DE3448536C2

DE3448536C2 - Torque transmission device

Info

Publication number: DE3448536C2
Application number: DE3448536A
Authority: DE
Inventors: Oswald Friedmann
Original assignee: LuK GmbH and Co KG
Current assignee: LuK GmbH and Co KG
Priority date: 1983-11-10
Filing date: 1984-03-05
Publication date: 1998-06-04
Anticipated expiration: 2004-03-06
Also published as: JPS60116942A; JPH0723743B2; FR2554891A1

Description

The invention relates to a torque transmission device a first, attachable to the output shaft of an internal combustion engine and a second, a transmission can be switched on and off via a clutch Inertia, which can be rotated relative to one another via a bearing are and between which a damping device is provided with in Effective energy accumulators in the circumferential direction.

Such torque transmission devices have become known, for example, and are described in FR-PS 2 166 604. This document shows an engine-clutch-manual transmission group with a torsionally elastic connecting means between the engine crankshaft and a flywheel, which is one of the input elements of a clutch, the output element of which is rotatably connected to the input shaft of a manual transmission. The two flywheel parts 10 and 5 connected via a damper 26 are held coaxially with one another via a roller bearing 11 and can rotate relative to one another against the action of the energy accumulator 26 by a limited angle.

Such torque transmission devices with a structure according to the FR-PS have already proven themselves in general in vehicle use like in vehicles where the axial space is not so extreme is cramped, as is the case with those with a transverse arrangement of the drive unit motor and transmission is the case in many cases, namely predominantly in vehicles with longitudinal arrangement of engine and transmission. For vehicles with very limited space for the drive unit, especially for such with transverse arrangement of engine and gearbox, are such two masses flywheels just because of the limited space available in them technically applicable way applicable.

The object of the present invention was to provide a torque Carrier device with a damping device to create the opposite the previously known torque transmission devices of type mentioned an improved function and a longer shelf life has, a simple structure and light and simple together construction with small dimensions and thus an extended installation area by simply adapting to the respective application and ensures cost-effective production. In addition, a Wall-free storage of the flywheels relative to each other and an optimized Lifetime can be guaranteed.

This object is achieved according to the invention in that the storage radially inside the screw holes for that of the internal combustion engine machine side of the first flywheel screwed away Screws for attaching the first flywheel to the output shaft of the Internal combustion engine is provided and that in the second flywheel the screw holes aligned, an actuation of the screws allowable passage recesses are available.

These passage recesses can be used to carry out at least one Screwing tool for attachment, e.g. B. screwing, the Torque transmission device on the output shaft of the internal combustion engine serve. The passage recesses in the second flywheel can advantageously be designed such that the screws can be inserted axially, ie have a cross section that enables the axial passage of a screw head. Through a such a structure of the torque transmission device can behave small and inexpensive bearings can be used.

By using a rolling bearing with a small diameter, it is possible, including the bearing width, i.e. the extent of the bearing in the axial direction, to reduce and use a narrow bearing, for example also the effect of any dream movements of the two Inertia are reduced to each other and so the bearing in the axial direction burden less. Furthermore, the bearing load is reduced by the Verrin reduction in peripheral speeds resulting from the reduction of the bearing diameter results. By using a roller bearing with smaller ones Dimensions, it is therefore also possible to determine the axial dimensions of the ge to keep the entire unit smaller, so that the axial space requirement is reduced device. This enables the field of application to be expanded in this way stalten torque transmission device, so that for example Vehicles with transversely installed front-wheel drive unit with such Dual mass flywheel can be equipped.

It can be particularly useful if at least one of the momentum has an axial extension to accommodate the bearing.

It can prove to be particularly useful if the extension is integral with one of the flywheels. For some applications it can also be advantageous if the extension is one of this flywheel is a separate component.

The invention enables particularly simple handling and assembly and inexpensive manufacture by the torque transmission device in Form a split flywheel a pre-assembled and on the output shaft the internal combustion engine attachable unit that the two Inertial masses can include bearings in relation to each other.

Furthermore, it can be with a torque transmission according to the invention supply device prove to be advantageous if the axial extension Has recess for mounting the gear shaft.

In addition, it can be described in a torque transmission device benen kind of advantage if the second flywheel a bearing to the location tion of the transmission input shaft, the so-called pilot bearing. For inventions torque transmission devices according to the invention, it can be advantageous if the bearing is formed by a roller bearing, the inner ring of the Bear the roller bearing on the axial extension of one of the centrifugal masses and the outer ring can carry the other flywheel and the diameter water of the outer ring smaller than the diameter on which the screw Exercise holes are provided, can be.

It can also prove to be advantageous to mount the bearings with a plain bearing form, it may be useful if the plain bearing self-lubricating is. However, it can also be designed as a dry sliding bearing or with a Be lubricated.

In a torque transmission device according to the invention, it can be from Be advantageous if the plain bearing has a conical or conical cross-section has, the tapering region of the plain bearing in the direction of the internal combustion engine can point away.

Furthermore, it can prove to be advantageous if the two contact surfaces for the plain bearing in the second and first flywheel opposite Ko nicity, with the seal ring nestling against these surfaces.

In the case of a plain bearing, it can generally be advantageous if the plain bearing is in the direction of the taper under an axial biasing force, whereby a automatic play compensation or automatic wear adjustment of the Plain bearing is made possible. It may also be convenient if the camp is slotted.

In a torque transmission device according to the invention, it can be from Be advantageous if the energy accumulator at least the two masses push back almost to their starting position. It can also be beneficial be to train a torque transmission device according to the invention that the second has a friction surface for a clutch disc The flywheel is in one piece.

It may prove useful if the first flywheel and / or the second flywheel immediately a seat or a seat form for storage. In general, it can be particularly advantageous if between the two flywheels in addition to a torsionally elastic Damping device a slip clutch connected in series with this is provided.

Further objectives, features and advantages of the invention result from the following figure description of exemplary embodiments.

It shows:

Fig. 1 a damping device partially sectioned according to the invention,

Fig. 2 shows a possible embodiment of an effective between the two flywheels of a damping device according to the invention, the friction device

Fig. 3 to 6 further variants from the invention.

The damping device shown in FIG. 1 1 for receiving and compensating for rotational shocks has a flywheel 2, which is divided into two flywheel masses 3 and 4. The flywheel 3 is attached to the crankshaft 5 of an internal combustion engine, not shown, via fastening screws 6 . On the flywheel 4 , a friction clutch 7 is attached by means not shown. Between the pressure plate 8's of the friction clutch 7 and the flywheel 4 , a clutch disc 9 is easily seen, which is received on the input shaft 10 of a transmission, not shown. The pressure plate 8 of the friction clutch 7 is acted upon in the direction of the flywheel 4 by a plate spring 12 pivotably mounted on the clutch cover 11 . By actuating the friction clutch 7 , the flywheel mass 4 and thus also the flywheel 1 can be engaged and disengaged from the transmission input shaft 10 via the clutch disc 9 . Between the two momentum masses 3 and 4 , a damping device is easily seen, which is formed by force storage in the circumferential direction in the form of coil springs 13 , only one of which is shown, and a friction device 14 , 15 .

The two flywheels 3 and 4 are rotatably mounted relative to each other via a bearing 16 . The bearing 16 consists of a rolling bearing 17 , the outer bearing ring 17 a in a bore 18 of the momentum mass 3 and the inner bearing ring 17 b on a central, axially extending in the direction of the crankshaft 5 cylindrical pin 19 of the momentum mass 4 is rotatably arranged . The inner bearing ring 17 b is secured against the pin 19 via a spring connection 20 against rotation.

The flywheel 3 has a radially extending flange 21 which forms the input part for the force accumulator 13 of the damping device. Disks 22 , 23 are arranged on both sides of the flange 21 and are connected in a rotationally fixed manner at an axial distance from one another via spacer bolts 24 . The spacer bolts 24 also serve to fasten the two disks 22 , 23 to the flywheel 4 . In the disks 22 , 23 and on the flange 21 , recesses 22 a, 23 a and 21 a are made, in which the energy accumulator 13 of the damping device are received. The energy stores 13 counteract a relative rotation between the two flywheels 3 and 4 . The friction device 14, 15 has too directed between the successive end surfaces 3 a, 4 a of the two flywheel masses 3, 4 in front of the viewed friction ring 14 and a two flywheels 3 and 4 are axially clamped force store in the form of a plate spring 15 °. The bias of the plate spring 15 causes the friction ring 14 provided in the radially outer edge region of the flywheel 2 to be axially clamped between the two flywheels 3 and 4 . The flywheel 3 has a shoulder 3 b, on which the friction ring 14 is taken up for centering men. The prestressed plate spring 15 is supported radially on the outside on a shoulder 3 c of the flywheel 3 and radially on the inside on the radially outer region 22 b of the disk 22 and thus braces the two flywheels 3 and 4 towards one another.

So that the friction ring 14 is clamped between the two flywheels 3 and 4 even when worn by the plate spring 15, an axial displacement possibility is provided between the inner bearing ring 17 b of the rolling bearing 17 and the pin 19 by an axial clearance 25 between the inner bearing ring 17 b and the flywheel 3 is provided. The clamping voltage of the two centrifugal masses 3 and 4 avoids that even with a production-related play in the storage 16, the centrifugal mass 3 can wobble, that is to say that the centrifugal mass 3 is always held in a plane perpendicular to the axis of rotation 26 by the bracing. Thus, in the embodiment shown in FIG. 1, the roller bearing 17 provided in the axial height of the flywheel 3 only needs to take over the radial guidance of the flywheel 4 .

So that the flywheel 2 can be mounted as a unit on the crankshaft 5 , the pin 19 of the flywheel mass 3 and the bearing 16 are provided radially within the screws 6 for fastening the flywheel mass 3 to the crankshaft 5 . Furthermore, in the radially extending region 27 of the centrifugal mass 3 recesses 28 are introduced, through which the screws 6 can be carried out.

The friction ring 114 shown in FIG. 2 has a V-shaped cross section and is between an annular groove 104 a made in the flywheel mass 104 a and an axial projection 103 a molded onto the flywheel mass 103 , each of which has a V-shaped friction ring 114 are adjusted, clamped. The axial bracing of the friction ring 114 between the two flywheels 103 and 104 can be carried out in a manner similar to that in the embodiment shown in FIG. 1 by means of a plate spring 15 .

The mutual interlocking of the projection 103 a, the annular groove 104 a and the V-shaped friction ring 114 provided between them causes the flywheel mass 104 on the flywheel 103 attached to a crankshaft 5 both in an at least approximately perpendicular to the axis of rotation of the flywheels 103 and 104 Level as well as in the radial direction leads or is centered. It can thus, if necessary, in one embodiment of the friction device according to FIG. 2, which is omitted in FIG. 1 for the radial guidance of the bearing 16 in relation to the flywheels 3 and 4 relative to one another.

In the embodiment shown in FIG. 3, the flywheel 204 is rotatably mounted relative to the flywheel 203 attached to the crankshaft 5 by means of an inclined ball bearing 217 and a radially effective needle bearing 229 provided at an axial distance. The flywheel 204 has a cylin drical pin 219 on which the inner ring 217 b of the angular contact ball bearing 217 is rotatably received. The pin 219 extends into a centrally provided on the crank shaft 5 bore 230 . The needle bearing 229 is provided in the axial overlap area between the bore 230 and the pin 219 .

The inertia mass 203 has a radially inwardly directed away from the crankshaft 5 protrusion 231, whose inner contours form a bore 218 in which the outer race is fixedly received 217 a of the angular contact ball bearing 217 rotating. The flywheel mass 203 further comprises an axially into the bore 230 of the crankshaft 5 extending tubular extension 232, whose outer circumferential surface 232 a is used to center the flywheel mass 203 relative to the crankshaft. 5 Between the inner circumferential surface 232 b of the tubular 232 and the end portions of the pin 219 , the radially effective needle bearing 229 is arranged. The flywheel 203 is attached to the crankshaft 5 in a manner similar to that in FIG. 1 by means of screws 6 . The flywheel mass 204 has recesses 228 through which the screws 6 can be passed, so that the flywheel masses 203 and 204 together with the bearing 216 can be mounted as a unit on the crankshaft 5 .

Disks 222 , 223 are arranged on both sides of the radially extending regions 221 of the flywheel mass 203 and are fixedly connected to one another and to the flywheel mass 204 via spacer bolts 224 . On the side of the flywheel 203 facing away from the angular contact ball bearing 217, a preloaded energy accumulator in the form of a plate spring 215 is provided between the radially running regions 221 and the disk 222 . The prestressing of this disc spring 215 causes the angular contact ball bearing 217 to remain axially clamped, as a result of which the flywheel mass 204 is also axially fixed with respect to the flywheel mass 203 . The plate spring 215 also causes frictional damping in a relative rotation between the two flywheels 203 and 204 .

In the embodiment shown in FIG. 3, the extension 232 and the extension 231 are formed in one piece with the flywheel 203 or the radially extending regions 221 of this flywheel. To simplify the production, however, the division into different components according to the dashed line 233 can be done.

On the side of the flywheel 203 or the journal 219 facing away from the crankshaft 5 , a central bore 234 is provided, in which a pilot bearing 235 is provided for the journal 110 a of a gear shaft 110 .

In the variant shown in FIG. 4, the flywheel 304 is rotatably supported by means of a slide bearing 316 in relation to the flywheel 303 fastened to a crankshaft 5 by means of screws 6 . The bearing 316 comprises a plain bearing bush 317 which is provided between a central recess 318 of the flywheel mass 303 and the central pin 319 of the flywheel mass 304 which extends axially into this recess 318 . The slide bearing 316 further comprises a disc-shaped axial sliding bearing 329 , which is arranged between the end face 319 a of the pin 319 and the support surface 5 a provided on the crankshaft 5 . An annular support shoulder 5 b is provided on the crankshaft 5 for centering the axial sliding bearing 329 . The axial sliding bearing 329 serves to absorb the axial forces which act during the actuation of the friction clutch (not shown) attached to the flywheel 304 in the direction of the crankshaft 5 .

The pin 319 has a central bore 334 , in which a slide bearing 335 is arranged for mounting the end pin 310 of a transmission input shaft.

To seal the bearing space 336 formed by the recess 318 of the flywheel 303 , a sealing ring 337 is provided in the end region of the recess 318 facing away from the crankshaft 5 between the pin 319 and the recess 318 . To receive the sealing ring 337 , a shoulder 318 a is screwed onto the end of the recess 318 .

The crankshaft 5 has an oil supply channel 338 which opens into the storage space 336 and is connected to the pressurized oil circuit of the internal combustion engine. Furthermore, an oil return channel 339 is provided in the crankshaft 5, which starts from the storage space 336 and opens into the crankcase of the internal combustion engine.

Another possibility of lubricating the slide bearing 316 is to provide a grease filling in the bearing chamber 336 . Furthermore, the plain bearings forming the plain bearing 316 could be self-lubricating or so-called dry plain bearings or plain bearings soaked with a lubricant.

In the embodiment shown in FIG. 5, a slide bearing 416 is provided between the cylindrical regions of the pin 419 of the flywheel 404 and the conical recess 418 of the flywheel 403 . The taper of the recess 418 is placed such that the recess 418 decreases in diameter in the direction away from the internal combustion engine. The slide bearing 417 provided between the pin 419 and the recess 418 has a conical or conical cross section which tapers in the direction away from the internal combustion engine. The plain bearing 417 has a carrier ring 417 a, on the outer and inner surface of the plain bearing material 417 b, 417 c is glued or sintered. The slide bearing 417 is slotted on the outer circumference and is acted upon by a plate spring 440 , which is supported on the flywheel 3 radially on the outside by means of a snap ring, in the direction of the tapering of the recess 418 . This action causes the slotted, annular slide bearing 417 to nestle against the cone-shaped recess 418 of the flywheel mass 403 and on the pin 419 of the flywheel mass 404 and this also in the event of wear in the slide bearing 416 . The latter occurs as a result of the preloading of the plate spring 440 , which causes the sliding ring 417 to taper in the direction of the recess 418 .

In the embodiment shown in FIG. 5, the pin 419 used for slide bearing is cylindrical. However, this could also have a conicity of the recess 418 opposite conicity, the inner circumferential surface of the bearing ring 417 or the sliding material 417 c must have a suitably adapted conicity.

The damping device 501 shown in FIG. 6 for compensating for rotary shocks has a flywheel 502 , which is divided into two flywheels 503 and 504 . The flywheel 503 is attached to a crankshaft 5 of an internal combustion engine, not shown, via fastening screws 6 . A friction clutch 7 is attached to the flywheel 504 by means not shown in detail. Between the pressure plate 8 of the friction clutch 7 and the flywheel 504 , a clutch disc 9 is provided, which is received on the input shaft 10 of a transmission, not shown. The pressure plate 8 of the friction clutch 7 is struck in the direction of the flywheel 504 by a plate spring 11 pivotally mounted on the clutch cover 12 Bea. By actuating the friction clutch 7 , the flywheel mass 504 and thus also the flywheel 502 can be coupled in and out via the clutch disc 9 of the transmission input shaft 10 .

Between the flywheel mass 503 and the flywheel mass 504 there is a torsion damping device 513 and a slip clutch 514 connected in series therewith, which enable a limited relative rotation between the two flywheel masses 503 and 504 .

The two flywheels 503 and 504 are rotatably mounted relative to one another via a bearing 515 . The bearing 515 consists of two roller bearings 516 , 517 , which are arranged one behind the other. The outer bearing ring 516 a of the roller bearing 516 is in a bore 518 of the flywheel 503 and the inner bearing ring 517 a of the roller bearing 517 is on a central, in Rich direction of the crankshaft 5 axially extending cylindrical pin 519 of the flywheel 504 rotatably arranged. The inner bearing ring 516 b and the outer bearing ring 517 b of the roller bearings 516 , 517 are rotatably connected to one another via an intermediate part 520 . The intermediate part 520 has a, in the direction of the crankshaft 5 facing approach 520 a, on which the inner bearing ring 516 b is received and a pin 519 of the flywheel 504 encompassing hollow region 520 b, in which the outer bearing ring 517 b is provided .

To ensure that even with very small vibrations, that is, with very small reciprocating relative rotations between the two flywheels 503 and 504, the roller bearing rings 516 b, 517 b, which are non-rotatably connected to one another via the intermediate piece 520 , compared to the masses with the flywheel 503 , 504 rotatably connected roller bearing rings gene 516 a, 517 a are rotated, means of transport 521 , 522 are provided. These transport means 521 , 522 form free-wheel-like locking means, the locking direction of the transport means 521 , 522 being the same with respect to the intermediate piece 520 or to the bearing rings 516 b, 517 b connected to one another in a rotationally fixed manner.

The construction principle shown in FIG. 6 has the advantage that the flywheel 503 can be preassembled onto the crankshaft 5 in the usual manner like a flywheel and then by the flywheel 504 , the damping device 513 , the slip clutch 514 and possibly the flywheel 504 before assembled clutch 7 and the pre-centered between the pressure plate 8 and the flywheel 504 a tensioned clutch disc 9 unit formed by means of the screws 523 can be attached to the flywheel 503 . The bearing formed by the roller bearings 516 and 517 can already be pre-assembled on the flywheel mass 503 or can also be assembled together with the unit mentioned. In the embodiment shown in Fig. 6, the bearing rings 516 b and 517 b are connected to each other via the intermediate part 520 . According to an embodiment variant not shown, the two bearing rings 516 b and 517 b could be formed in one piece or the intermediate part 520 could have the raceways for the rolling elements of the two bearings 516 and 517 .

Furthermore, it is possible to assign the two roller bearings 516 and 517 radially one above the other instead of axially one behind the other, in tight axial space conditions, so that a particularly small axial installation space is necessary for the bearing. With such an arrangement of the two roller bearings 516 and 517 , they can have a common intermediate ring.

Claims

1. Torque transmission device with a first flywheel attachable to the output shaft of an internal combustion engine and a second flywheel that can be switched on and off via a clutch, which are rotatably supported relative to one another via a bearing and between which a damping device is provided, with effective in the circumferential direction Energy storage, characterized in that the bearing ( 16 ) radially inside the screw holes for the screws ( 6 ) screwable from the side of the first flywheel mass ( 3 ) facing away from the internal combustion engine for fastening the first flywheel mass ( 3 ) to the output shaft ( 5 ) the internal combustion engine is provided and that in the second flywheel ( 4 ) with the screw holes aligned, an actuation of the screws ( 6 ) permitting through recesses ( 28 ) are present.

2. Torque transmission device according to claim 1, characterized in that at least one of the flywheels has an axial lengthening tion ( 19 ; 219 , 231 ; 416 ; 519 ) for receiving the bearing.

3. Torque transmission device according to claim 2, characterized in that the axial extension ( 19 , 231 ) is in one piece with one of the flywheels.

4. Torque transmission device according to claim 2 or 3, characterized in that the axial extension has a recess ( 334 ) for mounting the gear shaft ( 310 ).

5. Torque transmission device according to one of claims 1 to 4, characterized in that the divided flywheel is on the down Drive shaft of the internal combustion engine attachable unit forms.

6. Torque transmission device according to claim 5, characterized records that the unit the two flywheels to each other stocked warehouse includes.

7. Torque transmission device according to one of claims 1 to 6, characterized in that the second flywheel ( 204 , 304 ) also carries the pilot bearing ( 235 , 335 ).

8. Torque transmission device according to one of claims 1 to 7, characterized in that the bearing ( 16 ) is formed by a roller bearing ( 16 ).

9. Torque transmission device according to claim 8, characterized in that the inner ring ( 217 b) of the rolling bearing ( 217 ) sits on the axial extension ( 219 ) of one of the flywheels ( 204 ) and the outer ring ( 217 b) the other flywheel ( 203 ) carries and that the diameter of the outer ring ( 217 a) is smaller than the diameter on which the screw holes ( 6 ) are provided.

10. Torque transmission device according to one of claims 1 to 7, characterized in that the bearing is formed by a slide bearing ( 317 , 417 , 417 a).

11. Torque transmission device according to claim 10, characterized in that the sliding bearing ( 317 , 417 , 417 a) is self-lubricating.

12. Torque transmission device according to claim 9 or 10, characterized characterized in that the plain bearing is a dry plain bearing.

13. Torque transmission device according to claim 10, characterized records that the plain bearing is soaked with a lubricant.

14. Torque transmission device according to one of claims 10 to 13, characterized in that the sliding bearing ( 217 , 217 b) has a conical or conical cross section.

15. Torque transmission device according to claim 14, characterized in that the tapering region of the plain bearing ( 417 ) points in Rich direction away from the internal combustion engine.

16. Torque transmission device according to claim 14 or 15, characterized characterized in that the two contact surfaces for the plain bearing in second and first flywheels have opposite taper, the sliding ring nestles against these surfaces.

17. Torque transmission device according to one of claims 14 to 16, characterized in that the slide bearing ( 417 ) is in the direction of the taper under an axial biasing force.

18. Torque transmission device according to one of claims 10 to 17, characterized in that the bearing ( 417 ) is slotted.

19. Torque transmission device according to one of the preceding claims, characterized in that the force accumulator ( 13 ) push the two flywheels back into their starting position.

20. Torque transmission device according to at least one of the preceding Claims, characterized in that the one friction surface for a Coupling disc having second flywheel is integrally formed.

21. Torque transmission device according to at least one of the preceding claims, characterized in that the first flywheel mass and / or the second flywheel mass immediately form a receptacle or a seat for the bearing ( 16 ).

22. Torque transmission device according to at least one of the preceding claims, characterized in that between the two flywheels in addition to a torsionally elastic damping device ( 513 ) a slip clutch ( 514 ) connected in series therewith is provided.