DE3425161C2 - - Google Patents

Description

The invention relates to a torque transmission device with a flywheel for an internal combustion engine, which in two over a roller bearing and against the effect of one Damping device divided rotatable flywheels is, namely on the output shaft of the internal combustion engine firmly connectable first flywheel and a friction surface second to attack a clutch disc Inertia, on which also the clutch disc with a Gear coupling and decoupling friction clutch is stigbar.

It has already been proposed with such torque ment transfer facilities storage immediately between to provide the two flywheels, so that when using a bearing ring with the one Flywheel and the other of the bearing rings with the other Flywheel is non-rotatably connected. Although with torque Transmission devices of this type have very good damping  between the engine and the drive train to achieve vibrations occurring in a motor vehicle is, these could be due to in automotive engineering short service life between the flywheels have not yet enforced storage. This storage forms one of the critical points of such a facility because storage due to the unfavorable operating conditions fails after a short period of operation.

The present invention was based on the object Torque transmission device to create the opposite Torque transmission devices of the aforementioned Kind of an improved function and an increased lifespan has and continues to be particularly simple and economical Licher way is producible.

According to the invention this is achieved in that the Heat flow from the friction surface to the bearing at least reducing Provision in the form of a between the friction surface and the bearing arranged insulation and that further an additional on the insulation attacking seal is provided, wherein the insulation between the support area of the second swing mass and the bearing and the seal between the bearing and Insulation is arranged.

The measures according to the invention on the one hand thermal load on the bearing is reduced since the during  Heat released by the actuation of the friction clutch gie, which in the prior art in the long run inadmissible ge caused thermal stress on the bearing, at least largely cannot get to the warehouse at all. In particular this occurred when using bearings with a small clearance so far on feeding symptoms in storage, as their Ursa che the very occurring between the individual components rapid and different heating and cooling and the related expansion or contraction Differences are to be assumed, whereby the internal clearance through the occurring large temperature differences between the one individual storage parts is lifted. On the other hand, through the invention avoided that, if heating of the Bearing lubricant, such as oil, grease or the like, occur should the lubricant, which becomes thin, escape. It also prevents dirt from entering. So it will always a perfect storage function and therefore also one ensures longer storage life. As a result of that the invention further provides the seal between bearings and provide thermal insulation, i.e. between the insulation on the one hand - which also has the supporting function for the second flywheel has to fulfill - and the camp of others on the one hand, that is, within the insulation, that is, on the thermal stress facing away from the insulation, is also largely abge the heat flow to the seal shields. This gives the main advantage that the seal even with high heating of the insulation  stored flywheel can not be overheated. There through the full seal over the required service life the effect is retained, d. H. the one for the required Sealing effect required elasticity of the seal otherwise it would be lost due to a premature heat Embrittlement.

Depending on the application, it can be advantageous if the Insulation preventing the bearing from overheating Plastic, which may be fiber-reinforced, consists of or from a ceramic material. For the production of plastic insulations can advantageously Thermosets, especially phenoplasts, such as hard paper or but also thermoplastics, e.g. Polytetrafluoroethylene, Polyimide or polyamideimide can be used. It can also be useful, the insulation from a fiber reinforced To produce polycarbonate.

In particular with a torque transmission device, at one of the flywheels has an axial shoulder, the one in the axial direction in a central recess of the other Flywheel protrudes and between the base and recess the storage is arranged, it may be advantageous if the isolation between the central recess and the Warehouse is arranged. In other applications where also one of the centrifugal masses tap a central one has like approach, which in the axial direction in a central  Recess of the other flywheel protrudes, and between Spigot and recess the storage is arranged, it can be useful if the insulation between the zapfenarti gene approach and the camp is arranged.

It can be particularly advantageous if the second swing mass, which can be connected to the input part of a transmission is, which has a central recess and between this and a non-rotatably connected bearing ring the insulation is provided. It can be useful when the re bearing ring of the bearing on the approach of the first flywheel se and the outer bearing ring in the central recess of the second flywheel mass is added, then the insulation tion carries the second flywheel and between the insulation tion and the outer bearing ring, the seal is clamped.

It can be useful if the insulation is also is used as a seal for the bearing. For this can the insulation has molded a seal for the bearing. Such insulation with seal can also in particularly advantageously by at least one in Cross-section L-shaped ring to be formed with a his leg axially covers one of the bearing rings and embraces and with the other of the legs radially in Extends towards the other bearing ring. Is expedient when the radial seal forming the seal Leg one of the L-shaped insulation itself at least  partially extends radially over the bearing ring, which of the Insulation is not axially covered and axially on this Ring supports.

Although it may be sufficient for some use cases, if the insulation is ge by a single L-shaped ring is formed, the axially extending leg at least at least approximately over the entire width of the bearing ring can stretch it, especially for other use cases be advantageous if the insulation by two in the cross cut L-shaped rings is formed, each of one side are applied to one of the bearing rings.

In particular in the case of torque transmission devices which a rolling bearing in a central recess of the Flywheel with friction surface is added, it can be particularly useful if the L-shaped in cross section Insulation rings - seen in cross section - radially towards have inside facing leg and on the outer bearing ring are included.

In order to ensure that the bearing is properly sealed sern, it can be particularly advantageous if the Seal of the bearing serving, radially extending legs of the Insulation rings additionally axially in by a force accumulator Direction of the bearing ring is applied, which of the leg is covered radially so that the leg against  the end face of the bearing ring is pressed. Such one Energy storage can be conveniently by a plate spring be educated.

It may also be appropriate if the L-shaped Insulation ring is designed such that during assembly of the insulating ring on the bearing of the radial one Thigh is resiliently biased and thus on the of supports it radially covered bearing ring resiliently.

When using a disc spring to act on the radial sealing leg of the insulation can be particularly useful if the plate spring is radial outside on the second with the input part of a transmission connectable flywheel supports and radially inside the End regions of the radial leg of the sealing ring axially acted upon.

When using bearings with lubricant filling (so-called permanent lubrication) it can be particularly advantageous if the additional seal between the one of the campers ge axially overlapping and encompassing leg of the L-shaped gene ring and this bearing ring is provided so that also it is particularly effective to prevent the lubricant, e.g. due to centrifugal forces, between the isolates tion and the bearing ring can escape.  

Such a seal can advantageously by a O-ring be formed. The seal can adhere to the inner lack surface of the axially extending leg of the Support insulation and in a recess, e.g. Chamfer or groove, the outer bearing ring must be included.

It can be expedient if the seal is provided in this way is that they are between the end face of the axially extending Thigh of insulation and a shoulder of the outer Bearing ring is jammed.

For fastening the insulation to the bearing that supports it Depending on the choice of material, different processes can be used be beneficial. For example, the insulation on the bearing or sprayed onto the corresponding bearing ring tert or also, if it is insulation rings with is a sleeve-like area, pressed onto the bearing be. Another way between the camp and the apply insulation to the appropriate flywheel, is that the camp is on the appropriate swing mass is pre-assembled by the outer bearing ring in a a larger diameter than the outside diameter of the Bearing ring having recess is added and the Free space between recess and bearing ring with an art is poured out or sprayed out.

For assembly, it can be particularly advantageous if the  Isolation has a sleeve-shaped area that in the the bearing receiving recess of the corresponding swing is pressed in. Depending on the application, it can be appropriate, either first the insulation in the Ausneh and then press in the bearing or the insulation first of all to the warehouse and then, together with this, to press into the recess, previously the Seal was inserted between the bearing and insulation. It can be the sleeve-shaped area of the insulation, which encompasses the bearing - viewed in the axial direction - under have different thickness or diameter ranges, so that only the areas with a larger diameter or greater thickness with an interference fit in the bearing acceptance are included.

The invention will be explained in more detail with reference to FIGS. 1 to 3.

It shows:

Fig. 1 is a sectional torque transmission device according to the invention and

Fig. 2 and 3, other arrangements according to the invention of Vorkeh approximations to reduce the flow of heat between the friction surface and the bearing of a torque transmitting device.

As can be seen from FIG. 1, the device 1 for compensating rotary shocks has a flywheel 2 , which is divided into two flywheels 3 and 4 . The flywheel 3 is on a crankshaft 5 of an internal combustion engine, not shown, screws 6 attached. On the flywheel 4 , a friction clutch 7 is attached via means not shown. Between the pressure plate 8 of the friction clutch 7 and the flywheel 4 , 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 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 4 and thus also the flywheel 2 of the transmission input shaft 10 can be coupled in and out. Damping means in the form of a damping device 13 and a slip clutch 14 connected in series therewith are provided between the flywheel mass 3 and the flywheel mass 4 , which allow a limited relative rotation between the two flywheel masses 3 and 4 .

The two flywheels 3 and 4 are rotatably mounted relative to one another via a bearing 15 . The bearing 15 comprises a roller bearing in the form of a single-row ball bearing 16 . The outer bearing ring 17 of the roller bearing 16 is arranged in a bore 18 of the flywheel 4 and the inner bearing ring 19 of the roller bearing 16 is arranged on a central pin 20 of the flywheel 3 which extends axially away from the crankshaft 5 and projects into the bore 18 .

The inner bearing ring 19 is received with a press fit on the spigot 20 and is axially secured between a shoulder 21 of the pin 20 and the inertial mass 30 and a lock washer 22, the side on the end 20a of the pin 20 by means of screws 23 clamped axially .

Between the outer bearing ring 17 and the flywheel 4, a thermal insulation 24 is provided, which a centrifugal mass 4 interrupts the flow of heat from the clutch disc which interacts with the friction surface 9 4 to the bearing 16 or at least reduced. This prevents ver that a thermal overload of the grease filling of the bearing and an excessive thermal distortion or an inadmissible expansion of the bearing, which may result in jamming of the balls 16 a between the bearing rings 17 and 19 , occurs. To accommodate the insulation 24 , the bore 18 of the flywheel 4 has a larger diameter than the outer diameter of the outer bearing ring 17 , whereby a radial space is formed.

The insulation 24 is formed by two rings 25 , 26 with an L-shaped cross section, which are each applied to the outer bearing ring 17 from one side. The axially facing legs 25 a , 26 a of the cross-sectionally L-shaped insulating rings 25 , 26 overlap or encompass the outer bearing ring 17th The radially inwardly facing legs 25 b , 26 b extend partially radially over the inner bearing ring 19 and are axially supported on it, thereby simultaneously serving as a seal for the bearing 16 . In order to ensure a perfect seal of the bearing 16 , the radially extending legs 25 b , 26 b are acted upon axially in the direction of the end faces of the inner bearing ring 19 by a force accumulator in the form of a plate spring 27 , 28 . The plate spring 27 is supported radially on the outside on a shoulder of a disk 30 which is fixedly connected to the second flywheel 4 by means of bolts 29 and acts radially on the inside of the end regions of the radial leg 25 b of the insulation sealing ring 25 . In a similar manner, the plate spring 28 is supported radially on the outside on a shoulder of the flywheel 4 and acts radially on the inside of the end regions of the radial leg 26 b of the insulating sealing ring 26 .

For the assembly of the rings 25 , 26 and the bearing 16 , it is advantageous in the embodiment according to FIG. 1 if the rings with their sleeve-shaped area are first pressed onto the outer bearing ring 17 and then the bearing 16 with the pressed-on rings 25 , 26 is pressed into the bore or recess 18 of the flywheel 4 . The bearing 16 is axially secured against the flywheel 4 by being axially clamped between a shoulder 31 of the flywheel 4 and the disk 30 with the interposition of the rings 25 , 26 .

The damping device 13 has two disks 30 , 33 which are arranged on both sides of the flange 32 and are connected to one another in a rotationally fixed manner at an axial distance via the spacer bolts 29 . The spacer bolts 29 also serve to fasten the two disks 30 , 33 to the flywheel 4 . In the disks 30 , 33 and in the flange 32 Ausneh measures are introduced, in which energy storage in the form of screw spring 34 are added. These energy stores 34 counteract a relative rotation between the flange 32 and the two disks 30 , 33 .

The damping device 13 further has a friction device 13 a, which sen about the possible angle of rotation between the two Schwungmas 3 and 4 is effective. The friction device 13 a is arranged axially between the disc 30 and the flywheel 3, and has an energy store formed by a plate spring 35, the loading between the ticket 30 and is held clamped at a pressure ring 36, whereby the between the pressure ring 36 and the flywheel 3 arranged Friction ring 37 is clamped. The force exerted by the plate spring 35 on the disk 30 is intercepted via the bearing 16 .

The flange 32 forms on the one hand the input part for the Dämpfungsein device 13 , on the other hand the output part of the slip clutch 14th The input part of this slip clutch 14 is formed by two axially spaced disks 38 , 39 which are non-rotatable with the flywheel 3 . The ring-shaped disk 39 is fastened to the flywheel 3 by means of rivets 40 . The disc 38 has integrally formed axial tabs 38 a , which engage to prevent rotation of the disc 38 relative to the disc 39 in recesses 41 of the disc 39 . Radial arms 42 of the flange 32 are clamped axially between the disks 38 , 39 . For this purpose, the two disks 38 , 39 are clamped together by a plate spring 43 . For this purpose, the plate spring 43 is supported on the one hand on the flywheel 3 and on the other hand strikes the disk 38 in the direction of the disk 39 . In the area between the arms 42 of the flange 32 , recesses are made in the disks 38 , 39 which axially align and accommodate energy stores 44 , which serve as end stops for the arms 42 of the flange 32 and thus limit the angle of rotation of the slip clutch 14 .

In the embodiment shown in FIG. 2, a ball bearing 116 is again used to support the flywheel 4 relative to the flywheel 3 , which is arranged in a manner similar to that of the ball bearing 16 according to FIG. 1. The outer bearing ring 117 of the Kugella gers 116 has chamfers 117 a , 117 b , through which free spaces between the bearing ring 117 and the axially overlapping insulation rings 125 , 126 are formed. Seals in the form of O-rings 145 , 146 are provided in these free spaces. These O-rings 145 , 146 prevent the bearing grease between the L-shaped rings 125 , 126 and the bearing ring 117 from being pressed out or from being able to crawl out. The chamfers 117 a , 117 b and O-rings 145 , 146 are coordinated with one another in such a way that the O-rings are elastically deformed between the rings 125 , 126 with an L-shaped cross section and the chamfers 117 a , 117 b of the bearing 116 .

As can further be seen from FIG. 2, the radial legs 125 b , 126 b of the cross-sectionally L-shaped insulating or sealing rings 125 , 126 compared to the axially extending legs 125 a , 126 a are reduced in thickness. At the radially inner end of the legs 125 b , 126 b , a sealing lug 125 c , 126 c is formed.

In the embodiment shown in FIG. 3, an insulating ring 225 with a conical or conical cross section is arranged between the recess 218 of the flywheel 4 , which receives the bearing 216 , and the outer bearing ring 217 . In the illustrated embodiment, for example, both the outer surface and the inner surface of the insulating ring 225 are conical in the axial direction. However, it would be readily possible to form only one of these surfaces in a conical shape.

The recess 218 is the outer conical surface and the outer surface of the bearing ring 217 is adapted to the inner conical surface of the insulating ring 225 . The insulation ring 225 is acted upon axially in the direction of its tapering by a plate spring 227 , which is supported on the disk 230 , which is axially fixed with respect to the flywheel 4 . The insulation ring 225 has a radially inward region 225 b , which seals the bearing by being axially supported on the bearing inner ring 219 . To seal the bearing on the other side, a ring made of insulating material 226 is provided, which is clamped axially between the outer bearing ring 217 and a shoulder 231 of the flywheel 4 under the effect of the plate spring 227 . The sealing ring 226 has a nose 226 b , which are supported axially on the inner ring 219 .

In the embodiments according to FIGS. 1 and 2 Tellerfe 27 , 28 are provided, the radial sealing areas 25 b , 26 b and 125 b , 126 b axially in the direction of the bearing ring 19 and 119 beat. By suitable selection of materials, the rings 25 , 26 and 125 , 126 could, however, also be designed such that, when these rings 25 , 26 or 125 , 126 are installed, their radial legs 25 b , 26 b or 125 b , 126 b are elastically deformed are, so that they are axially under preload on the bearing ring 19 or 119 . This measure could eliminate the disc springs 27 , 28 .

In the embodiments described so far, the insulation is formed by additional rings which are arranged between the second flywheel 4 and the bearing 16 , 116 , 216 . According to further embodiments of the invention, not shown, the insulation can, however, also be sprayed or sintered onto the bearing 16 , 116 , 216 or onto the bearing ring 17 , 117 , 217 , so that the insulation is then practically integral with the bearing . In a similar manner, the insulation could also be applied to the outer surface of the recess 18 , 118 , 218 .

When using bearings provided with sealing rings, for example, as are offered by the bearing manufacturers, it is also possible to preassemble the bearing 16 on the flywheel 4 by the outer bearing ring 17 having a larger diameter than the outer diameter of the bearing ring 17 18 is inserted and held in the center and the space between recess 18 and bearing ring 17 is poured out or injected with a plastic or synthetic resin.

Claims (15)

1. Torque transmission device with a flywheel be for an internal combustion engine which is divided into two flywheels rotatable via a rolling bearing and counter to the action of a damping device, namely a first flywheel that can be connected to the output shaft of the internal combustion engine and a second friction surface for engaging a clutch disc Flywheel to which a friction clutch coupling and decoupling the second flywheel can be fastened, characterized in that a provision ( 24 ; 125 , 126 ; at least reducing the heat flow from the friction surface ( 4 a ) to the bearing ( 15 ) 225 , 226 ) in the form of an insulation arranged between the friction surface ( 4 a ) and the bearing ( 15 ) and in that an additional seal ( 145 , 146 ) engaging the insulation is provided, the insulation between the support area ( 18 , 118 , 218 ) of the second flywheel ( 4 ) and the position r ( 16 , 116 , 216 ) and the seal ( 145 , 146 ) between the bearing ( 16 , 116 , 216 ) and insulation ( 24 , 125 , 126 , 225 , 226 ) is arranged. 2. Torque transmission device according to claim 1, characterized in that the insulation ( 24 ; 125 , 126 ; 225 , 226 ) is made of plastic. 3. Torque transmission device according to one of claims 1 or 2, wherein one of the flywheels has an axial extension which projects in the axial direction into a central recess of the other flywheel and the bearing is arranged between the extension and recess, characterized in that the insulation ( 24 ; 125 , 126 ; 225 , 226 ) between the central recess ( 18 , 118 , 218 ) and the bearing ( 16 , 116 , 216 ) is arranged. 4. Torque transmission device according to one of the Claims 1 or 2, wherein one of the flywheels has a central, cone-like approach, which in Axis direction in a central recess of the other Flywheel protrudes and between the pin and the recess mung the storage is arranged, characterized in that the isolation between the cone-like approach and the camp is arranged.   5. Torque transmission device according to at least one of the preceding claims, characterized in that the insulation ( 24 ; 125 , 126 ; 225 , 226 ) also serves as a seal for the bearing ( 16 , 116 , 216 ). 6. Torque transmission device according to claim 5, characterized in that the insulation ( 24 ; 125 , 126 ; 225 , 226 ) has a seal ( 25 b , 26 b , 125 b , 126 b , 225 b , 226 b ) for the bearing ( 16 , 116 , 216 ). 7. Torque transmission device according to one of claims 1 to 6, characterized in that the insulation ( 24 ; 125 , 126 ; 225 ) is formed by at least one ring with an L-shaped cross section ( 25 , 26 ), which with one of its legs ( 25 a , 26 a ; 125 a , 126 a ; 225 a ) one of the bearing rings ( 17 , 117 , 217 ) axially covered and encompassed and with the other ( 25 b , 26 b , 125 b , 126 b , 225 b ) of the legs extends radially in the direction of the other bearing ring ( 19 , 119 , 219 ). 8. Torque transmission device according to claim 7, characterized in that the radially extending leg ( 25 b , 26 b , 125 b , 126 b , 225 b ) of the L-shaped insulation ( 24 ; 125 , 126 ; 225 ) at least partially radially over the bearing ring ( 19 , 119 , 219 ) extends, which is not axially covered by the insulation and is axially supported on this ring ( 19 , 119 , 219 ). 9. Torque transmission device according to one of claims 7 or 8, characterized in that the radially extending leg ( 25 b , 26 b , 125 b , 126 b , 225 b ) of the insulating rings ( 25 , 26 ; 125 , 126 , 225 ) axially through an energy accumulator ( 27 , 28 , 227 ) in the direction of the bearing ring ( 19 , 119 , 219 ) is acted upon, which is radially covered by the leg. 10. Torque transmission device according to claim 9, characterized in that the energy accumulator is formed by a plate spring ( 27 , 28 , 227 ). 11. Torque transmission device according to claim 9 or 10, characterized in that the plate spring ( 27 , 28 ) is supported radially outside on the second flywheel ( 4 ) which can be connected to the input part ( 10 ) of a transmission and the end regions of the radial leg ( 25 b , 26 b ) of a sealing ring ( 25 , 26 ) axially loaded. 12. Torque transmission device according to one of claims 1 to 11, characterized in that between the one ( 117 ) of the bearing rings axially overlapping and encompassing leg ( 125 a , 126 a ) of the L-shaped insulation ( 125, 126 ) and this bearing ring ( 117 ) a seal ( 145 , 146 ) is provided. 13. Torque transmission device according to one of the preceding claims, characterized in that the seal is formed by an O-ring ( 145 , 146 ). 14. Torque transmission device according to claim 12 or 13, characterized in that the seal ( 145 , 146 ) on the inner circumferential surface of the axially extending leg ( 125 a , 126 a ) of the insulation ( 125 , 126 ) is supported and in a recess, such as Eg chamfer or groove of the outer bearing ring ( 117 ) is added. 15. Torque transmission device according to claim 13 or 14, characterized in that the seal between the Face of the axially extending leg of the isolator and one shoulder of the outer bearing ring is stuck.