JP2550020B2 - Device for absorbing rotational shock of an internal combustion engine - Google Patents

Description

Description: FIELD OF THE INVENTION The present invention relates to a device for absorbing rotational shock, in particular moment fluctuations, of an internal combustion engine, the device comprising at least two damping elements arranged coaxially with one another. Having flywheel masses which are pivotable relative to each other against the action of the device, one of these flywheel masses being connected to the internal combustion engine and the other of the flywheel masses being able to be connected to the input of the transmission The damping device comprises a circumferentially effective energy store and / or a friction or sliding element, to which at least one second damping device is additionally provided for the flywheel mass. The type provided in the torque transmission path between them.

OBJECT OF THE INVENTION The object of the invention is to improve a device of the above type, in particular with regard to its construction or structure and its wear resistance and function, and to further expand the usable area of said device. Also the cheap manufacture of the device must be guaranteed.

[Means for Solving the Problems] According to the present invention, the above-mentioned problems are solved by the first damping device and the second damping device.
A damping device each having at least two axially spaced discs, each disc group being non-rotatable on the other flywheel mass and between the two disc groups. This has been solved by providing an effective common intermediate flange for transmitting the rotational moment between the first and the second damping device.

Embodiment According to an advantageous embodiment of the invention, the intermediate flange may cover both disc groups in the radial direction, in order to ensure a particularly short structure length in the axial direction. Furthermore, it is advantageous if one disk group is arranged substantially radially inside the other disk group and that the flange radially covers both disk groups.

According to a further advantageous embodiment of the invention, the input of the second damping device consists of a disc group associated with the first flywheel mass, the output of which constitutes the input of the first damping device. It is also configured by an intermediate flange that also configures the first
The output of the damping device in question is constituted by both discs which are connected to a second flywheel mass. In this case, it is particularly advantageous for the two flywheels to be able to pivot relative to each other.
Forming connections may be formed between the intermediate flange and the radially inner disc group and / or between the intermediate flange and the radially outer disc group. Such a form-fitting connection is possible by forming abutment contours on the flange and one or both disc groups and ensuring that the two contours cooperate with each other.

Further in accordance with the invention, the disc group of the first damping device is non-rotatable with the second bounce mass which is connectable to the input part of the transmission and the second damping device is Advantageously, it is non-rotatable with the first flywheel mass associated with it. However, again, the disc group of the first damping device is not rotatable with the first bounce mass and the disc group of the second damping device is not rotatable with the second bounce mass. Good.

Furthermore, in order to ensure a particularly simple construction of the second damping device, the intermediate flange may be axially clamped between the disc groups of the second damping device forming the sliding moment. In this case, depending on the magnitude of the required sliding moment, it is advantageous for the flange and the two discs of the second damping device to come into direct frictional contact. In most applications, however, it is advantageous to provide a friction lining or a sliding lining with at least one flange of the disc of the second damping device, so that a suitable friction for each application is provided. Alternatively, it may be possible to use a sliding lining.

In order to ensure axial clamping of the flanges between the disc groups of the second damping device, advantageously one disc of the second damping device is fixed axially to one of the bouncing masses. It is preferable that the other disc is axially movable with respect to the disc. Further, at this time, it is advantageous that the disc fixed in the axial direction prevents rotation of the other disc. The anti-rotation between both discs of this second damping device is preferably such that one of the discs of the second damping device has an axial projection to prevent rotation, which projection is This is possible by engaging the notch in the other disc. Furthermore, in this case, as a particularly simple structure, the projection is formed by an axially extending tongue portion integrally formed on at least one disc, and the tongue portion is provided on the outer circumference of the other disc. It is advantageous if it projects axially into the cutout provided. Depending on the application, the projection may be provided on the axially fixed disc and / or the axially displaceable disc of the second damping device. Furthermore, the axial projection is the second
It is advantageous if at least one of the discs of the damping device in question is provided on the outer circumference in radial direction, so that the projection axially covers the outside of the intermediate flange. It is also advantageous, according to the invention, to axially fix the second damping device to one of the at least one flywheel masses of the disk by means of rivets.

In order to form a sliding moment between the disc group of the second damping device and the intermediate flange, the axially displaceable disc of the second damping device is preferably axially opposite the other by the energy store. It is good to be loaded toward the disk. Therefore, by properly designing the accumulator, the slipping moment of the second damping device can be varied and adapted to the respective use case. In this case, the accumulator, which loads a disc that is movable in the axial direction, is supported by the flywheel mass body, and it is possible that the disc that is immovable in the axial direction is fixed to this flywheel mass body.

More advantageously, it comprises a disc spring-shaped member of the energy storage device, which disc spring-shaped member has a slit or is open at its outer periphery, the outer periphery of which constitutes this member. It may be surrounded by the shoulders of the supporting flywheel mass. This member, which has slits or is open at the outer circumference, can be manufactured particularly easily by roller processing of the strip. Also, such a disc spring-like member can be easily mounted in a groove or shoulder surrounding it.

Furthermore, according to an advantageous embodiment of the invention, an axial projection provided in at least one of the disks of the second damping device for preventing rotation penetrates the notch of the flange. This notch is preferably arranged on the outer peripheral surface of the flange and is optionally open outwards. In this case, it is particularly advantageous if there is a play between the cutout and the projection which, in the circumferential direction, corresponds to the angle of rotation permitted by the second damping device. Furthermore, the individual axial projections may abut the contours of the flange cutouts in order to limit the pivoting angle of the second damping device. It is also advantageous if the abutment contour for the projection of the at least one disc of the second damping device is formed by a radial overhang which is integrally formed on the outer circumference of the flange. This limits the pivoting angle of the second damping device by abutment of the flange overhang on the axial projection of at least one disc of the second damping device.

According to a further embodiment of the invention, a notch axially aligned with the disc group of the second damping device receives a retractable energy store between the disc and the flange. Is advantageously provided. It is also possible in this case for the power store to be effective in the end range of the pivot angle of the second damping device. Such a power store is advantageously a second
Serves as a stopper body for limiting the rotation angle of the damping device. This prevents, for example, a violent collision between the overhanging portion of the flange and both discs of the second damping device in the end range of the rotation angle of the second damping device, and extends Noise is also avoided. Furthermore, it is advantageous if the energy store is constituted by a coil spring and / or a rubber block. Furthermore, in this case, it is advantageous if the energy storage device is provided between the flange overhangs and is directly loaded by the overhangs.

According to another very inexpensive embodiment of the invention, an effective friction lining between the flange and the at least one disc of the second damping device is provided on the overhang of the flange by means of a friction or sliding member. Advantageously, it is composed of individual segments consisting of It is also more advantageous if the flange is guided concentrically through the at least one flywheel mass.

According to a further advantageous embodiment of the invention, at least one of the bobbin masses has a ring-shaped appendage extending axially towards the other bobbin mass, which is radially inward of this appendix. A second damping device and a first damping device are arranged. It is also advantageous here for the additional part to grip the second damping device in the axial direction, i.e. in many applications, a dish for loading the axially displaceable disc of the second damping device. Advantageously, the spring-like member is supported axially and radially in a groove provided in the open end region of the appendage. However, for another example of use, a second damping device is mounted on the end face of the appendage holding the second damping device axially.
A disk fixed in the axial direction of the damping device is fixed, and a ring-shaped chamber is formed between the flywheel mass body having an additional portion and the disk, and a flange is radially formed in the chamber. It is advisable that the disc that is movable in the axial direction of the second damping device is received in this chamber. In this case, it is advantageous if the first flywheel mass connected to the crankshaft of the internal combustion engine has an additional part. In this configuration, the disc spring-shaped member of the second damping device is further provided as the first member.
Advantageously, there is a contraction between the flywheel mass and the axially displaceable disc of the second damping device.

According to a further embodiment of the invention, an overhang integrally formed on the outer peripheral surface of the flange is radially supported on the axial addition of the mass body for guiding the flange concentrically. Is advantageous. With this configuration,
It is prevented that the function of the first damping device is hindered by external friction. This is particularly advantageous for the range of rotation of the first damping device in which the moment transmitted between the two mass bodies is relatively small. Furthermore, it is advantageous if a friction or sliding lining is provided between the additional part of the corresponding flywheel mass and the flared part of the flange, which serves for radial guidance of the flange. According to an advantageous construction of the device, at least the individual overhangs of the flange are each gripped by a cap made of friction and / or sliding material, which on the one hand guarantees radial guidance of the flange. On the other hand, on the other hand, it may be tightened in order to generate a friction moment between each disc and the flange between the second damping device.
In this case, the cap preferably has an integrally deformable, elastically deformable stop region in the region of one end when viewed in the radial direction, which stop region is pivotable for the second damping device. It may cooperate with a stopper to limit the angle.

According to a further preferred embodiment of the invention, at least the individual overhangs of the flange for centering the flange are--in the circumferential direction--supported by a corresponding axial extension of the flywheel mass. It is gripped by the guide shoe, and the side leg of the U-shaped guide shoe is
Is adapted to cooperate with a stop which limits the rotational play of the damping device. This stop may be, for example, a coupling member extending axially between the two discs, or a storage device or a corresponding addition of a flywheel mass received in the notches of the two discs of the second damping device as described above. It can be formed by the abutment portion arranged at. Furthermore, it is advantageous if there is play in the circumferential direction between the side legs of the U-shaped guide shoe and the flared portion of the flange. Further, a power storage device may be provided between the side leg of the U-shaped guide shoe and the protruding portion of the flange. Such a power storage device is preferably made of an elastic material, for example rubber. This energy store avoids too strong abutments in the end region of the second damping device and thus prevents noise generation.

A stop is provided between the flange and the second bounce mass for limiting the circumferential movement of the first damping device in order to limit the permissible pivoting angle between the two bounce masses. And is advantageous.

At this time, the stopper is also formed by a spacer pin, which connects the discs of the first damping device to each other and to the second bounce mass, so that the flange cutout is axially aligned. It's good to stick. Furthermore, it is advantageous in this case that the pivot angle of the first damping device is limited by the spacer pin abutting against the end region of the cutout of the flange. The structure and arrangement of the notches in the flange are also advantageous in that the flange has radial teeth on its inner circumference, which teeth engage between the spacer pins.

Furthermore, it is preferable that the teeth are formed by forming a notch in a region radially inward of the flange. The spacer pins, which connect both discs of the first damping device, are brought into contact with the teeth of the flange, so that the rotation of the flange with respect to the corresponding flywheel mass is restricted.

According to a further advantageous embodiment of the invention, the disks of the second damping device are axially fixed to one another via spacer members, for example spacer pins, at least one of the disks being the spacer member. There is a circumferentially extending elastically biased corrugation which crimps the flange towards the other disc. With this construction of the second damping device, no special energy store is required for the two discs of the second damping device to be crimped together. Furthermore, it is advantageous in this arrangement that the spacer pins arranged between the two discs of the second damping device simultaneously serve for fixing the discs to one of the bounce masses.

Furthermore, according to the invention, it is advantageous for the disks provided on both sides of the flange of the second damping device to be clamped against the flange by circumferentially distributed U-shaped springs or clamps. In this case, in addition, a U-shaped spring or clamp axially grips the flange and the discs of both the second damping device, the radially extending legs gripping the disc axially from the rear and It is good to load toward the flange. Advantageously, the legs of this U-shaped spring or clamp extend radially inward.

According to a further advantageous embodiment, one of the flywheel masses has an axial projection which engages a notch in a disc of the second damping device which protects the flanks of the flange, Prevents plate rotation. In this case, it is further advantageous that the projection, which is integrally formed on the outer circumference of the flange, is engaged in the radial direction between the projections in the axial direction when viewed in the circumferential direction, and the energy storage device of the second damping device. It is received in a notch in the disc and the energy store is second.
It is preferable that the damping device is used as a terminal stopper of the overhanging portion of the flange in order to limit the rotation angle of the damping device. Further, the notch for receiving the accumulator of one disc is received in the notch of the other disc axially opposed to the notch axially opposed to said notch. Advantageously, the force device is circumferentially offset so that the disc is clamped circumferentially against the projections through the notches in the disc. This avoids noise generation. Further, the axial projection is formed by a bolt or pin, and this bolt or pin is preferably fixed to one of the bobbin mass bodies.

According to a further advantageous embodiment of the invention, the flange has axial notches in the area of the disc of the second damping device, in which notches a friction block or a friction lining is received, This friction block or friction lining is clamped between the discs of the second damping device. In this case, in many applications, the notches penetrate in the axial direction, and a friction block having a thickness larger than the thickness of the flange may be inserted through the notches. Furthermore, it is advantageous if the friction block is axially displaceable in the recess and is guided radially and / or circumferentially.

However, in many applications, a pair of friction blocks arranged one behind the other in axial cutouts are received, between which a force store, for example a disc spring, is provided. It is also advantageous for the force device to clamp the friction block towards the disc of the second damping device. Furthermore, in order to allow a simple assembly of the device, it is advantageous if the friction blocks and the energy stores interposed between them are arranged axially via a coupling element, the coupling element being a force accumulation element. Both friction blocks are allowed to move in the axial direction within a limited range against the action of.

Furthermore, in a structure in which the friction block is arranged in the second damping device, it is more advantageous if the flanges have blind bores for receiving the friction block, the flanges axially facing each other. The intermediate wall between the two facing blind holes has a notch, through which a connecting pin for connecting the axially facing friction block is penetrated, and at least one friction block A force store, for example a disc spring, is arranged between it and the intermediate wall, and the force store clamps the friction block between the discs of the second damping device so that the friction blocks with the coupling members facing each other It is advisable to allow a limited movement in the axial direction against the action of the energy store.

Furthermore, according to an embodiment of the invention, it is advantageous if the first damping device is provided radially inward of the second damping device.

The invention will now be described with reference to the drawings: The device 1 for compensating for rotary impacts shown in FIGS. 1 and 2 has a flywheel 2 divided into two flywheel masses 3,4. . The first flywheel mass 3 is fixed on a crankshaft 5 of an internal combustion engine (not shown) via fixing screws 6. A friction clutch 7 is fixed on the second flywheel mass 4 by means not shown. A clutch disc 9 is provided between the pressure plate 8 of the friction clutch 7 and the flywheel mass 4. The clutch disc 9 is received on an input shaft 10 of a transmission (not shown). The pressure plate 8 of the friction clutch 7 is loaded towards the flywheel mass 4 by a disc spring 12 pivotally supported on the clutch cover 11, by actuating the friction clutch 7, the flywheel mass 4, and thus the flywheel. Two
Is connected to and disconnected from the input shaft 10 of the transmission. A first damping device is provided between the flywheel mass body 3 and the flywheel mass body 4.
13 and a second damping device 14 arranged in series with this damping device 13 are provided. This damping device 14 is a bouncing mass
Allows limited relative rotation between 3,4.

Both flywheel masses 3, 4 are rotatably supported by bearings 15 relative to each other. The bearing 15 is a double row angular contact roller bearing 16 having a divided inner race 17. Outer race 16a of this angular type rolling bearing 16
The divided inner race 17 is arranged in the hole 18 of the flywheel mass 4 and is arranged on a cylindrical pin 19 extending axially from the center of the flywheel mass 3 to the side opposite to the crankshaft 5. .

Both race parts 17a, 17b of the inner race 17 are axially clamped by a force store in the form of a disc spring 20. In order to secure the race portion 17b on the end surface 19a of the pin 19, a securing disc 21 is fixed with a screw 21a. This secure disk 21
Extends radially outward beyond the pin 19 and axially supports the race portion 17b. A disc spring 20 arranged between the race part 17a and the flywheel mass 3 axially loads the race part 17a towards the race part 17b. In this case, the spiral spring 20 is supported by the flywheel mass 3 in the radially outer region, and in the radially inner region, the race portion 17a.
Act on. With such a structure, the rolling elements of the angular rolling bearing 16 are contracted between the rolling paths assigned to the rolling elements. The disc spring 20 produces a force greater than the maximum force required to activate the friction clutch 7 so that the angular roller bearing 16 remains clamped when the friction clutch 7 is activated. Disc spring 20 is advantageous
The force produced by the is selected to be at least approximately twice the maximum force required to disengage the friction clutch 7.

The flywheel mass body 3 has a ring-shaped additional portion 22 in the axial direction on the outer side in the radial direction. This additional part 22 forms a chamber 23,
In this chamber 23 a first damping device 13 and a second damping device 14 are received. The input of the damping device 14 is formed by a disk group, i.e. two masses 24, 25 which are axially spaced from one another and which are non-rotatable with the flywheel mass 3. The ring-shaped disc 25 is fixed to the end surface 22a of the additional portion 22 with a rivet 26 and axially limits the chamber 23 within a range 25a located inside. The disc 24 received in the chamber 23 has an axial projection formed by an integrally molded tongue 24a on the outer periphery. To prevent the disc 24 from rotating with respect to the disc 25, the tongue 24a engages with the notch 27 of the disc 25. The notch 27 and the tongue 24a are configured so that the disc 24 can move in the axial direction with respect to the disc 25. Both discs
A radial overhang 28 of a flange 29 is axially clamped between 24 and 25. For this purpose the disc 24
An accumulator in the form of a disc spring 30 mounted between the and the flywheel mass 3 loads the disc 24 towards the disc 25. For this purpose, the disc spring 30 is supported in the radially outer region by the flywheel mass 3 and in the radially inner region by the disc 24. The outer periphery of the disc spring 30 is open or has a slit. That is, the ring-shaped base body of the disc spring 30 is separated at one location, and the disc spring 30 is radially supported by the ring-shaped shoulder 31 of the bobbin mass 3 at the outer peripheral portion on the radially outer side. Friction linings are provided between the overhang 28 of the flange 29 and both discs 24, 25. The friction lining is composed of individual lining segments 32 adhered to the overhang 28.
Between the overhanging portion 28 of the flange 29, the notches 33, 33
34 is provided, these notches 33, 34 being axially aligned with one another and receiving a power store 35. In the illustrated embodiment, this energy store is formed by a coil spring 35, but it is also possible to use a hard rubber spring. The energy store 35 serves as a limit stop for the overhang 28 of the flange 29 and thereby limits the pivoting angle of the second damping device 14. Due to the damping action of the energy store 35, a hard collision is avoided in the end range of the rotation angle of the damping device 14.

As can be seen especially from FIG. 2 in which the damping device 14 is shown in the intermediate position, there is a play 36+ between the energy store 35 and the overhang 28.
36a is present. This play 36 + 36a is enlarged by the amount by which the energy store 35 is compressed and defines the angle of rotation allowed between the overhang 28 forming the output of the damping device 14 and the disc 24 forming the input. .

The flange 29 forming the output of the damping device 14 simultaneously forms the input of the first damping device 13. The first damping device 13 comprises another disc group, namely two discs 37, 38 arranged on opposite sides of the flange 29. This disk 37,
38 are non-rotatably connected to each other via a spacer pin 39 at an axial distance and are pivotally attached to the flywheel mass body 4. Both discs 37, 38 are surrounded radially outside by ring-shaped discs 24, 25 of the damping device 14. Further, in the illustrated embodiment, the disks 37 and 24 and 38 and 25 are at least approximately coplanar. Discs 37 and 38 and flange
Notches 37a, 38 are formed in the radially inner area of the projecting portion 28 of 29.
A and 29a are provided, and a power store in the form of a coil spring 40 is housed in these notches 37a, 38a, 29a. The energy store 40 acts against relative rotation between the flange 29 and both discs 37, 38.

Furthermore, the first damping device 13 has a friction device 13a which is effective over the total pivoting angle which can be provided between the two mass bodies 3,4.

The friction device 13a is arranged axially between the disk 37 and the flywheel mass 3 and has a force store 41 formed by a disc spring. The force input device 41 is clamped and held between the disc 37 and the pressure ring 42, whereby the friction ring 43 arranged between the pressure ring 42 and the flywheel mass 3 is clamped. The force generated in the disk 37 by the power storage device 41 is received via the bearing 15. The pressure ring 42 is provided with a bulge 42a which grips the head of a spacer pin 39, which is designed as a rivet, by means of which the pressure plate is non-rotatably connected to the flywheel mass 4.

Flange 29 is a notch that opens inward on the radially inner circumference.
44, through which the spacer pin 39 projects in the axial direction. This notch has teeth 45 facing radially inward
To form. This tooth 45-as seen in the circumferential direction-is a spacer pin
39 between the spacer pin 39 and the first damping device.
Cooperate to limit 13 angular displacements.

The cutouts 37a, 38a of both discs 37, 38, the cutout 29a of the flange 29 and the coil spring 40 provided therein form a multistage damping characteristic line over the outer circumference of the first damping device 13. Have dimensions and are arranged such that

Flange 29 with respect to the axis of rotation 47 and bouncing mass 3,
To guide the guides approximately concentrically with respect to 4, the flange 29
Is supported by the radially extending portion 28 on the inner peripheral surface 22b of the axially additional portion 22 of the bobbin body 3.

From the inactive position shown in FIG. 2, the device according to the illustrated embodiment is designed such that, when a change in moment occurs, the first bounce mass 3 first moves together with the disk groups 24, 25 and the flange 29. It is rotated against the action of the spring 40 with respect to the second mass body 4 and the disk groups 37, 38. In this case, the damping action is gradually increased due to the different sizes of the window openings in the flange 29 and the disc groups 37, 38. This relative rotation is carried out until the rotational moment produced by the tightening of the spring 40 reaches a friction moment which can be transmitted by the second damping device 14.
The second damping device begins to slip while the relative movement in this direction progresses. In this case, the spring 35 causes the overhang 28
The flange 29 is not rotated relative to the second bounce mass until it comes into contact with the side surface of the flange. The overhang 28 allows the flange 29 to move relative to the second bounce mass 4 together with the first bounce mass 3. In this case, the spring teeth 45 are compressed until they come into contact with the pin 39.

In particular, as can be seen from FIG. 2, in the embodiment shown, the overhang 28 is arranged such that it extends against a spring 35 in order to limit the maximum pivot angle of the second damping device 14. . However, the tongue portion 24a can be involved in the additional portion by appropriately changing the stopper contour of the overhang portion 28. In such an embodiment, the respective stopper contours of the overhanging portion 28 are such that the energy storage device 35 and the tongue portion 24a--in the circumferential direction--the energy storage device 35 first receives the rotational impact and then the tongue-shaped element. twenty four
Together with a, it must be configured to limit rotation between both discs 24,25 and flange 29. It is also possible to omit the energy store 35 and to engage only the tongue 24a in order to limit the pivoting angle between the input and the output of the second damping device.

In the embodiment shown in FIG. 3, an axially extending tongue is formed on the radially outer side of a disk 125 which is non-rotatably connected to the first bounce mass 103 via a rivet connection 126. It has a shape portion 125a. The tongue 125a extends toward the second bounce mass 104 and engages in a notch 127 in the outer periphery of the disc 124. The notch 127 and the tongue portion 125a are such that the disc 124 is fixed in the circumferential direction with respect to the disc 125,
In the axial direction, however, they are coordinated with one another with the possibility of readjustment. A flange 129 forming the output of the second damping device 114 is fastened between the discs 124 and 125 forming the input of the second damping device 114. A friction lining 132 is arranged between the flange 129 and the discs 124, 125. The flange 129 simultaneously forms the input of the first damping device 113. The output parts of this first damping device 113 are two discs 13 which are non-rotatably connected to one another and to the mass body 104 by means of spacer pins 139.
It is formed by 7,138. The second damping device 114 and the first damping device 113 include the axial addition portion 12 of the flywheel mass body 103.
It is arranged radially inward of the inner peripheral surface of 2. Addition unit 122
A groove 131 is formed at the free end of the
130 is supported radially and axially. The disc spring 130 has a slit in the outer peripheral portion or is opened for better mounting. The disc spring 130 axially loads the disc 124 axially towards the disc 125, whereby the flange 129 is axially clamped between both discs 124, 125 and the friction lining A transmissible sliding moment of the second damping device is defined via the axial force and the friction value between 132 and the flange.

In the embodiment shown in FIG. 4 and FIG. 5, in the second damping device 214, it corresponds between the inner peripheral surface 222b of the additional portion 222 of the bobbin mass 203 in the axial direction and the projecting portion 228 of the flange 229. A friction lining 248 is located. The corresponding friction lining 248 guides the flange 229 concentrically to the flywheel mass 203. The corresponding friction lining 248 forms the bottom of the cap 249 in the illustrated embodiment. This cap 249 is placed on the overhang portion 228 and
I'm holding 228. The lateral extents 250, 251 of the cap 249 are axially clamped between the overhang 228 of the flange 229 and the discs 224, 225 of the second damping device 214 arranged on both sides of the flange 229 to create a friction moment. This axial tightening force is provided by the disc spring 232. The disc spring 232 axially loads the disc 225 and is axially supported by the bobbin mass 203. In order to secure the cap 249 in the radial direction against the action of centrifugal force, the lateral regions 250 and 251 have arcuate protrusions 250a and 251a on the side facing the overhanging portion 228. The raised portions 250a and 251a engage with the corresponding arcuate grooves 252 of the overhanging portion 228. In order to allow the cap 249 to fit over the overhang 228 due to its inherent elasticity-as viewed in the circumferential direction-the ridges 250a, 251a extend over only a portion of the dimension of the overhang 228 or groove 252. Not extended. Areas 253 and 254 viewed in the circumferential direction of the cap 249 form an elastic or cushioning contact area. This contact area cooperates with the flywheel mass 203 and the non-pivotable stop 255 to limit the pivoting angle of the second damping device 214. The stopper 255 is formed by a pin or a bolt. This pin or bolt is fixed to the flywheel mass 203 and is a disc 2 to prevent rotation of the discs 224, 225.
It penetrates 24,225 in the axial direction.

In the embodiment shown in FIG. 6, a U-shaped guide shoe 349 is provided on the overhang 328 of the flange 329 to center the flange 329 with respect to the bounce mass 303. The guide shoe 349 grips the projecting member 328, and the side legs 353, 3 extending in the radial direction of the guide shoe 349.
54 cooperates with the bounce mass 303 and a non-rotatable stopper 355 to limit the pivot angle of the second damping device 314.
As in the embodiment shown in FIGS. 4 and 5, the stopper 355 is fixed to the flywheel mass 303 and the second damping device.
It is formed by a pin or bolt axially passing through a disk of 314, which is arranged on both sides of the flange 329. The area 349a connecting both legs 353 and 354 of the guide shoe 349 is guided between the axial addition 322 of the flywheel mass 303 and the radially outer peripheral surface of the overhang 328. The guide shoe 349 has a larger dimension than the protruding portion 328 when viewed in the circumferential direction. Therefore, on both sides of the overhang 328, there is a play X between the overhang 328 and the side legs 353, 354 of the guide shoe 349. The space formed by the play X is provided with a power storage device in the form of a hard rubber block 357. The hard rubber block 357 damps the impact between the side legs 353, 354 and the stopper 355. The guide shoe 349 can be formed of metal or friction or sliding material.

In FIGS. 7 and 8 both discs 424, 425 are fixedly connected to each other and to the flywheel mass 403 by means of spacer members in the form of spacer pins 455. Between both discs 424, 425 there is a radial overhang of the flange 429.
428 is engaged. In this case, a friction lining 432 is provided between the overhang 428 and both discs 424, 425.

As can be seen from FIG. 8, the disc 425 has corrugated portions 425a extending in the circumferential direction between the fixing holes 455a of the spacer pins 455. The wavy portion 425a is biased with the disk 425 attached, as can be seen in FIG. On the basis of this bias, the flange 429 or its overhanging portion 428 is clamped between the discs 424, 425 and produces a friction moment during relative movement. In order to limit the rotation angle of the second damping device 414, a power storage device 435 is provided in the notches of the disks 424 and 425.
Is provided. The overhanging portion 428 of the flange 429 is brought into contact with the power storage device 435.

In the embodiment shown in FIGS. 9 and 10, the disks 524,5 of the second damping device 514 are provided on both sides of the flange.
25 is clamped to the flange 529 via a friction ring 532 by a circumferentially distributed U-shaped spring or spring clamp 530. A U-shaped spring or spring clamp 530 axially grips the flange 529 and both discs 524, 525 and loads the discs 524, 525 with radially inwardly directed spring legs 530a, 530b. In order to prevent rotation of the discs 524, 525, the flywheel mass 503 is provided with an axial projection in the form of a pin 555. This projection is axially aligned with the corresponding hole 555 in the disc 524, 525.
penetrates a, 555b. The discs 524, 525 are provided with notches 533, 534 for receiving the energy store 535. This accumulator 5
35 cooperates with the overhang 528 of the flange 529 to limit the pivoting angle of the second and damping device 514.

As can be seen from FIG. 10, the notch 533 of the disc 524 is displaced from the notch 534 of the disc 525 by the value Y in the circumferential direction when the discs 524 and 525 are assembled. This causes the force store 535 to be axially contracted between the disks 524, 525 on one side only or asymmetrically. Disks 524 and 525 pass through holes 555a and 555b due to the asymmetric tightening of the energy storage device 535.
The 555 is clamped in the circumferential direction. This tension significantly improves the function of the second damping device 514. Because play with this tension, for example holes 555a in discs 524,525,
Because the play between 555b and pin 555 is compensated, there will always be a damping action during the relative rotation.

In the embodiment of the second damping device 614 shown in FIG. 11, the flange 629 is a disc that forms the input of the second damping device 614.
Blind holes 65 axially aligned with each other in the range between 624,625
It has 6,657. 1 in each of these blind holes 656 and 657
Two disc-shaped friction linings 658,659 are received. The intermediate wall 660 of the flange 629, located between both blind holes 656, 657, has a notch 661, which is rivet 662.
A coupling member in the form of is pierced. This coupling member axially couples axially opposed friction linings 658, 659. Friction lining 658 and intermediate wall 6 viewed axially
A constricted Belleville spring 663 is provided between the two.
The disc spring 663 axially expands or pushes apart both friction linings 658 and 659. This causes the friction linings 658,659 to be pressed against the corresponding discs 624,625 frictionally coupled to them.

Coupling rivets 662 allow both friction linings 658, 659 to be axially displaced to a limited extent from the installed position shown in FIG. Both friction linings 65
The limited axial movement of 8,659 provides wear compensation of the friction linings 658,659 on the one hand and the second damping device 6 on the other hand.
Friction lining 658, with 14 not already installed,
659 and Belleville spring 663 are axially fixed to the flange 629, which considerably simplifies the mounting of the second damping device 614. When assembling the second damping device 614, both friction linings 658 and 659 are axially clamped between both discs 624, 625 against the spring force of the disc spring 663.

Further, as can be seen from FIG. 11, the friction lining 659 is axially supported directly on the intermediate wall 660. On the other hand, there is an axial space between the friction lining 658 and the intermediate wall 660. Therefore, the friction lining 658 is moved axially within the blind hole 656 against the action of the disc spring 663.

[Brief description of drawings]

The drawings show a plurality of embodiments of the invention,
FIG. 2 is a sectional view of the device of the present invention, FIG. 2 is a partial view of the device shown in FIG. 1 as seen from the direction of arrow II, and FIG. 3 is one implementation of a second damping device of the device of the present invention. FIG. 4 is a cross-sectional view of an example, FIG. 4 is a view showing another embodiment of the second damping device of the device of the present invention, FIG. 5 is a cross-sectional view taken along line VV of FIG. 4, and FIG. The figure shows another embodiment of the second damping device of the device of the present invention, and FIGS. 7, 8 and 9 and 10 show the second damping device of the device of the present invention. Another embodiment is shown below.
The figure shows the discs of the disc group of the second damping device in the unassembled state, FIG. 9 is a sectional view taken along the line IX-IX in FIG. 10, and FIG. 11 is the present invention. FIG. 7 shows a modified embodiment of the second damping device of the device. 1 ... A device that absorbs rotational shock, 2 ... Flywheel, 3,4
...... Bounce mass, 5 ...... Crank shaft, 6 ...... Fixing screw, 7 ...... Frictional clutch, 8 ...... Pressure plate, 9 ...... Clutch plate, 10 ...... Input shaft, 11 ...... Clutch cover, 12 ... … Disc springs, 13 …… First damping device, 14 …… Second damping device,
15 …… Bearing, 16 …… Angular type rolling bearing, 17 ……
Inner race, 18 ... hole, 19 ... pin, 20 ... disc spring, 21 ...
… Secure disk, 22 …… Additional part, 23 …… Room, 24,25 …… Disk, 26 …… Rivet, 27 …… Notch, 28 …… Overhanging part,
29 …… flange, 30 …… disc spring, 31 …… shoulder, 32 …… lining segment, 33,34 …… notch, 35 …… accumulator, 3
6 …… Play, 37,38 …… Disc, 39 …… Spacer pin, 40…
… Accumulator, 41 …… Accumulator, 42 …… Pressure ring, 43 …… Friction ring, 44 …… Notch, 45 …… Teeth

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor, Ozwald Alt Friedmann, Reichtenau Mosel Schitraße, Federal Republic of Germany 59 (56) References JP 55-20964 (JP, A) JP 61-6445 (JP, A) JP-A-61-10120 (JP, A) JP-A-56-94049 (JP, A) Actually-laid-open Sho-55-31075 (JP, U)

Claims (75)

(57) [Claims] 1. A device for absorbing rotational shock of an internal combustion engine, comprising at least two flywheel masses arranged coaxially to one another and rotatable relative to one another against the action of a damping device. One of the bounce masses, the first bounce mass is connectable to the internal combustion engine and the other bounce mass is connectable to the input of the transmission, the damping device being effective at least in the circumferential direction. A first type of power storage device and / or a friction or sliding member, in which in addition to this damping device at least one further damping device is provided in the torque transmission path between the two flywheel masses, Damping device (13,113) and another damping device (14,114,214,314,41)
4,514,614) and a disc pair (37 + 38; 137 + 138; 24 + 25; 124 + 125; 224 + 225; 424+, each consisting of at least two discs axially spaced from each other.
425; 524 + 525; 624 + 625), and each disk pair is connected to another bobbin mass body (3,4; 103,104; 203; 303; 403; 503), and the bobbin mass body (3,4; 103,104; 203; 303;
Both disc pairs (37 + 38; 137 + 138; 2 different from 403; 503)
4 + 25; 124 + 125; 224 + 225; 424 + 425; 524 + 525; 624 + 62
5) An integral common intermediate flange (29;
129; 229; 329; 429; 529; 629) is the first damping device (13; 11
3) and a further damping device (14; 114; 214; 314; 414; 514; 614) for transmitting torque, the torque being provided to the first flywheel mass (3; 103; 203; 303; 403; 503) to one disk pair (24 + 25; 124 + 125; 224 + 225; 424 + 425; 52
4 + 525; 624 + 625) and from there another damping device (14; 11
4; 214; 314; 414; 514; 614) through the intermediate flange (29; 12
9; 229; 329; 429; 529; 629) from this intermediate flange (29; 129; 229; 329; 429) to the first damping device (13:11).
2) via another pair of discs (37 + 38; 137 + 138) via 3)
A device for absorbing rotational shock of an internal combustion engine, characterized in that it is adapted to be transmitted to the fly's mass body (4; 104). 2. Another damping device (14,114,214,314,414,514,6)
14. The device according to claim 1, wherein 14) comprises a force store and / or a friction or sliding member which is effective at least in the circumferential direction. 3. Both damping devices (13,113; 14,114,214,314,
Device according to claim 1 or 2, characterized in that 414, 514, 614) are provided in series with one another. 4. Device according to claim 1 or 2, characterized in that both flywheel masses (3,4; 103,104) are supported and centered on one another via rolling bearings (15). . 5. A first mass body (3,103,203,403,50)
3) at least one disc (24,12) of a disc pair combined with
4,224,225,524,525,624), wherein the device is axially movable with respect to the first bounce mass, and the device according to any one of claims 1 to 4. 6. The movable disk (24,124,224,22)
Device according to claim 5, characterized in that 5,524,525,624) is movable against the action of a power store (30,130,232,530,663). 7. A bouncing mass body (3,4,103,104,203,303,403,
Device according to any one of claims 1 to 6, characterized in that 503) is restricted and rotatable relative to one another. 8. An intermediate flange (29,129,229,329,429,529,6
29) is radial and both disc groups (37 + 38,137 + 13)
8; 24 + 25,124 + 125,224 + 225,524 + 525,624 + 625), the device according to any one of claims 1 to 7. 9. One disc groove (37 + 38,137 + 138)
Is almost radial direction and other disk groups (24 + 25,124 + 125,
224 + 225,424 + 425,524 + 525,624 + 625), and the flange (29,129,229,329,429,529,629)
Has both disc groups (37 + 38,137 + 138; 24 + 25,124 +
125, 224 + 225, 424 + 425, 524 + 525; 624 + 625) radially covering the device according to any one of claims 1 to 8. 10. A second damping device (14,114,214,314,414,5).
Disk group (24 + 25,124 + 125,224 + 225,424) whose input part of 14,614) is connected to the first mass body (3,103)
+425,524 +525,624 +625) and the output part is constituted by the intermediate flange (29,129,229,329,429,529,629) which also constitutes the input part of the first damping device (13,113), and the output part of the first damping device is the second Device according to any one of claims 1 to 9, characterized in that it is constituted by both discs (37, 38; 137, 138) which are connected to said bounce mass. 11. An intermediate flange (29,129,229,329,429,52
9,629) and disk group radially inward (37 + 38,137 + 1)
38) and / or intermediate flanges (29,129,229,329,4)
29,529,629) and the radially outer disk group (24 + 25,1)
24 + 125,224 + 225,424 + 425,524 + 525,624 + 625), wherein the connection is made by means of a form connection, the device according to any one of claims 1 to 10. 12. A disk group (37 + 38,137 + 138) of a first damping device (13,113) is a second bounce mass (4,104).
And the second damping device (14,114,214,31
4,414,514,614) disk group (24,25; 124,125; 224,2
25; 424,425; 524,525; 624,625) is non-rotatable with the first bounce mass (3,103,203,303,403,503) and the device according to any one of claims 1 to 11. 13. An intermediate flange (29,129,229,329,429,52
9,629) is the second damping device (14,114,214,314,414,514,61)
4) Disc group (24,25; 124,125; 224,225; 424,425; 5
24,525; 624,625), wherein the device is axially clamped between the devices according to any one of claims 1 to 12. 14. At least a second damping device (14,114,21).
4,314,414,514,614) disk (24,25; 124,125; 224,225; 4
24,425; 524,525; 624,625) and flange (29,129,2)
29.329,429,529,629) with a friction or sliding lining (32,132,249,432,532,658,659). 15. A disk (25,125) of one of the second damping devices (14,114) is axially fixed to one of the bouncing masses (3,4; 103,104) and the other disk (24,124). Device according to any one of claims 1 to 14, characterized in that)) is axially displaceable with respect to the disc (25,125). 16. Device according to claim 15, characterized in that the axially fixed disc (25, 125) prevents rotation of the other disc (24, 124). 17. One of the disks (24,25,124,125) of the second damping device (14,114) has an axial projection (24a; 125a) for preventing rotation, which projection (24a; 125a). ) Is engaged with the notch (27,127) of the other disc (25,124),
The device according to claim 15 or 16. 18. A projection (24a; 25a) is formed by an axially extending tongue (24a, 125a) integrally formed on at least one disc (24,25,124,125), and this tongue is formed. Claims, wherein (24a, 125a) axially projects into a notch (27, 127) provided on the outer circumference of the other disc.
The apparatus according to item 17. 19. The disk according to claim 17, wherein the disk (125) fixed in the axial direction holds the projection (125a).
The apparatus according to item 18. 20. A disk according to claim 17, wherein the disk (24) movable in the axial direction has a projection (24a).
Item. 21. At least one disc (24,25,124,12) of the second damping device (14,114) with axial projections (24a, 125a).
The device according to any one of claims 17 to 20, which is provided on the outer periphery as viewed in the radial direction in 5). 22. A second damping device disc (24, 25, 124, 125,
A rivet (26,126,455) is used to axially secure at least one (25,125,424,425) of (424,425) to one of the bouncing masses (3,4,103,104,403) by means of rivets (26,126,455). Any one up to
Item. 23. The axially movable disc (24,125,225,524,525) of the second damping device (14,114,214,514) is axially displaced by the energy storage device (30,130,232,530) to the other disc (25,12).
Device according to any one of claims 14 to 22 loaded towards 4,224,525,524). 24. A disk (25,12) wherein an energy storage device (30,130) for loading a disk (24,124) movable in the axial direction is immovable in the axial direction.
Device according to any one of claims 21 to 23, which is carried by the fixed flywheel mass (3, 103) of 5). 25. Device according to claim 24, characterized in that the energy store (30, 130) is composed of a disc spring-shaped member. 26. A flywheel mass (3,103) having a disc spring-like member (30,130) having a slit or an opening at the outer circumference thereof, the outer circumference of which (30,130) supports the member (30,130). Surrounded by the shoulders (31,131) of
Device according to claim 25. 27. The axial projection (24a) has a flange (29, 12).
The device according to any one of claims 17 to 26, which penetrates the notch of 9). 28. There is a play between the notch and the projection (24a, 125a), viewed in the circumferential direction, which corresponds to the rotation angle permitted for the second damping device (14, 114). Claim 27th
Item. 29. A second axial projection (24a, 125a) is provided.
29. Device according to claim 27 or 28, which abuts against the contour of the cutout of the flange (29,129) in order to limit the pivoting angle of the damping device (14,114). 30. A flange (29,229,329,429,529) has a radial overhang (28,228,328,428,528) on its outer circumference, and this overhang (28,228,328,428,528) is a damping device (14,214,3).
Device according to any one of claims 1 to 29 for limiting the pivoting angle of 14,414,514). 31. The overhanging portion (28) has at least one axial projection (24a) of the discs (24, 25) of the second damping device (14).
31. Apparatus according to claim 30 which abuts against. 32. A second damping device (14,114,214,414,514)
Disc group (24 + 25,124 + 125,424 + 425,524 + 52
A notch (33,34; 533,534) axially aligned with 5) is provided to receive a retractable energy store (35,435,535) between this disc and the flange (29,129,429,529), Any one of claims 1 to 31
Item. 33. Device according to claim 32, in which the energy store (35,435,535) is effective in the end range of the pivot angle of the second damping device. 34. Device according to claim 32 or claim 33, in which the energy store (35,435,535) serves as a stop for limiting the turning angle of the second damping device. 35. Device according to any one of claims 32 to 34, in which the power store (35,435,535) is constituted by a coil spring. 36. A device according to any one of claims 32 to 34, wherein the power storage device is constituted by a rubber block. 37. A power storage device (35,435,535) is provided with a flange (29,4).
Device according to any one of claims 32 to 36, provided between the overhangs (28,428,528) of (29,529) and loaded by the overhangs (28,428,585). 38. A flange (29) and a second damping device (14).
An effective friction lining with at least one of the circular discs (24,25) of the flange (29) is fixed to the overhang (28) and consists of individual segments of friction or sliding material. An apparatus according to any one of claims 1 to 37. 39. At least one flange (29,229,329).
39. Device according to any one of claims 1 to 38, which is concentrically guided by two flywheel masses. 40. At least one of the bouncing masses (3,103,
203,303,503) and the ring-shaped additional part (22,122,222,322) extending axially toward the other bouncing mass (4,104).
And a second damping device (14, 114, 214, 314, 514, 614) and a first damping device (13, 11) inside the additional portion in the radial direction.
3) and are arranged, claims 1 to 3
The apparatus according to any one of items 9 to 9. 41. Device according to claim 40, characterized in that the additional part (22,122,222,322) axially grips the second damping device (14,114,214,314,514,614). 42. A disc-spring-like member (130) for loading an axially movable disc (124) of the second damping device (114) is provided in the range of the open end of the addition part (122). 42. Device according to claim 41, which is supported axially and radially in a groove (131). 43. A second member is provided on the end surface (22a) of the addition portion (22).
The disc (25) fixed in the axial direction of the damping device (14) is fixed, and the circular disc (25) and the additional portion (22) of the flywheel mass body (3) having the additional portion (22). A ring-shaped chamber (23) is formed between the chamber and the chamber, and a flange (29) projects radially into the chamber (23). 14) A disk that can move in the axial direction (2)
4) is accepted, and claim 40 or 41
Item. 44. A first momentary mass body (3,103,203,303,50)
Device according to any one of claims 40 to 43, wherein 3) has an adder (22,122,222,322). 45. A disk in which a disc spring-shaped member (30) of a second damping device (14) is axially movable between the first bobbin mass body (3) and the second damping device (14). Any one of claims 25 to 44, which is tightened between
Item. 46. An extension portion (28,228,328) of the flange for concentrically guiding the flange (29,229,329) has an axial additional portion (22,222,32) of one of the bounce mass bodies (3,203,303).
2) Radially supported by 2), Claim 1
The apparatus according to any one of paragraphs to 45. 47. A friction or sliding lining (248,349) is provided between the additional portion (222,322) and the overhanging portion (28,228) of the flange (29,229) when viewed in the radial direction. The device according to the item. 48. At least the individual overhangs (228) of the flange (229) are each gripped by a cap (249) of friction and / or sliding material, which cap (249) on the one hand is provided with a flange (228). 229) is secured to ensure radial guidance and, on the other hand, to generate a friction moment between the discs (224, 225) between the second damping devices (214). The apparatus according to paragraph 47. 49. Stopper area (253, 254) in which the cap (249)-as seen in the circumferential direction--is elastically deformable in the end area.
Is integrally molded and has a stopper range (25
The third aspect of the present invention is the third aspect of the present invention, in which the second damping device (214) cooperates with the stopper (255) to limit the turning angle of the second damping device (214).
The device according to item 8. 50. At least an individual overhang (328) of the flange (329) for centering the flange (329).
-When viewed in the circumferential direction-The additional part (32
Device according to any one of claims 1 to 49, which is gripped by a U-shaped guide shoe (349) carried by 2). 51. Side legs (35) of a U-shaped guide shoe (349).
Device according to claim 50, in which 3,354) cooperates with a stop (355) which limits the pivotal play of the second damping device (314). 52. Side legs (35) of a U-shaped guide shoe (349).
Claim 50 or 51, wherein there is a play (X) in the circumferential direction between the projecting portion (328) and the projecting portion (328).
Item. 53. Side legs (35) of a U-shaped guide shoe (349).
53. The device according to any one of claims 50 to 52, wherein a power storage device (357) is provided between the overhanging portion (328) and the overhang portion (328). 54. Device according to claim 53, in which the energy store (357) is made of an elastic material, for example rubber. 55. A stopper (39,139) for restricting circumferential movement of the first damping device (13,113) is provided between the flange (29,129) and the second bounce mass body (4,104). Any one of claims 1 to 54
Item. 56. The stopper is formed by a spacer pin (39,139), and the spacer pin (39,139) is a first pin.
Discs (37, 38; 137, 138) of the damping device (13, 113) of FIG. A device according to claim 55. 57. The spacer pin (39,139) is attached to the flange (2).
57. Device according to claim 56, wherein the pivoting angle of the first damping device (13,113) is limited by abutting the end region of the notch (44) of the (9,129). 58. A method according to claim 55, wherein the flange (29) has radial teeth (45) on its inner circumference, which teeth (45) engage between the spacer pins (39). The device according to any one of paragraphs 57 to 57. 59. Device according to claim 58, in which the tooth (45) is formed by providing a notch (44) in the region radially inward of the flange (29). 60. A flange (29,129,229,329,429,529,62
Device according to any one of claims 1 to 59, characterized in that 9) is pivotable in a restricted manner with respect to the second bounce mass (4, 104). 61. The discs (424, 42) of a second damping device (414).
5) are axially fixed to each other via spacer pin members (455), eg spacer pins, and at least one of the discs (424, 425) (425) extends circumferentially between the spacer members (455). Elastically biased corrugations (425a), which corrugate (425a)
Device according to claim 1, wherein 9) is crimped towards the other disc (424). 62. Spacer pins (455) are discs (424,425)
62. A device according to claim 61 used to secure one to one of the bouncing masses. 63. The flange (5) of the second damping device (514).
29. Discs (524,525) provided on both sides of 29) are clamped against the flange (529) by circumferentially distributed U-shaped springs (530) or clamps. Equipment. 64. A U-shaped spring (530) or clamp axially grips the flange (529) and the discs (524, 525) of both the second damping device (514) and extends radially. 64. Apparatus according to claim 63, wherein the disks (524,525) are axially gripped from behind by (530a, 530b) and are loaded towards the flange (529). 65. One of the flywheel masses (503) has an axial projection (555), which projection (555) protects the side surface of the flange (529) of the second damping device (514). Disc (52
4,525) engaging notches (555a, 555b) and disc (524,52)
5) to prevent rotation, claims 1 to 64
The apparatus according to claim 1. 66. A projecting portion (5) integrally formed on the outer circumference of the flange (529) between the projections (555) in the axial direction when viewed in the circumferential direction.
28) is engaged in the radial direction, and the energy storage device (535) is the second
Attenuator (514) disc (524,525) notch (533,53)
4), the accumulator has a bulge (528) on the flange (529) for limiting the rotation angle of the second damping device.
The device according to claim 65 used as a terminal stopper of a device. 67. A notch (534) in one disc (525) for receiving a power storage device (535) axially faces the notch (534) in the other disc (524). To the notch (533), the power storage device (535) received in the notch (533,534) facing each other in the axial direction makes the disc (524,525) the disc (524,525).
A device according to claim 65 or 66, wherein the device is circumferentially offset so as to be circumferentially clamped against a projection (555) passing through the notches (555a, 555b). 68. Claim 66, in which the axial projection is formed by a bolt (555) or pin, which bolt (555) or pin is fixed to one of the bouncing masses (503). The device according to any one of items 67 to 67. 69. A flange (629) has a second damping device (61).
4) Axial notch (656,65) in the area of the disc (624,625)
7) having and friction blocks in these notches (658,659)
A device according to claim 1, characterized in that the friction block (658,659) is clamped between the discs (624,625) of the second damping device (614). 70. The cutouts (656,657) extend axially through which a friction block (658) having a thickness greater than the thickness of the flange is inserted. Apparatus according to clause 69. 71. Claim 69 or claim 70, wherein the friction block (658) is axially displaceable within the notch (656) and is guided radially and / or circumferentially.
Item. 72. A pair of friction blocks (658,659) arranged one behind the other in axial cutouts (656,657) are received between which a power store, for example a disc spring (663). ) Is provided, and this power storage device is equipped with a friction block (65
Claims 69 to 71, wherein the clamps (8,659) are clamped towards the discs (624,625) of the second damping device (614).
The apparatus according to claim 1. 73. Friction blocks (658, 659) and a power storage device (663) interposed therebetween are grouped in the axial direction via a coupling member (662), but the coupling member (662) stores the force. Both friction blocks (65
A device according to claim 72, which allows the axial movement of (8,659) to a limited extent. 74. A flange (629) has a blind hole (656,657) axially facing each other for receiving a friction block (658,659), the flange (629) having two axially facing one another. The intermediate wall (660) between the blind holes (656,657) has a notch (661). This notch (661)
Friction blocks axially facing through (658,659)
A coupling member (662) that couples with each other penetrates through, and a force accumulator, for example, a disc spring (663) is arranged between at least one friction block (658, 659) and the intermediate wall (660). Device holds the friction block (658,659) between the discs (624,625) of the second damping device (614), and the coupling members (662) face each other (658,659).
Claim 69 and Clause 69, which enable a limited movement in the axial direction against the action of the energy store (663).
The device according to any one of paragraphs 71 to 73. 75. A method according to any one of claims 1 to 74, wherein the first damping device (13,113) is provided radially inward of the second damping device (14,114,214,314,414,514,614). Equipment.