion can be.

to Application of provided between the two flywheel masses and effective in the circumferential direction of energy storage can advantageously radial arms on the outer circumference be provided of the axial lid portion. Such boom can in a simple manner by individual attached to the outer circumference of the lid Tabs are formed. The arms or tabs can as flat components, the z. B. are produced by punching formed be. In a particularly simple manner, the boom on the axial Cover section welded be. Furthermore, it may be advantageous if the boom relative to the axially offset back free end portion of the axial lid portion are, so that axially on both sides the boom a self-contained lid area is present. This will ensure that in the Range of fixings between the cantilevers and the axial Cover section a higher Stiffness is present and that a deformation of the axial Lid section as a result of the boom in the circumferential direction acting spring forces can be avoided or higher Transmit forces can be without one Deformation occurs.

Especially it may be advantageous if the torque transmission device so that is built up the outer axial Cover section at least over the entire axial extent of the energy storage extends.

According to an additional inventive embodiment of a torque transmission device of the type mentioned, in which the annular space through the outer regions of a fastened to the output shaft of an internal combustion engine disc-shaped component and by an attached to the radially outer regions of this disc-shaped member annular member, the a radially inwardly extending, the energy storage at least partially enclosing wall is limited, at least the annular member and the clutch cover from the same material, ie be made from the same metal strip or from the same board. In torque transmission devices comprising a friction clutch with a clutch disc having a hub provided for receiving on a transmission input shaft and a hub flange attached thereto, it may be particularly advantageous if at least two of the three components, namely annular member, clutch cover and hub flange of the same material or metal strips are made. It may be particularly advantageous if the components produced from the same material or the same board are first produced in one piece, for. B. by deep drawing and / or embossing and / or punching and then separated by a separating cut. It when the torque transmission device is designed such that the annular member, the clutch cover and the hub flange can be formed from the same sheet metal strip is particularly advantageous.

According to a further inventive embodiment of a torque transmission device of the type mentioned above, the clutch cover is connected to the flywheel carrying it via at least one welded joint. Particularly advantageous training opportunities such welds are in conjunction with the 6 to 9 described.

Around the life and the function of torque transmission devices with a dual mass flywheel, a chamber or an annular space has which or which at least partially with a viscous Medium filled is to increase, can it according to one further independent inventive feature be particularly advantageous if between the friction clutch bearing flywheel and the annular space or the torus-like chamber provided a thermal insulation is.

to increase the thermal stability of a torque transmission device according to the invention it may be particularly advantageous if between the second Flywheel and carried by this admission areas for the Power storage of the damping device a thermal insulation is provided.

In a particularly advantageous and simple way, a thermal Insulation between the second flywheel and the clutch cover provided become.

According to one Another inventive feature, it may in a torque transmission device with a coupling, which has a lid, a non-rotatable with this, However, axially limited displaceable connected thrust washer and at least one effective between lid and pressure washer energy storage owns the thrust washer in the direction of one with the lid rigid Connected NEN back pressure plate, wherein between thrust washer and counter-pressure disc a clutch disc is provided, especially be advantageous if the lid with axially extending portions the outer contour the counter-pressure disk engages and in axially the counter-disc umfreifenden sections of the cover radial material deformations are present, which in cruciform or star-shaped depressions of the outer contour engage the counter pressure plate. To form the cruciform Wells can on the outer circumference the second flywheel or the counter-pressure plate in the circumferential direction extending radial groove and / or grooves extending in the axial direction be introduced. It can be particularly advantageous if the circumferentially extending groove with the in the axial direction extending grooves, at least approximately at an angle of 90 °. The grooves or depressions extending in the axial direction can thereby in cross section, at least approximately, semicircular be so that they z. B. can be made by drilling.

The Forming the radial deformations of the material of the lid can be particularly Advantageously by radial impressing depressions in the lid material take place, wherein the embossing can be done in such a way that in essentially a flow process takes place in the lid material. The lid material is both in the circumferential groove as well as in the longitudinal direction extending grooves or depressions displaced, so that the positive connection between the Cover and the counter-pressure disc warranting warts formed cross-shaped are. The by the repressive stamp generated deformation on the lid can be an annular, z. B. cylindrical or dome-like shape.

Based on 1 to 13 let the invention be explained in more detail.

The show 1 to 3 in each case a section through a torque transmission device according to the invention,

4 a design possibility or production possibility for components of the device according to 3 .

5 a section through another Vari ante of a torque transmission device according to the invention,

the 6 to 9 various possibilities for connecting a clutch cover with the flywheel carrying it,

the 10 to 12 Another attachment between a clutch cover and a counter-pressure plate or flywheel, wherein the 11 a view in the direction of the arrow XI the 10 and the 12 a view in the direction of the arrow XII the 11 represent and

13 a particularly advantageous possibility of sealing the ring-like space.

In 1 is a split flywheel 1 shown, one, attachable to a crankshaft, not shown, of an internal combustion engine, first or primary flywheel 2 owns and a second or secondary flywheel 3 , On the second flywheel 3 is a friction clutch 4 with the interposition of a clutch disc 5 fastened, via which a likewise not signed gear can be connected and disconnected. The momentum 2 and 3 are about a storage 6 mounted to each other verdehbar, radially within the holes 7 for the implementation of fastening screws 8th for the assembly of the first flywheel 2 is arranged on the output shaft of the internal combustion engine. Between the two momentum masses 2 and 3 is the damping device 9 effective, the helical compression springs 10 owns that in an annular space 11 , which is a toroidal area 12 forms, are housed. The annular space 11 is at least partially filled with a viscous medium such as oil or fat.

The primary flywheel 2 is mainly due to a component 13 formed from sheet metal material. The component 13 has a substantially radially extending flange-like area 14 , the radially inwardly integrally formed, axial approach 15 carries, which of the holes or holes 7 is surrounded. The single row rolling bearing 6a the rolling bearing 6 is with his inner ring 16 radially outward on the end portion 15a of the axial approach 15 added. The outer ring 17 of the rolling bearing 6a carries the trained essentially as a flat, disk-shaped body second flywheel 3 , For this has the flywheel 3 a central recess in which the bearing 6a is included. The substantially radially extending region 14 goes radially outward in a half-shell-like or C-shaped area 18 over, the energy storage 10 at least partially surrounds and guides or supports at least over the outer periphery. The radially outer, shell-like area 18 of the sheet metal body 13 is opposite to the radially inner areas 14 offset axially in the direction of the internal combustion engine. The bowl-shaped area 18 engages with an outer, axially extending portion of the coil springs 10 at least partially and limits the annular space 11 or its torus-like region 12 radially outward. At its in the direction of the second flywheel 3 or the clutch 4 pointing end bears the shell-like area 18 a likewise shell-like body 19 , which can be formed from sheet metal and also to the formation or delimitation of the annular space 11 serves. The shell-like body 19 partially surrounds the scope of the energy storage 10 , In the illustrated embodiment, the shell-like region extend 18 and the shell-like body 19 each at least approximately over half of the axial extent of an energy storage device 10 , The body 19 is with the sheet metal body 13 welded (at 20 ) and has a radially inwardly extending portion 19a , The through the shell-like body 19 and the bowl-like area 18 formed toroidal area 12 is, viewed in the circumferential direction, divided into individual images in which the energy storage 10 are provided. The individual recordings are, viewed in the circumferential direction, separated from each other by loading areas for the energy storage 10 which pass through into the sheet metal part 13 and the bowl-like body 19 embossed pockets can be formed. The pictures for the springs 10 are through in the sheet metal parts 18 and 19 introduced indentations formed. The second flywheel 3 associated admission areas 21 for the energy storage 10 are from the clutch cover 22 carried.

The admission areas 21 are by radial arms 21 formed, which are integral with the clutch cover 22 and in the annulus 12 radially engage, between the ends of circumferentially adjacent force accumulators 10 , The loading areas or arms 21 are radially inward with an axially extending, cylindrical area 23 of the lid 22 connected. The axially extending lid area 23 envelops or surrounds with a section 23a the second flywheel 3 and is with this over in the section 23a introduced stampings 24 , which are in corresponding recesses of the flywheel 3 intervene, firmly connected. For positioning the second flywheel 3 opposite the clutch cover 22 during their connection, owns the lid 22 an axial shoulder 25 on which the flywheel 3 can support axially.

The on the outer contour of the flywheel 3 centered clutch cover 22 owns at its the loading areas 21 opposite end a substantially radially inward delay fenden, annular area 26 , on which an effective as two-armed lever disc spring 27 is pivotally supported in a conventional manner. With radially outward areas applied to the plate spring 27 a printing plate 28 , whereby the friction linings 29 the clutch disc 5 between the second flywheel 3 and the printing plate 28 be clamped axially.

As can be seen from the figure, is the annular space 11 or its torus-like region 12 predominantly radially outside the outermost contours of the second flywheel 3 arranged. As a result, as can be seen from the figures, that for the articulation of the first flywheel 2 serving on the output shaft of the internal combustion engine and the toroidal region 12 bearing component 13 , which is adjacent to the internal combustion engine, and the second flywheel 3 radially within the annular space 11 over a relatively large radial extent, forming a gap or air gap 30 , directly opposite, so be directly adjacent, creating a very compact in the axial direction of the design of flywheel 1 , Clutch 4 and clutch disc 5 existing aggregate is made possible. In the illustrated embodiment, the flywheel is 3 over practically its entire radial extension of the engine-side component 13 adjacent. This is made possible inter alia by the sealing of the annular space 11 through a seal 31 ensures that between the inner areas of the radial section 19a and an outer, on the outer circumference of the lid 22 molded sealing surface is effective. As a result of the structure according to the invention, therefore, no components extend radially between the two flywheel masses 2 and 3 ,

Depending on the application, the gap 30 have at least 50% of its radial extent an axial width between 0.5 and 4 mm. It is expedient if this gap has a gap width between 1 and 2 mm. Advantageously, this gap 30 for cooling the flywheel 1 serve, and indeed, by passing through this gap 30 a cooling air flow is passed. To generate such a cooling air circulation, has the second flywheel 3 radially within the friction surface 32 axial recesses 33 that, starting from the clutch 4 facing side of the flywheel 3 , in the direction of the radially extending area 14 the engine-side component 13 extend and into the gap 30 open, so that the air flow directly to the area 14 flowed by or on this area 14 is directed. Additionally or alternatively to the recesses 33 may be the radially extending area 14 of the sheet metal body 13 axial passages 34 have the gap 30 with the motor facing side of the component 13 connect. To improve cooling, the second flywheel can 3 further axial passages 35 have, which lie radially outward and on the friction surface 17 opposite side with the gap 21 communicate and on the clutch 4 facing side of the flywheel 3 radially outside the friction surface 17 open out. The passages 35 are radially outward through the axial section 23a of the lid 22 which is the flywheel 3 encompasses, limited. The axial passages or recesses 33 . 34 and 35 can, viewed in the circumferential direction, be elongated. The recesses 33 simultaneously serve to accommodate or carry out the fastening screws 8th ,

For sealing the partially filled with viscous medium, annular chamber 11 are a radially inner seal 36 and the radially outwardly disposed seal 31 intended. The seal 36 is formed by a membrane-like or plate spring-shaped component, which is located on the radially extending portion 14 the flywheel 2 supported, on a diameter range, which is radially outside the mean friction diameter of the friction surface 32 the flywheel 3 located. The seal is supported radially on the outside 36 on a shoulder 37 of the lid 22 through which it is simultaneously centered. The axially spring-loaded seal 36 is at the radial height of the ventilation channels 35 the flywheel 3 intended. In the illustrated embodiment according to 1 is the seal 31 formed by a rubber or plastic ring in a groove or an annular groove of the wall 19a is included. However, it could also be used here a plate spring or membrane-like seal. Due to the design and arrangement of the seals 31 . 36 ensures that the free space or air gap 30 that is directly between the two momentum masses 2 and 3 is provided, a relatively large radial extent, whereby the cooling of the friction surface 32 having inertia 3 can be significantly improved. Furthermore, due to the arrangement of the seal 31 , the radially outer ventilation channels 35 radially within this seal 31 axially guided past this and open the coupling side. The clutch cover 22 has in its axially extending region 23 recesses 38 that with the passages 35 cooperate to generate a cooling air flow. The partly in the radially outer region of the friction surface 32 provided, radially inner seal 36 seals the clearance or the air gap 30 opposite the radially outer annular space 11 from.

The shell-like body 19 carries a starter sprocket 39 that has a weld connection connected with him.

Together with the clutch unit, consisting of clutch 4 and clutch disc 5 , that forms in 1 illustrated two-mass flywheel 2 + 3 a structural unit A, which is pre-assembled as such, so shipped and stored and can be screwed onto the crankshaft of an internal combustion engine in a particularly simple and efficient manner. For the assembly of the unit A, the first coupling 4 and the second flywheel 3 , with interposition of the clutch disc 5 , connected with each other. Thereafter, the subunit consisting of coupling 4 , Flywheel 3 and clutch disc 5 with the component 13 axially merged, whereupon the shell-like body 19 on the outer edge 23 the clutch cover 22 is received, to rest against the outer regions of the component 13 brought and with this (at 20 ) can be welded. Before the axial merging of the two components 13 and 19 became the feathers 10 in the toroidal area 12 inserted. Furthermore, before the axial merging of the component 13 with the clutch 4 bearing second flywheel 3 the seal 36 as well as the camp 6a positioned or attached to one of the components to be axially brought together. The assembly A thus already has integrated the bearing 6 which is on the axial neck 15 is applied, in turn to the first flywheel 2 is provided. In the holes 7 of the flange area 14 are also still the mounting screws 8th already pre-assembled or contained, in the form of Allen screws 8th , Here are their screw heads 40 axially in such a position between the flange 41 the clutch disc 5 and the attachment area 14a the first flywheel 2 , and the threaded areas 40a are sized and, as described below, held so that they are not axially beyond the contour 42 the first flywheel, so the engine-facing contour 42 , stick out. The screws are held in this position and captive in the unit or the unit A, on the one hand by the overlapping areas of the flange 41 on the other hand by resilient means which hold the screws in such a position that the threaded portions 40a not from the openings 7 protrude. These resilient means are sized so that their holding force when tightening the screws 8th is overcome. Such a resilient means may be provided by a plastic liner which defines the threaded portion 40a a screw 8th in the axial region of a bore 7 surrounds, be formed. This intermediate layer is clamped between the screw thread and the bore 7 ,

The clutch disc 5 is in a pre-centered to the axis of rotation of the crankshaft position between pressure plate 28 and friction surface 32 the second flywheel 3 clamped and beyond in such a position that the openings provided in the clutch disc 43 are in such a position that during the assembly process of the unit A on the output shaft of the internal combustion engine, a screwing tool can be moved through. It can be seen that the openings 43 are smaller than the heads 40 the screws 8th , so that thereby a perfect and captive mounting of the screws 8th in the unit A is guaranteed.

Also in the plate spring 27 , in the area of their tongues 27a , are openings or cutouts 44 provided for the passage of the screwing tool. The cutouts 44 may be provided such that they widenings or extensions of between the tongues 27a form existing slots. The openings 44 in the plate spring 27 . 43 in the clutch disc 5 and 33 in the flywheel 3 cover each other while in the axial direction in such a way that even with a due to be positioned to be carried out assembly of the unit A on the crankshaft required asymmetrical arrangement of the holes 7 an assembly tool, such as an Allen key, properly through the openings 44 in the plate spring 27 and 43 in the clutch disc 5 , pass through and into the recesses of the heads 40 the screws 8th can intervene. The passages 44 for the screwing tool are also smaller than the heads 40 the screws 8th ,

One Such complete unit A facilitates the assembly of the flywheel considerably, because it eliminates various operations, such as the otherwise required centering for the clutch disc, the Operation for the insertion of the clutch disc, the attachment of the clutch, the Introduce the centering mandrel, centering the clutch disc itself, the insertion of the screws and the screwing of the clutch and the removal of the centering mandrel.

In the 2 represented unit 101 has a flywheel 102 , which is similarly connectable with an internal combustion engine, as in connection with 1 has been described, as well as with respect to this over a storage 106 rotatable flywheel 103 , On the flywheel 103 is a clutch 104 attached, being axially between the pressure plate 128 the clutch 104 and the second flywheel 103 the Reibeläge 129 a clutch disc 105 are axially clamped. This is the main component of the first flywheel 102 forming component 113 carries radially inside an axial approach 115 , being between this axial approach 115 and the second flywheel 103 the rolling bearing 106a in a similar way as in connection with 1 described, is arranged. The axial approach 115 is formed by a separate component, which at the radially inner portions of the formed by a sheet metal part 113 is attached. The axial approach 115 limits a cavity 150 in the axial end areas 151 the hub 152 the clutch disc 105 intervention. In the cavity 150 can continue to be a hub 152 hineinerstrecken receiving transmission input shaft. As schematically in 2 can be indicated in the cavity 150 a pilot camp 153 be provided for supporting the end pin of the transmission input shaft. In embodiments in which the pilot bearing is received and centered directly in the output shaft of the engine, the transmission input shaft may extend axially over the entire length of the cavity 150 first record. The attachment of the unit 101 takes place at the output shaft of the internal combustion engine, in a similar manner as in connection with 1 described, by means of screws 108 , where appropriate Ausnhemungen are provided in the individual components and the screws 108 are secured during transport against falling out accordingly.

The in the toroidal area 112 the annular chamber 111 recorded, effective in the circumferential direction Schraubenenfedern 110 are at a relative rotation between the two flywheels 102 . 103 through radial arms 121 , which are inclined in the axial direction to the internal combustion engine and with the clutch cover 122 are rotationally fixed, charged. The between the end of feathers 110 taken up arms 121 are radially inward through a closed, annular area 155 connected to each other, this area 155 via a weld with a substantially L-shaped ring 156 to a component 157 is summarized. The radially outwardly directed leg 156a of the L-shaped ring 156 is about screws 158 with the radially extending edge of the lid 159 connected.

The lid 122 and that the areas of application 121 for the springs 110 bearing component 157 are with the second flywheel 103 via a membrane-like component 160 connected. The membram-like component 160 has an outer, radially extending edge 161 that is between the outer lid edge 159 and the radially extending portion 156a of the component 157 is axially clamped. The outer radial area 161 the membrane-like component 160 goes radially inward into an axially extending area 162 over, the second flywheel 103 wrapped and embossed 163 , which are in corresponding recesses of the outer circumferential surface of the second flywheel 103 intervene, with this second flywheel 103 is firmly connected. At its the radially outer area 161 opposite end has the membrane-like component 160 a radially inwardly extending, annular region 164 , the second flywheel on the clutch 104 radially facing away from the opposite side. Axially between the radial area 164 the membrane-like component 160 and the second flywheel 103 are radial ventilation ducts 165 provided by the second flywheel 103 introduced, radially extending grooves are formed. Radially inside and radially outside are the grooves 165 with also axially extending ventilation passages 166 . 167 in connection. The radially inner ventilation passages or ventilation recesses 166 open radially within the friction linings 129 in the second flywheel 103 one. The radially outer ventilation passages or recesses 167 open radially outside the friction linings 129 coupling side and extend in the radially outer region of the second flywheel 103 adjacent to the axial region 162 the membrane-like component 160 , Further cooling can be done by an air flow through the recesses also serving for screwing 133 the second flywheel 103 opens, through the between the radial region 114 of the component 113 and the radial area 164 the membrane-like component 160 existing radial air gap 130 circulated and through recesses 134 of the radial region 114 radially outside, near the seal 136 , internal combustion engine side exit. Radially outward is the gap 130 through the seal 136 limited.

The seal formed by a plate-spring-like component 136 is axial between the component 113 and the annular area 155 clamped and at the radial height of the outer circumference of the second flywheel 103 arranged.

The radially outer seal 131 is also formed by a membrane-like or plate spring-like component, which is located at the radially inner regions of the component 113 connected, shell-like component 119 supported and radially inward also at the annular area 155 is applied. Advantageously, the outer seal 131 also have a radial area between the annular area 155 and the end portions of the axial leg 157 of the L-shaped ring 156 is clamped before the annular area 155 with the L-shaped ring 156 is welded.

The coupling 104 and the charging areas 121 or the component carrying this 157 are over the membrane-like component 160 opposite the second flywheel 103 centered.

In the 3 represented unit 201 has a flywheel 202 , which is similarly connectable to an internal combustion engine, as in connection with 1 has been described, as well as with respect to this over a storage 206 rotatable flywheel 203 ,

That's the primary flywheel 202 essentially forming component 213 differs from the component 13 according to 1 mainly in that the radially outer shell-like area 218 who the energy store 210 radially outwardly at least partially surrounds and guides or supports, not with respect to the radially inner areas 214 axially offset in the direction of the internal combustion engine. The cupped area 218 is arranged so that it is practically at the same axial height as the secondary flywheel 203 located. The cupped area 218 limited together with the also shell-like body 219 a toroidal or annular space 211 , The cupped area 218 and the shell-like body 219 each extend at least approximately over half of the axial extent of the energy storage 210 , Radial outside are the components made of sheet metal 218 . 219 through a weld 220 connected with each other. The annular space 211 is viewed in the circumferential direction divided into individual images in which the energy storage 210 are provided. These recordings are viewed in the circumferential direction separated from each other by Beaufschlagungsbereiche for the energy storage 210 which through through the sheet metal parts 218 . 219 embossed pockets 218b . 219b are formed.

Radially inward is the toroidal or annular space 211 by an axially extending, preferably cylindrically shaped, region 223 the clutch cover 222 limited. The cylindrical lid area 223 envelops or surrounds the second flywheel 203 and is with this over radial pins or clamping sleeves 224 that are in recesses of the lid 222 and the second flywheel 203 are included, firmly connected. For this connection also welded joints or fittings could be used.

The on the outer contour of the flywheel 203 centered clutch cover 222 owns for the energy storage 210 Supporting or loading areas 221 passing through on the outer lateral surface 223a of the cylindrical cover area 223 fixed radial arms, like arms 221 are formed. The outriggers 221 are formed by individual elements that on the outer cover shell or the lateral surface 223a z. B. are fixed by welding. The outriggers 221 are opposite to the sheet metal part 213 adjacent free end of the cylindrical lid approach 223 set back axially. This results in a stiffer connection between the applied admission areas 221 and the lid areas 223 achieved, as on both sides of the loading areas 221 remain in the circumferential direction closed lid areas remain so that in the connection area between the Beaufschlagungsmittel 221 and the lid areas 223 a higher stiffness of the lid material against deformation is present. In the illustrated embodiment, the Beaufschlagungselemente 221 at least approximately at the same axial height as the friction linings 229 the clutch disc 205 intended. The charging elements 221 can be produced in an advantageous manner from a material which has better mechanical properties compared to the cover material, in particular a higher wear resistance.

For sealing the at least partially filled with viscous medium chamber 211 is a seal 236 provided, which is formed like a membrane. The annular seal 236 has an axial area 236a placed on the outer surface of the cylindrical end 223b the axial lid approach 223 is pressed. Furthermore, the annular seal has 236 a substantially radially extending disc-shaped area 236b , with its radially inner edge on the motor side sheet metal body 213 supported. The radial area 236b is elastically braced in the axial direction.

How out 3 can be seen, there is the toroidal or annular space 211 radially outside the axial lid areas 223 and in the axial direction at least approximately at the same axial height with the second flywheel 203 and the printing plate 228 the clutch 204 ,

To form a cooling air circuit are in a similar manner as in connection with 1 described a gap 230 , Recesses or cutouts 233 . 234 . 238 and passages or ventilation channels 235 intended. The cutouts 238 in the clutch cover 222 can be formed such that ventilation wings can be formed out of the lid material. By such ventilation measures on the one hand, an air circuit between the lid 222 facing surface of the printing plate 228 and the clutch cover 222 So, around the diaphragm spring 227 , and on the other hand, a cooling air circuit between the flange-like area 214 of the sheet metal body 213 and the engine-facing rear of the secondary flywheel 203 causes the radially outward axially between the secondary flywheel 203 and the printing plate 228 on the one hand and the lid 222 on the other hand, along the direction of the transmission. The cutouts 238 or the ventilation wings formed by these can be designed such that the air is sucked out of the inner region of the coupling. In 3 are the Air flows symbolically represented by dash-dotted arrows.

For sealing the annular chamber 211 is still a seal 231 provided between the axially frusto-conical extending, radially inner regions 219a the shell-like body 219 and the outer lateral surface 223a of the axial approach 223 the clutch cover 222 is arranged. The annular seal 231 is formed in cross-section C- or U- or V-like. The radially inner leg of the seal 231 is on the outer surface 223a of the axial approach 223 recorded, z. B. pressed or shrunk. The radially outer, in the direction of the shell body 213 directed legs of the seal 231 runs in the axial direction in a truncated cone and forms with the also frusto-conical extending radially inner surface of the area 219a a sealing point. It may be particularly advantageous if the outer leg of the seal 231 with the radially inner surface of the area 219a forms a gap seal, since then no friction can occur, which is the characteristic of the damper 209 , in particular around the zero point position, can negatively influence. For some applications, however, it may also be expedient if the radially outer leg of the seal 231 with its free end portions resilient on the inner surface of the area 219a is applied. The frustoconical design of the outer leg of the seal 231 and the area of the area interacting with it 219a has the advantage that, if ever grease between the seal and the area of the area 219a This fat then again due to the centrifugal force in the annulus 211 is transported back.

In the illustrated embodiment, the hub body of the clutch disc 205 from a an inner toothing for receiving on a transmission input shaft having hub 205a and a riveted to this hub flange 205b , the radially outside the friction linings 229 wearing.

A particularly simple, efficient and inexpensive production of the unit 201 can be achieved in that at least two of the following three components, namely shell-like body 219 , Clutch cover 222 and clutch disc flange 205b from the same material, that is, from the same sheet metal strip, by concentrically forming it out of the material so that the waste can be minimized. It may be particularly useful if at least two of the above-mentioned components 219 . 222 . 205b , Preferably all three, are first made in one piece, so initially only form a sheet metal part and then separated by a punching or separating section. In 4 is such a sheet metal part 270 shown which the clutch disc flange 205b , the clutch cover 222 and the bowl-like body 219 forms. The separation of the individual components takes place in the 271 marked separating cut areas. How out 4 it can be seen, the sheet metal part 270 already means, like cones 272 . 273 integrally formed, as related to 3 can be seen, for attachment of lining carrier segments 229a at the hub flange 205b or for fixing a Tellerfederabwälzauflage 227a on the lid 222 can serve.

In the 5 illustrated torque transmitting device 301 possesses, similar to that in connection with 3 described a clutch cover 322 , whose radially outer regions by an axially extending projection or a tubular wall 323 are formed. The axial approach 323 and the two the ring chamber 311 confining bowl-like body 313 . 319 are formed such that two spring groups 310 . 310a can be arranged axially side by side. For applying the springs 310 . 310a are similar to this in conjunction with 3 has been described, on the outer circumferential surface of the axial extension 323 radial arms 321 . 321a attached. For applying the springs 310 . 310a has the primary flywheel which can be connected to an internal combustion engine 302 on the one hand embossed pockets 318b . 319b and on the other hand supporting means 318c . 319c that is axial between the two boom groups 321 . 321a are provided. The support means 318c . 319c can be formed by individual elements attached to the primary flywheel 302 z. B. are fastened by means of a welded connection, in particular radially within the radially outer circumferential wall of the primary flywheel 302 , The support means may form radially inwardly pointing arm, which, viewed in the circumferential direction engage between two adjacent springs. It is advantageous if the support means 318c and 319c circumferentially offset with respect to each other by half the length of a spring 310 respectively. 310a , The feathers 310 are thus also in relation to the springs 310a arranged offset in the circumferential direction. How out 5 it can be seen that are the clutch cover 322 worn outrigger 321 . 321a viewed in the axial direction between two Beaufschlagungs- or support areas, namely 318b . 318c and 319b . 319c recorded so that a proper loading of the force spoke [Ar 310 . 310a is guaranteed. The support areas 318c . 319c can also be used as radially inwardly extending arm of an annular, self-contained body 320a be educated.

In modification of in 5 shown Embodiment, the two spring groups 310 and 310a between the primary side flywheel 302 and the clutch cover 322 be arranged so that they are connected in series.

The transmission-side secondary flywheel 303 is on the primary flywheel 302 via a rolling bearing 306 stored. The outer bearing ring 306a is in an axial bore 303a the flywheel 303 added. For axial securing of the flywheel 303 in the release direction of the clutch 304 owns the flywheel 303 an axially to the hole 303a subsequent radial area 303b that is axially on the outer bearing ring 306a is applied. For fixing the outer bearing ring 306a opposite the flywheel 303 can between this flywheel 303 and the outer bearing ring 306a a shrink connection are provided, or the bearing ring 306a can into the hole 303a be pressed. Another possibility of axial securing of the bearing ring 306a consists in the axial extent of the receiving bore 303a and in the bearing ring 306a each to provide a radial recess, such as grooves for receiving a retaining ring 303c ,

The inner bearing ring 306b at the same time serves for axial contact pressure or attachment of the primary flywheel 302 to a flange of an engine output shaft. This is the inner bearing ring 306b radially formed relatively wide and has axial recesses such as holes 307 that deals with axial bores 307a in the shell-like body or housing part 313 cover. The recesses 307 , and 307a can be made the same in cross section. Through these holes 307 . 307a axially extend the mounting screws 308 , The bearing ring 306b is opposite the bowl-like body 313 centered. This is what the shell-like body possesses 313 radially inside an axial shoulder or shoulder 315 , on the outer circumferential surface of the inner bearing ring 306 is received centered at least over portions of the axial extent of its radially inner circumferential surface. The inner bearing ring 306 Can be used for axial securing on the neck 315 be pressed on. The outer bearing ring 306a can the secondary flywheel 303 directly record, as shown, but it can also between the outer bearing ring 306a and the flywheel 303 a thermal insulation z. B. may be formed by a plastic ring may be provided.

In one embodiment of the subject invention according to the in the 6 and 7 details shown is the axial, the secondary flywheel 403 cross-cutting approach 423 the clutch cover 422 by means of a welded joint 424 with the secondary flywheel 403 firmly connected, using at least one element or use 474 from a good weldable material, such. Steel. The use 474 has a central radially inwardly convex portion 474a and on both sides of this arranged arms 474b . 474c , The middle radially inward-facing area 474a of the insert 474 serves to prevent rotation, whereas the arms provided on both sides 474b . 474c for axial securing of the insert 474 opposite the secondary flywheel 403 made of cast. For holding the middle area 474a of several inserts 474 owns the secondary flywheel 403 distributed over the circumference, axially outwardly open countersinks 475 , which are concave radially inwardly, for receiving the convex portions 474a of deposits 474 , The countersinks 475 communicate with one in the outer circumference of the flywheel 403 introduced groove, such. B. a puncture 476 into which the circumferentially directed arms 474b . 474c the deposit 474 are absorbed, reducing the deposits 474 opposite the secondary flywheel 403 secured axially. How out 6 it can be seen, are the welded joints 424 , viewed in the axial direction, between the free end portions of the axial clutch cover neck 423 and on the outer circumference of this approach, attached boom 421 for applying the between the two momentum masses 402 and 403 provided and effective in the circumferential direction Kraftspei cher.

To form the connection between the lid 422 and the second flywheel 403 First, the stakes 474 in the groove 476 or in the countersinks 475 inserted and then with the interposition of the clutch disc, the clutch with its axial lid area 423 over the flywheel 403 pushed so that the welded joints 424 can be generated.

In the 8th shown detail shows another way to make a welded joint 524 for axial securing of the clutch cover 522 opposite the secondary flywheel 503 , In this embodiment, in radial bores or depressions 575 pen-like or rivet-like inserts 574 made of a good weldable material. For backlash-free securing of the welding inserts 574 These may be after inserting into the recesses 575 be deformed, so that in the recesses 575 a hole is created. The assembly between the clutch cover 522 and the flywheel 503 is done in a similar way as in connection with the 6 and 7 described.

The admission areas 421 . 521 for which between the two flywheel elements or flywheels 402 . 403 respectively. 502 . 503 provided energy storage are circumferentially opposite the welds 424 . 524 offset, so that the loading areas 421 . 521 for the formation of welds 424 . 524 not disturbing.

To form the welds 424 . 524 Are suitable welding methods that allow a weld formation by the lid material, and starting from the outer surface of the axial lid lugs 423 . 523 , For this purpose, welding methods such as spot welding, capacitor discharge welding, laser beam welding can be used in an advantageous manner.

At the in 9 illustrated embodiment, the clutch cover 622 with the secondary flywheel 603 via a disk-shaped component 674 connected, the radially outward via a welded joint 624 on the inner circumferential surface of the axial clutch cover approach 623 is attached. The disk-like component 674 is in the illustrated embodiment in an annular countersink 675 on the back of the flywheel 603 is provided, recorded. In addition to the welding 624 are for axial securing of the flywheel 603 opposite the clutch cover 622 riveted joints 624a between the disc-like component 674 and the flywheel 603 intended. The lid 621 has to act on between the two flywheels 602 . 603 in the circumferential direction effective energy storage radial boom 621 which are similar in design and effectiveness to those associated with 1 described Energiespeicherbeaufschlagungsbereiche 21 ,

According to a further and inherently inventive feature, it may be particularly advantageous for some applications if thermal insulation is provided between the flywheel carrying the clutch and the annular space filled at least in part with a viscous medium. Such thermal insulation can, as in the lower half of 3 is shown by an intermediate layer 264 be formed between the outer circumference of the flywheel 203 and this flywheel axially overlapping areas 223 of the lid 222 is arranged. The liner 264 can be formed by individual distributed over the circumference segments. The liner 264 However, it can also be closed in itself, ie it can be annular, in which case it will also be in the areas of the ventilation channels 235 extends over the circumference. In 3 is the liner 264 however, formed only by individual sections, so that the cross section of the ventilation channels 235 not reduced. Due to the thermally insulating intermediate layer 264 ensures that during a switching operation of the clutch 204 in the area of the friction surface of the flywheel 203 thermal energy does not flow unhindered over the lid 222 and the areas of responsibility borne by it 221 to the one in the chamber 211 contained viscous medium as well as the energy storage 210 is forwarded. This will cause a thermal overload in the chamber 211 recorded components or the viscous medium avoided.

In 2 could such thermal insulation, for. B. between the areas 156a and the areas 161 the membrane-like component 160 be provided.

To form a thermal insulation 264 are suitable in a particularly advantageous manner high temperature resistant plastics such. As polyamide or PEEK (polyether ether ketone).

The 10 to 12 show a further possibility of attachment between a counter-pressure plate and secondary flywheel 703 , and a clutch cover 722 , The clutch cover 722 has at least one axially extending region 723 , which may be cylindrical and sections 723a owns which the outer contour of the counter-disc 703 axially overlap and enclose in the circumferential direction or embrace. The axial lock between the clutch cover 722 and the back pressure plate 703 takes place via radially into the axial sections 723a introduced stampings 724 which in the illustrated embodiment warts 724 form, which in corresponding wells 774 on the outer circumference of the counter-pressure plate 703 intervention. The wells 774 are in the field of embossing 724 formed like a cross. This is in the outer periphery of the counter-pressure plate 703 a circumferential groove 775 , which is rectangular in cross-section, introduced and extending in the axial direction depressions 776 which may be at least approximately semicircular in cross-section and with the groove extending in the circumferential direction 775 at an angle of 90 °. The wells 776 or groove 775 can, viewed in the radial direction, at least approximately the same depth, it may be useful if the wells 776 opposite the bottom of the groove 775 are slightly set back. The formation of the cross-like depression sections 774 has the advantage that during the formation of the embossments or warts 724 the lid material in the wells 774 can flow without blasting or breaking out of the casting of the counter-pressure plate 703 due to increased congestion or displacement forces can occur. In the formation of the markings or warts 724 For example, the lidding material can be used both in the axial direction and in order direction are urged into the cross-like recesses, and it is particularly useful if the deformation is such that a flow of the lid material occurs. To form the stampings 724 can easily a cylindrical punch 777 be used.

The connection between the lid 723 and the counter-pressure disk or the secondary flywheel 703 can be done by first the back pressure washer 703 in the lid 723 pushed so far or is pushed in until the between the lid 723 and the pressure plate or the pressure plate 28 (please refer 1 ) effective energy storage 27 is biased to a defined, the proper function over the entire lifetime ensuring force, and then the embossments 724 be formed to a rigid connec tion between the lid 723 and the back pressure plate 703 to ensure. It is thus in such a mounting method in contrast to the embodiment according to 1 no axial boundary shoulder 25 between the lid 723 and the back pressure plate 703 required. Such a mounting method is particularly advantageous because a plurality of tolerances, which is the biasing force of the diaphragm spring 27 according to 1 influence, can be turned off. As a result, a better function of the friction clutch can be ensured.

In the 13 illustrated seal 831 to seal the energy storage receiving annular chamber consists of a support ring 831a and a ring-shaped plate-spring-like component 831b , The seal 831 is in turn between the radially inner regions 819a the wall connected to the first flywheel 819 and the outer lateral surface 823a an axial region 823 the clutch cover 822 arranged. The annular support ring 831a is formed in cross-section substantially L-shaped and has a radially inner sleeve-shaped portion 827 standing on the outer surface 823a is included. The substantially radially extending annular region 829 of the support ring 831a is slightly frustoconical, and axially in the direction of the wall 819 path. The truncated cone-shaped annular area 829 facing surface of the inner region 819a the wall 819 is also formed truncated TIG, at least approximately at the same angle as the annular region 829 of the support ring 831a , The plate spring-like component 831b is resiliently braced, with radially inner regions of the support ring 831a supported and with radially outer areas on the wall areas 819a , The support ring 831a can on the outer surface 823a be pressed on, for which purpose the lateral surface 823a may be mechanically processed, for. B. turned or ground. Another possibility is to at least the areas of the lid, which the support ring 831a to calibrate in a stamping or pressing tool.

When mounting the with a gasket 831 according to 13 equipped torque transmission device, before that the wall 819 is sealingly connected to the primary flywheel - z. B. by means of a welded connection 20 according to 1 - the support ring 831a as well as the plate spring-like component 831b on the axial area 823 of the lid 822 deferred, in an axial position, which is preferred to the final position. After that, the wall becomes 819 over the axial area 823 pushed and axially acted upon by a defined force in the direction of the primary flywheel, so that the wall 819 , similar to the wall 19 according to 1 , for support on the primary flywheel 2 or the disk-shaped component 18 comes and the welded joint 20 can be formed. By relocating the wall 819 in the direction of the primary flywheel mass is the plate-spring-like component 831b first between the frusto-conical areas or surfaces of the support ring 831a and the inner area 819a the wall 819 clamped flat, so that upon continuation of the axial displacement of the wall 819 the support ring 831a on the lateral surface 823a axially displaced or pressed, and that until the wall 819a comes to the primary flywheel to the plant. The area where the aforementioned force on the wall 819 acts and the size of this force are chosen so that when the wall 819 on the primary flywheel this wall has a certain elastic deformation, so that in case of elimination of this force after welding the wall 819 can spring back by a certain amount, which also clamped between the aforementioned frusto-conical surfaces plate spring 831b in turn can relax and the in 13 can take position shown. As a result, a defined bias and a perfect function for the plate spring-like component 831b guaranteed.

The Invention is not limited to the illustrated and described embodiments limited, but includes in particular also variants, which are characterized by a combination of individual, described in connection with the various embodiments, Characteristics or elements can be formed.

Furthermore, bearings can also be used in the present invention between the two relatively rotatable flywheel masses, which on a larger diameter are arranged as the screw diameter for the fastening screws for articulation of the first flywheel to the output shaft of an internal combustion engine.

Claims (51)

Torque transmission device with a first ( 2 . 202 ), attachable to an output shaft of an internal combustion engine and a second ( 3 . 203 ), connectable to the input shaft of a transmission, a friction surface ( 32 ) for a clutch disc ( 5 . 205 ) containing flywheel masses via a bearing ( 6 . 206 ) rotatably mounted to each other and via a damping device ( 9 . 209 ) are drivingly coupled, wherein the damping device ( 10 . 210 ) Has springs, which in one through components ( 13 . 19 ; 213 . 219 ) of the first flywheel radially outwardly limited annular space ( 11 . 211 ) are received and elastically deformable in a relative rotation of the flywheel masses, wherein the first flywheel ( 2 . 202 ) a sheet metal part ( 13 . 213 ), which has a radially extending flange-like region (FIG. 14 . 214 ) for attachment to the output shaft of the internal combustion engine, the radially outward in the direction of the second flywheel ( 203 ) axially extending regions ( 218 ), which border the ring-like space ( 211 ) radially outwardly serve and in which also a radially inwardly extending wall ( 219 ), characterized in that the annular space ( 11 . 211 ) predominantly radially outside the outer contours of the second momentum mass ( 3 . 203 ) is arranged so that the sheet metal part ( 13 . 213 ) and the second flywheel ( 3 . 203 ) radially within the annular space ( 11 . 211 ) over a relatively large radial extent to form a gap-shaped intermediate space ( 30 . 230 ) are directly opposite. Torque transmission device with a first ( 2 . 202 ) attachable to an output shaft of an internal combustion engine and a second ( 3 . 203 ), connectable to the input shaft of a transmission, a friction surface for a clutch disc ( 5 . 205 ) containing flywheel masses via a bearing ( 6 . 206 ) rotatably mounted to each other and via a damping device ( 9 . 209 ) are drivingly coupled, wherein the damping device springs ( 10 . 210 ), which in one by components ( 13 . 19 ; 213 . 219 ) of the first flywheel radially outwardly limited annular space ( 11 . 211 ) are received and elastically deformable in a relative rotation of the flywheel masses, wherein the first flywheel ( 2 . 202 ) a sheet metal part ( 13 . 213 ), which has a radially extending flange-like region (FIG. 14 . 214 ) for attachment to the output shaft of the internal combustion engine, the radially outward in the direction of the second flywheel ( 203 ) axially extending regions ( 218 ), which border the ring-like space ( 211 ) radially outwardly serve and in which also a radially inwardly extending wall ( 219 ), characterized in that the first flywheel ( 202 ) - viewed in the axial direction - forms a hollow body, the second flywheel ( 203 ) receives at least substantially axially, wherein radially outer contours of the second flywheel ( 203 ) serve to close the ring-like space, so that the sheet metal part ( 13 . 213 ) and the second flywheel ( 3 . 203 ) radially within the annular space ( 11 . 211 ) over a relatively large radial extent to form a gap-shaped intermediate space ( 30 . 230 ) are directly opposite. Torque transmission device according to claim 2, characterized in that the annular space ( 11 . 211 ) is at least substantially sealed, the annular space extending radially inwardly to a maximum of half of the radial Reibflächenausdehnung ( 32 ). Torque transmission device according to claim 2 or 3, characterized in that the second flywheel ( 203 ) at least over half the radial extent of the friction surface ( 32 ) the flange-like area ( 214 ) of the sheet metal part ( 213 ) of the first flywheel ( 202 ) is adjacent at a small distance. Torque transmission device according to one of claims 2 to 4, characterized in that the radially inwardly extending wall ( 219 ) has an inner diameter that is greater than the outer diameter of the friction surface ( 32 ) of the second flywheel ( 203 ). Torque transmission device according to one of claims 2 to 5, characterized in that the radially inwardly extending wall ( 19 ) axially extending portions of the second flywheel ( 3 ) surrounds. Torque transmission device according to one of claims 2 to 6, characterized in that the radially inwardly extending wall ( 219 ) with an annular seal ( 231 . 831 ) cooperates. Torque transmission device according to one of claims 1 and 3 to 7, characterized in that the first flywheel ( 202 ) - viewed in the axial direction - is designed as a hollow body, the second flywheel ( 203 ) receives at least substantially axially. Torque transmission device after egg nem of claims 1 and 3 to 8, characterized in that radially outer Kontoren the second flywheel to form the annular space ( 211 ) serve. Torque transfer device according to a claims 1 and 3 to 9, characterized in that radially outer contours the second flywheel to close the ring-like space serve. Torque transmission device according to one of claims 1 to 10, characterized in that the outer friction diameter, on the second flywheel ( 203 ) provided friction surface ( 32 ) is smaller than the diameter on which the radially innermost regions of the provided in the annular space springs ( 210 ) are located. Torque transmission device according to one of claims 1 to 11, characterized in that the radially inwardly extending wall ( 119 ) axially extending portions of a with the clutch cover ( 122 ) connected component ( 157 ) surrounds. Torque transmission device according to one of claims 1 to 11, characterized in that the radially inwardly extending wall ( 119 ) - radially inwardly - only over half the diameter of the radial extent of the in the annular space ( 111 ) recorded springs ( 110 ). Torque transmission device according to one of claims 1 to 13, characterized in that the annular space ( 111 . 211 ) is at least partially filled with a viscous medium and at least substantially sealed to the atmosphere. Torque transmission device according to claim 14, characterized in that the seal ( 31 . 231 . 831 ) is supported by one of the annular space forming components. Torque transmission device according to one of claims 1 to 15, characterized in that the bearing ( 6 . 106 ) radially inside and at least approximately at the axial height of a friction surface ( 32 ) of the second flywheel ( 3 . 103 ) is for a clutch disc. Torque transmission device according to one of claims 1 to 16, characterized in that the intermediate space ( 30 . 230 ) is used to carry out a cooling air flow. Torque transmission device according to one of claims 1 to 17, characterized in that in the radial flange-like region ( 14 . 214 ) of the first flywheel ( 2 . 202 ), preferably in the region of the opposite sections of the two flywheel masses, axial openings ( 34 . 234 ) are provided. Torque transmission device according to one of claims 1 to 18, characterized in that the second flywheel ( 3 . 203 ) radially within the friction surface ( 32 ) axial passages ( 33 ), which in the space ( 30 . 230 ). Torque transmission device according to one of claims 1 to 19, characterized in that the second flywheel ( 3 . 203 ) further passages ( 35 . 235 ) spaced from the space ( 30 . 230 ) and radially outside the friction surface ( 32 ). Torque transmission device according to one of claims 1 to 20, characterized in that in the existing between the two flywheel space ( 30 . 230 ) a seal ( 36 . 236 ) is provided. Torque transmission device according to claim 21, characterized in that the seal ( 36 . 136 ) between the first flywheel ( 2 ) and a clutch cover ( 22 ) or between the first flywheel ( 102 ) and one with the lid ( 122 ), application areas forming, component is effective. Torque transmission device according to one of claims 1 to 22, characterized in that the flywheel masses ( 202 . 203 ) at least substantially from the annular space ( 211 ) from radially inward, forming a gap ( 230 ), opposite each other over substantial radial areas. Torque transmission device according to one of claims 1 to 23, characterized in that the screwing diameter for fixing the first flywheel ( 302 ) on the internal combustion engine is located radially inside the bearing ( 5 ). Torque transmission device according to one of claims 1 to 24, characterized in that the screwing diameter for fastening the first flywheel to the internal combustion engine radially outside the storage ( 6 . 106 . 206 ) is located. Torque transmission device according to claim 25, characterized in that the second flywheel ( 3 . 103 ) has axial openings, for performing a screw connection Tool for fastening the torque transmission device ( 1 . 101 ) on the output shaft of an internal combustion engine. Torque transmission device according to one of claims 1 to 23, characterized in that the one cavity ( 150 ) for carrying out an element, such as a transmission shaft enclosing bearing ( 6 . 106 ) is provided on an at least substantially smaller diameter than the screw openings ( 7 ) for the side facing away from the engine of the one flywheel ( 2 . 102 ) screwed screws ( 8th . 108 ) for fixing the first flywheel ( 2 . 102 ) on the output shaft of the internal combustion engine, and that in the other flywheel ( 3 . 103 ) at least approximately aligned with the Verschraubungsbohrungen passage openings ( 33 . 133 ) are provided. Torque transmission device according to one of claims 1 to 27, characterized in that the bearing ( 6 . 106 ) an axial projection provided on one of the flywheel masses ( 15 . 115 ) encloses. Torque transmission device according to one of claims 1 to 28, characterized in that the axial projection ( 15 . 115 ) containing the viscous medium annular space ( 11 . 111 . 211 ) wearing. Torque transmission device according to one of claims 1 to 29, characterized in that for storage a bearing is used, the inner ring ( 16 ) is seated on an axial projection ( 15 ) (Extension) of one of the momentum masses ( 2 . 3 ) and its outer ring ( 17 ) the other flywheel ( 3 . 2 ), and that the largest diameter of the outer ring ( 17 ) is smaller than the diameter on which the screw holes ( 7 ) are arranged. Torque transmission device according to one of claims 28 to 30, characterized in that the axial projection ( 15 ) is integral with one of the flywheels ( 2 ). Torque transmission device according to one of claims 28 to 31, characterized in that the connectable to the output shaft of the internal combustion engine flywheel ( 2 ) the axial approach ( 15 ) wearing. Torque transmission device according to one of claims 27 to 32, characterized in that the hub ( 152 ) of the clutch disc ( 5 . 105 ) of the friction clutch axially into the (hollow) extension ( 15 . 115 immersed). Torque transmission device according to one of claims 27 to 33, characterized in that the passage openings in the second flywheel are smaller in diameter than the heads of the fastening screws ( 3 ). Torque transmission device according to one of claims 2 to 34, characterized in that one of the bearing rings of the bearing is integrally formed with an axial projection ( 15 . 115 ) one of the momentum masses. Torque transfer device according to claim 35, characterized in that the radially outer bearing ring one piece is associated with an approach associated with the first flywheel. Torque transmission device according to at least one of the preceding claims, characterized in that the split flywheel together with the clutch unit consisting of clutch ( 204 ) and clutch disc ( 205 ), an attachable to the crankshaft of the internal combustion engine assembly ( 201 ). Torque transmission device according to claim 37, characterized in that the structural unit also has a rolling bearing bearing the two centrifugal masses ( 6 . 106 ) includes. Torque transmission device according to one of claims 27 to 38, characterized in that the fastening screws ( 108 . 308 ) in the screw holes ( 307 . 307a ) are held captive. Torque transmission device according to claim 39, characterized in that the screws ( 8th ) are held by resilient means. Torque transmission device according to one of claims 37 to 40, characterized in that the clutch disc ( 5 ) in a pre-centered to the axis of rotation (A) of the crankshaft position between the second flywheel ( 3 ) and pressure plate ( 28 ) of the coupling ( 4 ) is clamped. Torque transmission device according to one of claims 37 to 41, characterized in that in the clutch disc ( 4 ) Openings ( 43 ) are present, which are congruent with the screw holes ( 7 ) for attachment to the engine, and that the clutch disc ( 5 ) between second flywheel mass ( 3 ) and pressure plate ( 28 ) of the coupling ( 4 ) is clamped that the screw holes ( 7 ) and the openings ( 43 ) cover each other. Torque transmission device according to one of claims 37 to 42, characterized in that in the plate spring ( 27 ) of the coupling ( 4 ) in the region of the tongues ( 27a ) Openings ( 44 ) are provided for introducing a screwing tool, and that these openings are overlapping with the openings ( 43 ) in the clutch disc ( 5 ) and the passage openings ( 33 ) in the second flywheel ( 3 ). Torque transmission device according to claim 43, characterized in that the openings ( 43 . 44 ) in the plate spring ( 27 ) and in the clutch disc ( 5 ) are aligned with the passage openings ( 33 ). Torque transmission device according to one of claims 43 or 44, characterized in that the openings ( 44 ) in the plate spring ( 27 ) are formed for the passage of a screwing tool and are smaller than the heads of the fastening screws. Torque transmission device according to one of claims 42 to 45, characterized in that the openings ( 43 ) in the clutch disc ( 5 ) are formed for the passage of a screwing tool and are smaller than the heads of the fastening screws. Torque transmission device according to one of claims 27 to 46, characterized in that the length of the fastening screws ( 8th ) and dimension them in the unit ( 1 ) are held that the heads ( 40 ) in the interior of the clutch ( 4 ) are enclosed space and the threaded areas ( 40a ) axially within the motor-side contour ( 42 ) of the first flywheel ( 2 ) are located. Torque transmission device according to one of claims 2 to 47, characterized in that the first flywheel ( 102 ) also the pilot camp ( 153 ) wearing. Torque transmission device according to one of claims 2 to 48, characterized in that between the friction clutch ( 204 ) bearing flywheel ( 203 ) and the annular space ( 211 ) A thermal insulation is provided. Torque transmission device according to one of claims 2 to 49, characterized in that between the second flywheel ( 203 ) and the supported by this support areas ( 221 ) for the springs ( 210 ) of the damping device ( 211 ) a thermal insulation ( 264 ) is provided. Torque transmission device according to one of claims 2 to 50, characterized in that the radially extending flange-like region ( 14 . 114 ) of the first flywheel ( 102 ) radially inward through a separate component ( 115 ) formed axial approach ( 115 ) contributes to the storage of the two masses of each other.