DE4143629C2 - 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 in known for example from DE 84 08 677 U1 and DE 37 21 705 A1 has been. This has a first, attachable with a motor, and one second, a flywheel that can be engaged and disengaged from a transmission Rolling bearings are rotatably mounted relative to each other and between them a damping device is provided with effective in the circumferential direction Power Save.

Torque transmission devices of this type with a divided or Dual mass flywheels have generally proven themselves in vehicle use, however, in the case of smaller vehicles, such devices, despite their advantages le, due to the relatively high price, is not yet widely available could enforce sis. Furthermore, such torque was transferred until now, especially in vehicles in which the axial Installation space is not as tight as in those with a transverse arrangement the drive unit motor and gearbox is frequently used namely mainly in vehicles with a longitudinal arrangement of engine and transmission.  For vehicles with very limited installation space for the drive unit, especially for those with a transverse arrangement of engine and transmission such dual mass flywheels just because of the limited space Do not enforce relationships in the way that is technically appropriate to them.

The object of the present invention was to provide a torque to create a support device that has an inexpensive structure, still has extremely small axial dimensions and therefore also for the Use with transversely installed drive units (motor and gearbox) is suitable.

In addition, proper storage of the flywheels should be relative to each other and an optimal function as well as the achievement of optimal damping rates are guaranteed.

Furthermore, this is intended to mount the device on a driving Wave in a simple and inexpensive way.

This is achieved according to the invention in that screws for fastening the first flywheel mass on a driving shaft before said attachment in the facility be captively attached and the bearing centering the centrifugal masses at least in the we is considerably provided on a smaller diameter than the screw Exercise bores of the first flywheel and screws  that through holes are provided in the other flywheel, via which the screws at least to fix the unit to the shaft are draggable. The bearing can be formed by a roller bearing, which has a cavity for the passage of an element such as a transmission wave, envelops.

The side of the flywheel facing away from the engine pullable or screwable screws for fastening the are the first flywheel mass on the output shaft of an internal combustion engine integrated in the torque transmission device according to the invention. In the the other flywheel provided through holes are in front preferably at least approximately aligned with the screw holes arranged.

The through holes in the other flywheel can be advantageous be designed such that the screws axially can be inserted, that is, have a cross section that the axial Hin enables a screw head. With such a construction the screws can be installed last in the device.

The construction of a torque transmission device according to the invention allows the use of a relatively small and inexpensive Wälzla gers. The fact that radially within the rolling bearing or radially within the area of the torque device receiving the rolling bearing  a cavity is provided, the hub of a clutch disc and / or the transmission input shaft receiving the clutch disc Immerse at least partially axially in the cavity so that the axial space required for that from torque transmission device, clutch disc and clutch formed torque transmission unit in the axial direction has a compact construction. The radially inside the rolling bearing seen cavity also allows the transmission input shaft in be Known way via a pilot bearing in the output shaft of the internal combustion engine to store, whereby the use of the torque transmission according to the invention supply facility can be significantly facilitated.

The means axially securing the screws in the unit can be advantageous Be designed in such a way that the holding force by tightening the screws this means is overcome. It can be useful if the security clamp the screws in a certain axial position.

It can be advantageous if both the first and the second Flywheel an axial approach is provided and between these the Inertial centering is provided. The axial approach of the second flywheel can axially into the hollow axial approach protrude into the first flywheel.  

For the structure and function of the torque transmission it can be particularly advantageous if the Bearing one on one of the flywheels encloses axial approach. It can be advantageous if this axial approach is in one piece with the corresponding one Flywheel. For some applications, however, it can also be useful if the one surrounded by the rolling bearing Approach by a corresponding to the radially inner areas appropriate flywheel attached tube or sleeve-shaped Component is formed. This sleeve-shaped component can the, radially inner areas delimiting a recess be attached to the flywheel. Can advantageously which can be connected to the output shaft of the internal combustion engine Flywheel carry the axial approach. However, it can also be useful for some applications if the with a flywheel connectable to the gearbox the axial approach carries or if both flywheels each have at least one have axial approach, these approaches are axial can overlap and radially between these the rolling bearing can be arranged.

It can be particularly advantageous if one is axial Inertial mass also has a viscous medium containing, annular space that carries the in circumference direction effective energy storage.

To position the two masses relative to each other which can be a roller bearing in a particularly advantageous manner  are used, the inner ring of which rests on the axial Approach or extension of one of the flywheels and whose outer ring carries the other flywheel, the largest diameter of the outer ring is smaller than that Diameter on which the screw holes are arranged are. In very tight spaces, it can also be from Be advantageous if at least one of the rolling tracks for the Rolling body is integrally formed with one of the momentum masses, it may be particularly useful if one such rolling track on the axial approach of the corresponding Inertia is molded on, so that this approach at the same time serves as a bearing ring. For some use cases it can be used for the function will be beneficial if the radially outer bearing ring is integrally formed with one with the first Flywheel connected approach. However, it can be advantageous also be if the radially inner bearing ring is in one piece with the approach carried by the first flywheel and the outer bearing ring carries the second flywheel, this outer bearing ring also in one piece with the second Inertia can be formed.

Another inventive measure, one particularly easy handling and assembly and inexpensive manufacture enables, is that the split flywheel together with the clutch unit, consisting of clutch and clutch disc, one on the crankshaft of the Brenn Engine attachable and pre-assembled unit forms, which also expediently the two  Inertial masses containing rolling bearings. It may be useful if the unit continues to be on the first flywheel provided for the flange Has rolling bearings in which axial bores are provided, in which the fastening screws for fastening the Unit already included on the crankshaft, i.e. before can be animal. It can also be useful if these mounting screws in the unit are captive are kept, this loss protection by compliant Means can be formed, the holding force then at Assembly, e.g. B. overcome by tightening the screws becomes.

According to another feature, it is pre-assembled The clutch disc is already in one unit for rotation pre-centered axis of the crankshaft or the pilot bearing Position between the second flywheel and the pressure plate the clutch clamped. It is also advantageous if in the clutch disc or in the flange of the same Openings are provided that are congruent with the Screw holes for attachment to the engine and when continue the clutch disc between the second The flywheel and clutch pressure plate are clamped, that the screw holes and the openings each other at least cover, whereby these are also in alignment could be. In addition, the Coupling, suitably between two individual tongues, Openings are provided for inserting a screwing tool,  these openings also being overlapping with the openings in the clutch disc and the holes in the second flywheel or in the supporting flange of the first Flywheel. The openings in the disc spring be aligned with the holes in the flange of the first Flywheel. However, the holes in the latter are in the Usually provided asymmetrically to each other to the first Flywheel mass in only one in relation to the crankshaft to be able to mount a very specific position. The openings in the disc spring and those in the clutch disc can also according to the division of the openings in the Supporting flange and in the output shaft of the internal combustion engine, such as B. the crankshaft, in an uneven distribution be provided. But it is also possible if the irregularity the circular distribution of the holes in the supporting flange the first flywheel mass or in the crankshaft only slightly gig, the openings in the disc spring for the passage a screwing tool symmetrical over the circumference to arrange, but they are larger in diameter than the diameter of the area to be passed through it che of the screwing tool, in such a way that the or Screwing tools properly on the screw or screws can be put on.

Regardless of the distribution of these openings, there may be be parous if the openings in the disc spring and / or the openings in the clutch disc are smaller than that Heads of the mounting screws so that these mounting screws  against falling out in the engine or first flywheel away from either direction Belleville washer or secured by the clutch disc. In the latter case, the distribution of the openings in the Clutch disc be made in the same way as this is described in connection with the plate spring.

The position in which the mounting screws are captive are held in the unit is expediently one such that on the one hand, as already mentioned, the heads in the Interior of the unit are held - z. B. within of the space enclosed by the disc spring - and others on the other hand, the thread areas do not have the motor-side contour of the first flywheel protrude, what in connection with the compliant already mentioned Means can be achieved using the screws in this Hold, pinch, or lock in position.

It can also be advantageous if the first swing mass also carries the pilot bearing pre-assembled, the Pilot bearing in the room covered by the rolling bearing can be provided. The pilot camp can be in the the first Schuwngng carried axial approach advantageous be taken up in a way that takes the approach that bearing two flywheels bearing radially outside.

Such a completely pre-assembled unit can be as already mentioned, easy and inexpensive to transport and  assemble during any necessary maintenance work, such as in particular when replacing the clutch disc worn clutch linings, done in a known manner can by removing the clutch from the second flywheel can be separated.

The invention is explained in more detail with reference to FIGS. 1 to 5.

Here, FIG. 1 shows a section through a torque transmitting device, and

Figs. 2 to 5 respectively show a section through a further embodiment of a Torque transmission device according to the invention ment.

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 fastened with the interposition of a clutch disc 5 , via which a gear, if not shown, can be engaged and disengaged. The flywheels 2 and 3 are mounted to each other via a bearing 6 , which is arranged radially within the holes 7 for carrying out fastening screws 8 for mounting the first flywheel 2 on the output shaft of the internal combustion engine. Between the two centrifugal masses 2 and 3 , the damping device 9 is effective, which has helical compression springs 10 which are placed in a ring-shaped space 11 , which forms a toroidal region 12 . The annular space 11 is at least partially filled with a viscous medium, such as oil or fat.

The primary flywheel mass 2 is predominantly formed by a component 13 which was produced from sheet metal material. The component 13 serves to fasten the first flywheel 2 to the output shaft of the internal combustion engine and supports the annular space 11 . The component 13 has an essentially radially extending, flange-like region 14 which , on the radially inside, carries an axially shaped projection 15 which is formed in one piece and which is surrounded by the bores or holes 7 . The single-row roller bearing 6 a of the roller bearing 6 is received with its inner ring 16 on an outer shoulder of the end portion 15 a of the axial extension 15 . The outer ring 17 of the roller bearing 6 a carries the second flywheel mass 3 , which is designed essentially as a flat, disc-shaped body. For this purpose, the flywheel 3 has a central recess in which the bearing 6 a is received.

The essentially radially extending region 14 merges radially on the outside into a half-shell or C-shaped region 18 which at least partially encompasses and guides or supports the energy accumulators 10 at least over their outer circumference. The radially outer, shell-like region 18 of the sheet metal body 13 is axially offset in the direction of the internal combustion engine in relation to the radially further inward regions 14 . The bowl-shaped area 18 engages with an outer, axially extending section, the screw springs 10 at least partially and delimits the annular space 11 or its toroidal area 12 radially outward. At its end pointing in the direction of the second flywheel 3 or the clutch 4 , the shell-like region 18 carries a shell 19 which is likewise shell-shaped and which can be formed from sheet metal and also serves to form or delimit the annular space 11 . The shell-like body 19 partially encompasses the circumference of the energy accumulator 10 . In the exemplary embodiment shown, the shell-like region 18 and the shell-like body 19 each extend at least approximately over half the axial extent of an energy accumulator 10 . The body 19 is welded to the sheet metal body 13 (at 20) and has a radially inwardly extending section or wall 19 a. The toroidal region 12 formed by the shell-like body 19 and the shell-like region 18 is, viewed in the circumferential direction, divided into individual receptacles in which the energy stores 10 are provided. The individual recordings are, viewed in the circumferential direction, separated from one another by application areas 18 a, 19 b for the energy accumulator 10 , which, as shown, can be formed by pockets 19 stamped into the sheet metal part 13 and the shell-like body. The receptacles for the springs 10 are formed by indentations introduced into the sheet metal parts 18 and 19 .

The provided on the second flywheel 3 Beaufschla supply areas 21 for the energy accumulator 10 are formed by at least one attached to the flywheel 3 acting medium 22 which serves as a torque transmission element between the energy stores 10 and the flywheel 3 . The loading means 22 can be formed by an annular component with a radial arm 21 or else by individual segments which are distributed over the circumference in accordance with the spring arrangement. Such a segment has a foot area for attachment to the second flywheel mass and a radial area for acting on the Kraftspei cher. When using an annular component 22 , this can have an inner, self-contained, annular region 22 a, which is connected to the second flywheel via blind rivet connections 23 and which supports radially outer cantilevers 21 , which extend radially between ends of energy stores 10 and in Idle state of the flywheel 1 , that is, if no torque is transmitted, are located axially directly between the application areas or pockets 18 a, 19 b.

The arrangement of the friction surface 25 of the flywheel 3 interacting with the friction linings 24 of the clutch disc 5 , in relation to the design of the loading means 22 , is such that more than 50% of the radial extension of the friction surface 25 is located radially within that of the or Acting means of limited, smallest diameter 26 are located. This allows the fasteners such. B. the rivets 23 , for fixing the loading means or the transmission element 22 to the flywheel 3 are relatively far out. This enables a configuration of the annular space 11 which ensures that this space 11 does not extend radially inwards over the average friction diameter 27 of the friction surface 25 . As a result, as can be seen from FIG. 1, the first flywheel 2 or the component 13 and the second flywheel 3 forming the main component of the flywheel 2 and the second flywheel 3 can be formed radially within the annular space 11 over a relatively large radial extent, with the formation of a space or Air gap 28 , lying directly opposite one another, that is to say directly adjacent, which enables a very compact design of the assembly consisting of flywheel 1 , clutch 4 and clutch disc 5 in the axial direction. Depending on the application, the space 28 can have an axial width between 0.5 and 4 mm. It is expedient if this intermediate space 28 has a gap width between 1 and 2 mm over at least 50% of its radial extent. Advantageously, this space 28 can be used to cool the flywheel 1 , specifically by passing a cooling air flow through this space 28 . To generate such a cooling air circulation, the second flywheel 3 has radial openings 29 radially inside the friction surface 25 , which, starting from the side of the flywheel 3 facing the clutch 4 , extend in the direction of the radially extending region 14 of the motor-side sheet metal body 13 and into the Open space 28 so that the air flow flows directly past area 14 or is directed towards this area 14 . In addition or as an alternative to the openings 29 , the radially extending region 14 of the sheet metal body 13 can have axial passages 30 which connect the intermediate space 28 to the side of the sheet metal body 13 facing the motor. In the circumferential direction between the fastening points 23 for the transmission element 22 , the flywheel 3 has in the direction of the friction surface 25 directed grooves or depressions 31 , which are used to generate a radial passage to the outside for the cooling air flow. To improve the cooling, the second flywheel 3 can have further axial passages 32 , which are located radially further outside and are on the side facing away from the friction surface 25 with the intermediate space 28 or the recesses, and on the side facing the clutch 4 Open flywheel 3 radially outside of friction surface 25 . To further improve the cooling, the radially inner passages 29 and the radially further outside passages 32 of the second flywheel 3 can be connected to one another via radially extending ventilation channels or grooves, which are provided and dash-dotted on the side of the second flywheel 3 facing away from the friction surface 25 are indicated and marked with 33. The axial passages or recesses 29 , 30 and 32, 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 34 , 35 are provided to seal the annular chamber 11 , which is partially filled with viscous medium. In the illustrated embodiment, the two lines you 34 , 35 are each membrane-like and made in one piece. However, the two seals 34 , 35 could also be formed by separate resilient components. The radially inner seal 34 is supported on the radially extending area 14 of the flywheel mass 2 , specifically on a diameter range which is located radially outside the average friction diameter 27 of the friction surface 25 of the flywheel mass 3 . Radially on the outside, the seal 34 merges into a radially extending region 36 , which is annular and is clamped between the annular region 22 a of the flange 22 and, viewed in the circumferential direction, between the ventilation channels 31 on the flywheel 3 , projections 37 . The annular region 36 connects the two seals 34 , 35 and has accordingly arranged recesses for carrying out the rivets required for the blind rivet connections 23 . The radially directed, also axially resilient, membrane-like seal 35 is supported radially on the outside against the radial wall 19 a and merges radially on the inside into an axial region 38 , which in turn is connected to the radial region 36 . As can be seen from FIG. 1, the axially resilient region 35 is arranged radially outside the friction surface 25 . The design and arrangement of the seals 34 , 35 ensures that the free space or air gap 28 , which is seen directly between the two flywheels 2 and 3 , has a relatively large radial extent, thereby cooling the friction surface 25 aufwei send flywheel 3 can be significantly improved. Furthermore, due to the arrangement of the membrane-like seal 34 , the radially outer ventilation channels 32 can be guided axially past the seal 34 axially and open out on the coupling side. In the area of the passages 32 , the clutch cover 39 has in its radially outer screwing area or edge area 40 and possibly also in its other areas interruptions 41 or recesses 42 which cooperate with the passages 32 to generate a cooling air flow. The interruptions 41 can be formed by axial bulges of the cover 39 , which supply means for receiving torque transmission, such as. B. leaf springs are used. The radially inner seal 34 arranged in the radially outer region of the friction surface 25 seals the free space or the air gap 28 with respect to the annular space 11 lying radially further outward.

To reduce the heat transfer from the flywheel 3 to the annular space 11 between the can with the Kraftspei Chern 10 cooperating flange 22 and between the individual segments and the flywheel 3, an intermediate layer of a thermally insulating material such. B. made of a heat-resistant plastic material. Instead of an intermediate layer, the seal 34 or 35 or both seals 34 , 35 can also be made of a material which has a low thermal conductivity. As a result, the radial areas 36 of the seals, which are clamped axially between the flywheel 3 and the flange body by 22 or the segment-like parts, act as thermal insulation.

The shell-type body 19 carries a starter ring 43 which is connected via a welded connection to the shell body 19th The starter ring gear 43 extends axially and encompasses the outermost contours of the flywheel 3 in the circumferential direction.

The roller bearing 6 a is pressed onto the shoulder provided in the end region 15 a of the axial extension 15 . The bearing 6 a is also included in the central recess of the second Schwungmas 3 with an interference fit. The axial support of the flywheel mass 3 with respect to the flywheel mass 2 takes place on the one hand via a radial shoulder 17 a, which is provided on the second flywheel mass 3 and radially engages over the outer bearing ring 17 at its end facing the clutch disc 5 , and on the other hand via a radial support step 16 a , which is integrally formed on the axial extension 15 on the disc 5 facing away from the inner bearing ring 16 . Over the shoulder 17 a and the support step 16 a, the disengagement force of the clutch 4 can be intercepted by the bearing 6 a.

The axial extension 15 of the flywheel 2 delimits a cavity 45 into which the end regions 46 of the hub 47 of the clutch disc 5 engage axially. A transmission input shaft accommodating the hub 47 can also extend axially into the cavity 45 . A pilot bearing 48 , in which the end journal of the transmission input shaft is centered, can be accommodated radially within the axial projection 15 in order to support the transmission shaft engaging in the cavity. From embodiments in which the pilot bearing is received directly in the output shaft of the internal combustion engine and is centered, the transmission input shaft can extend axially over the entire length of the axially continuous cavity 45 .

Together with the clutch unit, consisting of clutch 4 and clutch disc 5 , the dual-mass flywheel 1 forms a unit A, which is preassembled as such, shipped and stored and can be screwed onto the crankshaft of an internal combustion engine in a particularly simple and efficient manner. The assembly A thus already has the bearing 6 integrated , which is applied to the axial extension 15 , which in turn is provided on the first flywheel 2 . In addition, the fastening screws 8 are already pre-assembled or contained in the bores 7 of the flange region 14 , in the form of Allen screws 8 . There are, as shown in the lower half of FIG. 1, the screw heads 50 axially in such a position between the flange 51 of the clutch disc 5 and the fastening area 14 a of the first flywheel 2 , and the thread areas 52 are dimensioned so and, as described below, held so that they do not protrude axially beyond the contour 53 of the first flywheel 2 , that is to say the contour 53 facing the motor. In this position, the screws 8 are securely held in the unit A, on the one hand by the areas of the flange 51 which cover them, and on the other hand by flexible means which hold the screws in such a position that the threaded areas 52 do not run out protrude from the openings 7 . These resilient means are dimensioned such that their holding force is overcome when the screws 8 are tightened. Such a flexible means can be formed by a plastic intermediate layer which surrounds the threaded area 42 of a screw 8 in the axial area of a bore 7 . This inter mediate position is clamped between the screw thread 42 and the bore 7 .

The clutch disc 5 is clamped in a pre-centered to the axis of rotation of the crankshaft between the pressure plate 54 and the friction surface 25 of the second flywheel 3 and also in such a position that the openings 55 provided in the hitch be in a position such that the assembly process of the Unit A on the output shaft of the internal combustion engine can be moved through a screwing tool. It can be seen that the openings 55 are smaller than the heads 56 of the screws 8 , so that thereby a flawless and losier safe mounting of the screws 8 in the assembly A is guaranteed.

Openings or cutouts 58 are also provided in the plate spring 57 , specifically in the region of their tongues 57 a, for the passage of the screwing tool. The cut-outs 58 may be provided in such a way, they dab widenings or expansions of the form between the tongues 57 a existing slots. The openings 58 in the plate spring 57 , 55 in the clutch disc 5 and 29 in the flywheel 3 overlap each other in the axial direction in such a way that even with a position to be carried out due to assembly of the unit A on the crankshaft required asymmetrical arrangement of the holes 7th an assembly tool, such as an Allen wrench, properly through the openings 58 in the plate spring 57 and 55 in the clutch disc 5 , pass through and can engage in the recesses of the heads 56 of the screws 8 . The passages 58 for the screwing tool are also smaller than the heads 56 of the screws 8 .

Such a complete assembly A facilitates the assembly of the Flywheel considerably, because there are no different  Operations such as the otherwise required centering operation for the clutch disc, the operation for the Inserting the clutch disc, fitting the clutch, the insertion of the centering mandrel, the centering of the dome washer itself, inserting the screws and the Screw on the coupling and remove the centering pin nes.

In the upper half of FIG. 1, the position of a screw 8 is indicated, which this screw assumes after fastening the unit A to the output shaft of an internal combustion engine.

In the embodiment variant of a bearing 106 between the two flywheels 102 , 103 shown in FIG. 2, the component 113 which forms the main component of the first flywheel 102 carries an axial shoulder 115 radially on the inside, which is formed by a separate component which is connected to the radially inner one , A recess delimiting areas of the component 113 formed by a sheet metal part is attached. This attachment can be done by means of a welded connection. The approach 115 has at its end facing the internal combustion engine, an axial and radial region having step 115 b, on which the inner regions, in particular the inner lateral surface, of the central recess of the component 113 are received. The roller bearing 106 a, which is only shown schematically here, is accommodated in a similar manner, as described in connection with FIG. 1, on the axial shoulder 115 and in a central bore of the second flywheel mass 103 , here additionally between the radially outer bearing ring and the second one Flywheel 103 an intermediate ring 103 a, which can be pressed in, is provided, which is made of a material with low thermal conductivity, such as. B. a heat-resistant plastic. This intermediate ring 103 a forms a thermal insulation between the second flywheel 103 and the roller bearing 106 a. The shoulder 117 a for axially supporting the second momentum mass 103 is gebil det by a disc-shaped member 160 , which means not shown, such as. B. rivet, is firmly connected to the second flywheel 103 . Axial recesses 161 are provided in the disk-shaped component 160 for the passage of the screw heads 156 . The hub 152 of the clutch plate 105 engages with the projection 115 defined by the cavity 150 with its end portion 151st A pilot bearing 153 is provided in the cavity 150 for the end of a transmission input shaft. The pilot bearing 153 is centered on the axial extension 115 .

A securing ring 162 , which can be designed as a resilient ring, is provided for axially securing the roller bearing 106 a on the axial extension 115 . The locking ring 162 engages in a radial groove 163 which is introduced in the axial end region 115 a of the axial extension 115 , specifically on the side of the bearing 106 a facing the clutch disc 105 . The inner bearing ring of the roller bearing 106 a is thus axially held axially between the retaining ring 162 and the radial shoulder 116 a of the axial extension 115 .

In the embodiment shown in FIG. 3, the roller bearing 206 a is received on an axial shoulder 262 of the second flywheel mass 203 , specifically via the inner ring 216 . The outer ring 217 is received within an axial shoulder 215 of the first flywheel 202 . The two axial lugs 215 , 262 partially overlap in the axial direction and form an annular space in which the roller bearing 206 a is received. The axial extension 215 is formed in one piece with the essentially radially extending component 213 , which is used to fasten the second flywheel 202 to the output shaft of an internal combustion engine. The approach 215 could, however, also be formed by a tubular or sleeve-shaped part attached to the component 213 .

In the embodiment according to FIG. 4, only the second flywheel 303 has an axial extension 362 on which the roller bearing 306 a is received radially on the outside. The outer bearing ring of the bearing 306 a is received in a central bore 363 of the first flywheel 202 . The roller bearing 306 a is located radially within the bores 307 for receiving fastening screws for the articulation of the first flywheel 202 on the output shaft of an internal combustion engine.

In the case of very small installation conditions, in the individual exemplary embodiments described, the roller bearing can also be designed in such a way that at least one of the raceways of the roller bearing is formed directly on one of the axial projections, so that no special bearing ring is required. However, all the rolling tracks can also be formed directly on components of the two flywheels, so that only rolling elements are then required. So z. B. in the embodiment of FIG. 1, the inner bearing ring 16 is omitted and the corresponding rolling track can be formed directly on the axial extension 15 . In the embodiment according to FIG. 3, both bearing rings 216 , 217 could be omitted and the corresponding rolling tracks for the rolling elements could be formed directly on the axial projections 215 , 262 .

In Fig. 5 a divided flywheel 401 is shown having one machine to a not-shown crank shaft of an internal combustion fastened, first or primary flywheel mass 402 and a second or secondary flywheel mass 403rd On the second flywheel 3, a friction coupling 404 is mounted with the interposition of a clutch disk 405 through which a likewise not signed transmission increases and can be uncoupled. The flywheels 402 and 403 are mounted to each other via a bearing 406 so that their rolling elements, such as balls, are arranged radially inside the bores 407 for carrying out fastening screws 408 for mounting the first flywheel 402 on the output shaft of the internal combustion engine. Between the two momentum masses 402 and 403 , similar to Fig. 1, the damping device 409 is effective, the helical compression springs be seated, which are housed in an annular space 411 , which forms a torus-like area. The annular space 411 is at least partially filled with a viscous medium, such as oil or fat.

The primary flywheel mass 402 is predominantly formed by a component 413 which was produced from sheet metal material. The component 413 has a substantially radially extending, flange-like region 414 , which has holes or holes 407 radially on the inside.

The single-row ball bearing 406 a is made as a sheet metal bearing and has a radially inner raceway for the balls bearing ring 416 , which is centered relative to the primary flywheel mass 402 and a radially outer raceway outer bearing ring 417 , which carries the secondary flywheel mass 403 . The bearing ring 416 forming the inner rolling track has an axially shaped shoulder 416 a which is formed radially on the inside and points in the direction of the clutch disc 405 and which forms the rolling track radially on the outside. The axial extension 416 a is at least approximately at the same axial height with the secondary flywheel mass 403 . The axial bearing ring approach 416 a goes at its end facing away from the clutch disc 405 th into a radially outwardly extending annular gradation 416 b, which in turn opens into a radially outwardly directed flange-like or disc-like region 416 c. To center the bearing ring 416 , the component 413 made of sheet metal has moldings in the form of impressions 413 a, which cooperate with the outer diameter of the disk-shaped region 416 c for centering the bearing ring 416 . The disc-shaped area 416 c has recesses 407 a, which overlap with the axial recesses 407 - seen in the axial direction. The recesses 407 and 407 a can have the same cross section. When mounting the flywheel 401 on the output shaft of the internal combustion engine, the radially inner areas 414 a of the annular component 413 are axially clamped between the screw-on flange of the output shaft of the internal combustion engine and the disk-like area 416 c of the bearing ring 416 . So it is the bearing ring 416 secured by the screws 408 on the output shaft of the internal combustion engine.

The bearing ring 417 has formed radially on the inside in the direction of the component 413 axial shoulder 417 a, which forms the outer rolling track. At its end facing the clutch disc 405 , the axial extension 417 a merges into a disc-shaped region 417 b running radially outwards. Over this area 417 b, the bearing ring 417 carries the secondary flywheel mass 403 . For this purpose, the disk-like portion 417 b radially outwardly connected by rivet connections 403 a to the secondary flywheel mass 403rd The flywheel 403 has an axial recess 403 b, which forms a centering surface for the bearing ring 417 , this centering surface formed by the recess 403 b cooperating with the outer lateral surface of the radial bearing region 417 b.

The essentially radially extending region 414 merges radially on the outside into a half-shell or C-shaped region 418 which at least partially encompasses and guides or supports the energy accumulators at least over their outer circumference. The radially outer, shell-like region 418 of the sheet metal body 413 is axially offset toward the internal combustion engine in relation to the regions 414 lying radially further inward. At its end pointing in the direction of the second flywheel mass 403 or the coupling 404 , the shell-like region 418 carries a likewise shell-like body 419 , which can be formed from sheet metal and also serves to form or delimit the annular space 411 . The body 419 is welded to the sheet metal body 413 and has a radially inwardly extending section 419 a. When viewed in the circumferential direction, the toroidal region 412 formed by the shell-like body 419 and the shell-like region 418 is divided into individual receptacles in which energy stores are seen. The individual recordings are, viewed in the circumferential direction, separated from one another by areas of application for the energy accumulators, which can be formed by pockets 418 b, 419 b embossed into the sheet metal part 413 and the shell-like body 419 . The application areas 421 for the energy accumulators connected to the second flywheel mass 403 are carried by the clutch cover 422 .

The application areas 421 are formed by radial arms 421 , which are integral with the clutch cover 422 and engage radially in the annular space 411 , namely between the ends of adjacent energy stores in the circumferential direction. The application areas or arms 421 are connected radially on the inside to an axially extending, cylindrical area 423 of the cover 422 . The axially extending Deckelbe rich 423 envelops or engages with a portion 423 a, the second flywheel 403 and is connected to this via 423 a introduced into the impressions 424 , which engage in corresponding recesses of the flywheel 403 , firmly connected. To position the second flywheel 403 relative to the clutch cover 422 during their connection, the cover 422 can have an axial shoulder on which the flywheel 403 can be supported axially.

As can be seen from FIG. 5, the annular space 411 or its toroidal region 412 is predominantly arranged radially outside the outermost contours of the second flywheel mass 403 . Thereby, the serving and for the articulation of the first flywheel mass 422 on the output shaft of the internal combustion engine, the toroidal region 411 may bearing member 413, which is adjacent to the internal combustion engine, and the second flywheel mass 403 radially within the annular space 411 located over a relatively large radial extent, under Formation of an intermediate space or air gap 430 , directly opposite, that is to say directly adjacent, which enables a very compact design in the axial direction of the assembly consisting of flywheel 401 , clutch 404 and clutch disc 405 . In the exemplary embodiment shown, the flywheel mass 403 is adjacent to the motor-side component 413 over practically its entire radial extent. This is made possible, inter alia, by the fact that the sealing of the annular space 411 is ensured by a seal 431 , which is effective between the inner conical regions of the radial section 419 a and an outer, formed on the outer periphery of the cover 422 sealing surface. Due to the construction according to the invention, he does not stretch any components radially between the two flywheels 402 and 403 .

The space 430 is used to cool the flywheel 401 , specifically by passing a cooling air flow through this space 430 . To generate such a cooling air circulation, the radial region 417 b of the bearing 406 has radial recesses 433 radially inside the rivet connections 403 a. The air flow opening through the recesses 433 flows directly past the region 414 or is directed towards this region 414 . In addition or as an alternative to the recesses 433 , the radially extending region 414 of the sheet metal body 413 can have axial passages 434 which connect the intermediate space 430 to the side of the component 413 facing the motor. To improve the cooling, the second flywheel mass 403 can have further axial passages 435 , which are located radially further outwards and are connected to the intermediate space 430 on the side facing away from the friction surface 432 and radially outside the friction surface on the side of the flywheel mass 403 facing the clutch 404 432 discharge. The passages 435 are delimited radially on the outside by the axial section 423 a of the cover 422 , which engages around the flywheel mass 403 . The axial passages or recesses 433 , 434 and 435, viewed in the circumferential direction, can be elongated. The recesses 433 serve at the same time to receive or pass through the fastening screws 408 .

To seal the annular chamber 411 , which is partially filled with viscous medium, a seal 436 located radially further inwards and the seal 431 arranged radially further outward are provided. The seal 436 is formed by a diaphragm-like or plate spring-shaped component which is supported on the radially extending region 414 of the flywheel mass 402 , namely on a diameter range which is located radially outside the mean friction diameter of the friction surface 432 of the flywheel mass 403 . The seal 436 is centered radially on the outside on the cover 422 . The axially spring-loaded seal 436 is provided at the radial height of the ventilation ducts 435 of the flywheel 403 . The design and arrangement of the seals 431 , 436 ensures that the free space or air gap 430 , which is provided directly between the two flywheels 402 and 403 , has a relatively large radial extent, thereby cooling the flywheel 432 having the friction surface 403 can be significantly improved. Furthermore, due to the arrangement of the seal 431 , the radially outer ventilation channels 435 can be guided axially past this seal 431 axially and open out on the coupling side. The clutch cover 422 has in its axially extending region 423 recesses 438 which cooperate with the passages 435 to generate a cooling air flow.

The clutch 404 , the clutch disc 405 and the two-mass flywheel 401 , similar to that described in connection with FIGS . 1 and 2, form a structural unit which is preassembled.

The invention is not shown and in detail NEN described embodiments, but limited includes in particular variants, which by combinations by individual, in connection with the various designs tion forms described features or elements can be.

Claims (35)

1. Torque transmission device with a first, ver bindable to a motor, and a second, a gear can be coupled and uncoupled flywheel, which are rotatably mounted relative to each other and between which a damping device is provided, with force storage devices effective in the circumferential direction, characterized in that that screws ben for attaching the first flywheel to a driving shaft are already captive before said attachment in the device and the centrifugal masses centering position tion is at least essentially hen on a smaller diameter than the screw holes of the first centrifugal mass can be carried out Screws and that in the other flywheel through holes are provided through which the screws can be tightened at least for fastening the unit to the shaft. 2. Torque transmission device according to claim 1, characterized records that the bearing has an axial approach to one of the flywheels encloses.   3. Torque transmission device according to claim 2, characterized records that the flywheel also has the axial approach a chamber that holds the energy accumulators effective in the circumferential direction records and contains a viscous medium. 4. Torque transmission device according to one of claims 1 to 3, characterized in that the bearing uses a rolling bearing, the sen inner ring sits on a hollow axial approach one of the swing masses and the outer ring carries the other flywheel and that the diameter of the outer ring is smaller than the diameter on which the screw holes are provided. 5. Torque transmission device according to one of claims 2 to 4, characterized in that the axial approach is integral with the Flywheel. 6. Torque transmission device according to one of claims 2 to 5, characterized in that the hub of the clutch disc of the Rei Exercise coupling immersed axially in the hollow approach. 7. Torque transmission device according to one of claims 1 to 6, characterized in that the through holes in the second Inertia are smaller in diameter than the heads of the screws.   8. Torque transmission device according to one of claims 4 to 7, characterized in that one of the bearing rings of the rolling bearing is integrally formed with an axial approach one of the flywheel sen. 9. Torque transmission device according to claim 8, characterized records that the radially outer bearing ring is in one piece with that with the first flywheel-linked approach. 10. Torque transmission device according to at least one of the preceding existing claims, characterized in that the shared momentum wheel, together with a clutch unit, consisting of clutch and clutch disc, one attachable to the output shaft of the engine Unit forms. 11. Torque transmission device according to claim 10, characterized records that the structural unit also includes the two flywheels other centering bearings included. 12. Torque transmission device according to one of claims 1 to 11, characterized in that the screws in the screw hole stanchions are kept axially captive.   13. Torque transmission device according to one of claims 1 to 12, characterized in that the screws by compliant means are held. 14. Torque transmission device according to one of claims 10 or following, characterized in that the clutch disc in a for Rotation axis of the crankshaft precentered position between second Flywheel and clutch pressure plate is clamped. 15. Torque transmission device according to at least one of the An Proverbs 10 to 14, characterized in that in the clutch disc There are openings that are congruent with the screw drill holes for attachment to the engine and that the clutch disc in this way between the second flywheel and the pressure plate of the dome It is clamped that the screw holes and the opening cover each other. 16. Torque transmission device according to one of claims 10 to 15, characterized in that in the disc spring of the clutch in the area the tongues openings are provided for the insertion of a screw exercise tool and that these openings are covered with the opening in the clutch disc and the holes in the support flange for the Camp.   17. Torque transmission device according to claim 16, characterized records that the openings in the disc spring and in the clutch plate are aligned with the holes in the supporting flange. 18. Torque transmission device according to claim 17, characterized shows that the openings in the disc spring are evenly divided and are larger in diameter than the diameter of the screw mechanism stuff, in such a way that even with offset holes in the flange or the screwing tool (s) meets the screw. 19. Torque transmission device according to one of claims 16 or following, characterized in that the openings in the disc spring designed for the passage of a screwing tool and smaller are as the heads of the mounting screws. 20. Torque transmission device according to one of claims 15 or following, characterized in that the openings in the coupling disc designed for the passage of a screwing tool and are smaller than the heads of the fastening screws. 21. Torque transmission device according to one of claims 1 to 20, characterized in that the openings in the second flywheel designed for the passage of a screwing tool and smaller are as the heads of the mounting screws.   22. Torque transmission device according to one of claims 1 to 21, characterized in that the length of the fastening screws such dimensioned and these are held in the unit so that the heads are located in the interior of the installation space enclosed by the coupling and the thread areas axially within the contour of the motor first flywheel. 23. Torque transmission device according to one of claims 1 to 22, characterized in that the first flywheel also the pilot bearing wearing. 24. Torque transmission device according to one of claims 10 to 23, characterized in that the coupling is releasably attached to the unit is. 25. Torque transmission device according to one of the preceding An sayings, characterized in that the two flywheels rolling bearings are made of sheet metal material. 26. Torque transmission device according to one of the preceding An sayings, characterized in that at least one of the bearing rings egg NEN has an axially extending region that bil at least one rolling track det, as well as a radial disc artery connected to the axial region area for connecting the bearing ring to one of the flywheels sen.   27. Torque transmission device according to one of the preceding An sayings, characterized in that both bearing rings have an axial loading have rich to form at least one rolling track and a radi own area for attachment with a flywheel. 28. Torque transmission device according to one of claims 25 to 27, characterized in that the inner bearing ring with the primary Flywheel mass and the outer bearing ring with the secondary flywheel mass is connectable. 29. Torque transmission device according to one of the preceding An sayings, characterized in that both bearing rings a radial after have flange-like area facing outside. 30. Torque transmission device according to one of claims 25 to 29, characterized in that the radial area of the with the secondary flywheel connected bearing ring has openings, which overde are screwing with the screw holes for fastening the Pri Flywheel mass on the engine. 31. Torque transmission device according to one of claims 10 to 30, characterized in that the clutch cover with an axial loading reaches around the secondary flywheel mass and with it into the Section of the axial area encompassing the secondary flywheel mass  introduced impressions, which in corresponding depressions of the Intervene in the flywheel, is firmly connected. 32. Torque transmission device according to one of the preceding An sayings, characterized in that the holding force of the screws in overcome the axially securing means by tightening the screws that will. 33. Torque transmission device according to claim 32, characterized records that the securing means the screws in a certain axi Clamp the whole position. 34. Torque transmission device according to one of the preceding An sayings, characterized in that both on the first, as well as on an axial approach is provided for the second flywheel mass and between this the bearing centering the centrifugal masses is provided. 35. Torque transmission device according to claim 34, characterized records that the axial approach of the second flywheel axially in the hollow axial approach of the first flywheel protrudes.