JP3342952B2 - Device for absorbing rotational non-uniformity - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internal combustion engine for transmitting torque between an input shaft of a transmission of a motor vehicle and an internal combustion engine when a friction clutch is closed. The present invention relates to a device for absorbing rotational unevenness provided between an engine and a transmission. [0002] It is an object of the present invention to improve the above-mentioned device to improve its function. SUMMARY OF THE INVENTION An object of the present invention is to provide a device for absorbing rotational non-uniformity, comprising a drive plate and a flywheel which can be connected to a drive shaft, for example, a crankshaft of an internal combustion engine. A flywheel is connectable to an input shaft of a force transmitting device, for example, a transmission, and is disposed coaxially with the drive plate;
The flywheel is rotatably held on a drive plate via a rolling bearing, and a flywheel has a flywheel body extending in a radial direction,
The flywheel body is axially opposed to the drive plate and is disposed substantially parallel to the drive plate, and a spring device, a torque limiting device, and a hysteresis device are disposed between the drive plate and the flywheel. The spring device extends in the circumferential direction between the drive plate and the flywheel, the torque limiting device is adjusted so that slip occurs only when a transiently high torque acts on the torque limit device, and the hysteresis device is driven by the drive plate. A spring device and a torque limiting device are arranged in series with each other and as a vibration damping system between the drive plate and the flywheel, A hysteresis device is effective in parallel with the series connection of the spring device and the torque limiting device, and the hysteresis device has an energy storage device acting in the axial direction of the device. Characterized in that there has been solved by a device for absorbing the rotational non-uniform properties. According to the structure of the present invention, a friction device is provided which generates a frictional force when the driving plate and the flywheel move relative to each other. This friction device is arranged parallel to the spring device and the torque limiting device. Since the torque limiting device slips only in the event of an excess moment, the friction device mainly cooperates only with the spring device, the frictional force of which can be adapted to the conditions that occur during normal operation, i.e., when the slip clutch does not slip. . This frictional force can be defined by a suitable choice of the bias of the energy storage acting in the axial direction of the device. FIG. 1 is a perspective view of an apparatus for compensating for rotational shocks shown in FIGS. 1 and 2; FIG. 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. Pressure plate 8 of friction clutch 7 and flywheel mass 4
Is provided with a clutch disk 9. The clutch disk 9 is received on an input shaft 10 of a transmission (not shown). The pressure plate 8 of the friction clutch 7 is loaded toward the flywheel mass 4 by a disc spring 12 pivotally mounted on the clutch cover 11. 2 is connected and disconnected from the input shaft 10 of the transmission. Between the flywheel mass 3 and the flywheel mass 4 there is provided a first damping device 13 and a second damping device 14 arranged in series with the damping device 13. This damping device 14 allows a limited relative rotation between the flywheel masses 3,4. The two flywheel masses 3, 4 are rotatably supported via bearings 15 relative to one another. Bearing 1
Reference numeral 5 denotes a double-row angular rolling bearing 16 having a divided inner race 17. The outer race 16a of the angular rolling bearing 16 is disposed in the hole 18 of the flywheel mass 4, and the divided inner race 17 is a cylindrical cylinder extending axially from the center of the flywheel mass 3 to the side opposite to the crankshaft 5. Are arranged on the pins 19. [0007] Both race portions 17a of the inner race 17,
17b is axially clamped by a power storage device in the form of a disc spring 20. The race portion 17b is connected to the end face 1 of the pin 19
In order to secure above the 9a, the securing disk 21 is fixed to the screw 21a.
It is fixed at. The securing disk 21 extends radially outward beyond the pin 19 and supports the race portion 17b in the axial direction. A disc spring 20 arranged between the race part 17a and the flywheel mass 3 loads the race part 17a in the axial direction towards the race part 17b. In this case, the flat spring 20 is supported on the fly mass 3 in the radially outer area and the race part 17 in the radially inner area.
Acts on a. With such a structure, the rolling elements of the angular rolling bearing 16 are contracted between the rolling paths assigned thereto. The disc spring 20 produces a force greater than the maximum force required to operate the friction clutch 7 so that when the friction clutch 7 is activated, the angular rolling bearing 16 remains tightened. Advantageously, the force generated by the disc spring 20 is chosen to be at least approximately twice as great as the maximum force required to disengage the friction clutch 7. The flywheel mass 3 has an axially annular additional portion 22 on the radially outer side. This additional part 22 forms a chamber 23 in which the first damping device 13
And a second damping device 14 are received. Damping device 1
The input 4 is formed by a disk group, i.e. two disks 24, 25 which are axially spaced from one another and which are non-rotatable with the flywheel mass 3. The ring-shaped disk 25 is fixed to the end face 22a of the additional portion 22 with a rivet 26 and limits the chamber 23 in the axial direction within a range 25a located inside. The disk 24 received in the chamber 23 has an axial projection formed by a tongue 24a integrally formed on the outer periphery. To prevent the disk 24 from rotating with respect to the disk 25, the tongue 24a engages with the notch 27 of the disk 25. The notch 27 and the tongue 24a are configured so that the disk 24 can move in the axial direction with respect to the disk 25. A radial extension 28 of a flange 29 is axially clamped between the two disks 24 and 25. For this purpose, an energy storage device in the form of a disc spring 30 provided between the disk 24 and the flywheel mass 3 in the axial direction loads the disk 24 towards the disk 25. For this purpose, a disc spring 30
Are supported by the flywheel mass 3 in the radially outer area and by the disk 24 in the radially inner area. The outer periphery of the disc spring 30 is open or has a slit. In other words, the ring-shaped base of the disc spring 30 is cut off at one point, and the disc spring 30 is radially supported by the ring-shaped shoulder 31 of the flywheel mass 3 at the radially outer periphery. A friction lining is provided between the overhang portion 28 of the flange 29 and the two disks 24 and 25, respectively. This friction lining consists of individual lining segments 32 glued to the overhang 28. Between the overhangs 28 of the flange 29, the disks 24, 2
5 are provided with notches 33, 34, and these notches 3
3, 34 are axially aligned with one another and
Has been accepted. In the embodiment shown, this energy storage device is formed by a coil spring 35, but it is also possible to use a hard rubber spring. The energy storage 35 has a flange 29
Serves as a limit stop for the overhang 28 of the second damping device 14, thereby limiting the pivot angle of the second damping device 14. Due to the damping action of the energy storage device 35, a hard collision is avoided in the end range of the rotation angle of the damping device 14. As can be seen particularly from FIG. 2, in which the damping device 14 is shown in an intermediate position, there is a play 36 + 36a between the energy storage 35 and the overhang 28. This play 36
+ 36a is expanded by a value to compress the energy storage 35,
It defines the pivot angle allowed between the overhang 28 forming the output of the damping device 14 and the disk 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 disk group, namely two disks 37, 38 arranged on both sides of the flange 29.
have. These disks 37, 38 are spacer pins 39
Are axially spaced apart from one another and are non-rotatably connected to one another and are pivotally connected to the flywheel mass 4. Both discs 3
7 and 38 are surrounded on the radial outside by the ring-shaped disks 24 and 25 of the damping device 14. Furthermore, in the embodiment shown, disks 37 and 24 and 38 and 25 are arranged at least approximately in the same plane. Notches 37a, 38a and 39a are provided in the radially inner area of the protruding portions 28 of the discs 37 and 38 and the flange 29, and a coil spring 40 is formed in these notches 37a, 38a and 39a. Energy storage device is housed. Energy storage device 40 is flange 2
It acts against the relative rotation between 9 and both discs 37,38. Further, the first damping device 13 includes a friction device 13
a, this friction device 13a is effective over the total pivoting angle that can be provided between the two flywheel masses 3, 4. The friction device 13a is disposed between the disk 37 and the fly mass 3 in the axial direction and has a power storage device 41 formed by a disc spring. This energy storage device 41 is a disk 27
Between the pressure ring 42 and the flywheel mass 3, whereby the friction ring 43 arranged between the pressure ring 42 and the flywheel mass 3 is tightened. The force generated on the disk 37 by the energy storage device 41 is received via the bearing 15. The pressure ring 42 has an overhang 42a, which grips the head of the rivet 39, whereby the pressure plate is non-rotatably connected to the bounce mass 4. The flange 29 has a notch 44 opened inward in the outer peripheral portion on the radially outer side, and the spacer pin 39 protrudes in the axial direction through the notch 44. This notch forms a radially inwardly facing tooth 45. This tooth 45
Seen in the circumferential direction, engages between the spacer pins 39 and cooperates to limit the angular displacement of the spacer pins 39 and the first damping device 13. Notches 37a, 3 of both disks 37, 38
8a, the notch 29a of the flange 29 and the coil spring 40 provided therein have dimensions and are arranged such that a multi-stage damping characteristic line is formed around the outer periphery of the first damping device 13. . To guide the flange 29 substantially concentrically with respect to the axis of rotation 47 and with respect to the flywheel masses 3, 4, the flange 29 is provided with a radial extension 28 in the axial direction of the flywheel mass 3. It is supported by the inner peripheral surface 22b of the additional portion 22. The device of the embodiment shown in the drawing shows that, from the inactive position shown in FIG. 2, when a change in moment occurs, the first flywheel mass 3 first moves together with the disk groups 24, 25 and the flange 29. Second mass 4 and disk group 3
7 and 38 against the action of the spring 40. In this case, the flange 29 and the disk group 37,
Due to the different size of the window openings at 38 and 38, the damping action is gradually increased. This relative rotation is performed until the rotational moment generated by the contraction of the spring 40 reaches the frictional moment that can be transmitted by the second damping device 14. While the relative movement in this direction proceeds, the second damping device starts to slip.
In this case, the relative rotation of the flange 29 with respect to the second fly mass is not performed until the spring 35 contacts the side surface of the overhang portion 28. The overhang portion 28 has a first flange 29.
To move relative to the second flywheel mass 4 together with the flywheel mass 3. In this case, the spring is a tooth 45
Is compressed until it contacts the pin 39. In particular, in the embodiment shown in FIG. 2, the overhang 28 is configured such that the overhang 28 abuts a spring 35 in order to limit the maximum pivoting angle of the second damping device 14. ing. However, by appropriately changing the stopper profile of the overhang 28, the tongue 2
4a can also be involved. In such an embodiment, each stop profile of the overhang 28 is composed of the energy storage 35 and the tongue 2
4a, {accumulated in the circumferential direction} the energy storage 35 first receives the rotational shock and then, together with the tongue 24a, limits the rotation between the two disks 24, 25 and the flange 29. Need to be configured to It is also possible to omit the energy storage 35 and to involve only the tongue 24a in order to limit the pivot angle between the input and the output of the second damping device. In the embodiment shown in FIG. 3, a disk 125, which is non-rotatably connected via a first flywheel mass 103 and a rivet connection 126, is formed radially outward, in the axial direction. It has an extending tongue 125a. The tongue 125a extends toward the second bounce mass 104 and engages within a notch 127 provided on the outer periphery of the disk 124. The notch 127 and the tongue 125 a
Are circumferentially fixed with respect to the disk 125, but are axially matched to one another with the possibility of post-adjustment. Between the disks 124 and 125 forming the input of the second damping device 114, there is a second damping device 1
Flanges 129 forming the fourteen outputs are tightened. One friction lining 132 is arranged between the flange 129 and the disks 124 and 125, respectively.
Flange 129 simultaneously forms the input of first damping device 113. The outputs of this first damping device 113 are connected to each other and to the fly mass 104 via spacer pins 139.
And two disks 137, 138 that are non-rotatably connected. The second damping device 114 and the first damping device 113 are provided in the axial additional portion 1 of the flywheel mass 103.
22 is disposed radially inward of the inner peripheral surface of the inner peripheral surface 22. A groove 131 is formed at the free end of the additional portion 122, and this groove 13
1, a disc spring 130 is supported in the radial direction and the axial direction. The disc spring 130 has a slit in its outer peripheral portion or is opened to improve the mounting state. The disc spring 130 loads the disk 124 axially towards the disk 125 in the radially inner region, whereby the flange 129 is axially clamped between the two disks 124, 125, The transferable sliding moment of the second damping device is defined via the axial force and the friction value between the friction lining 132 and the flange. In the embodiment shown in FIGS. 4 and 5, in the second damping device 214, between the inner peripheral surface 222 b of the axial additional portion 222 of the flywheel mass 203 and the overhang portion 228 of the flange 229. A corresponding friction lining 248 is arranged. The flange 229 is guided concentrically with respect to the flywheel mass 203 by means of this corresponding friction lining 248. The corresponding friction lining 248 forms the bottom of the cap 249 in the embodiment shown. This cap 2
49 is mounted on the overhang portion 228 and
I'm grabbing. Side range 250, 25 of cap 249
1 is an overhang portion 228 of the flange 229 and the flange 229.
Disk 22 of the second damping device 214 arranged on both sides of the
4,225 to produce a frictional moment in the axial direction. This axial tightening force is provided by a disc spring 232. Belleville spring 232 axially loads disk 225 and is axially supported by fly mass 203. To secure the cap 249 in the radial direction against the action of the centrifugal force, the side regions 250 and 251 are
On the side facing 28, there are arc-shaped raised portions 250a and 251a. The raised portions 250 a and 251 a engage with corresponding arc-shaped grooves 252 of the overhang portion 228. In order to allow the cap 249 to be fitted over the overhang 228 based on its inherent elasticity, {when viewed in the circumferential direction}, the raised portions 250a, 251a are formed by the overhang 228 or the groove 25.
It extends only over a part of the two dimensions. The 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 bounce mass 203 and the non-rotatable stop 255 to limit the rotation angle of the second damping device 214. The stopper 255 is formed by a pin or a bolt. The pin or bolt is secured to the fly mass 203 and passes axially through the disks 224, 225 to prevent rotation of the disks 224, 225. 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 relative to the fly mass 303. This guide shoe 3
49 holds the overhang member 328, and
9, the radially extending side legs 353, 354 are used to limit the pivot angle of the second damping device 314.
3 and cooperate with a stopper 355 which cannot rotate. 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 31
4 are formed by pins or bolts which penetrate axially through the disks arranged on both sides of the flange 329. The area 349a connecting the two legs 353 and 354 of the guide shoe 349 is the additional part 3 in the axial direction of the fly mass 303.
22 and the outer peripheral surface of the overhang portion 328 in the radial direction. The guide shoe 349 has a larger dimension than the overhang 328 when viewed in the circumferential direction. Therefore, on both sides of the overhang portion 328, the overhang portion 328 and the guide shoe 349 are provided.
A play X exists between the side legs 353 and 354 of FIG.
A hard rubber block 3 is provided in the space formed by the play X.
A power storage device in the form of 57 is provided. The hard rubber block 357 includes side legs 353, 354 and a stopper 355.
Attenuate the impact between The guide shoe 349 can be formed from metal or a friction or slip material. 7 and 8, both discs 424,
425 are fixedly connected to each other and to the bounce mass 403 by spacer members in the form of spacer pins 455. A radial projection 428 of the flange 429 is engaged between the two disks 424 and 425. In this case, the overhang 428 and both disks 424, 425
Is provided with a friction lining 432. As can be seen from FIG. 8, the disk 425 has a wavy portion 425a extending in the circumferential direction between the fixing holes 455a of the spacer pins 455. This wavy portion 425a is shown in FIG.
As can be seen, a bias is applied with disk 425 attached. Based on this bias, the flange 42
9 or its overhang 428 is tightened between the disks 424, 425 and creates a frictional moment upon relative movement. In order to limit the rotation angle of the second damping device 414, the energy storage device 435 is provided in the notch of the disks 424 and 425.
Is provided. This energy storage device 435 has a flange 429
Overhang 428 is brought into contact. In the embodiment shown in FIGS. 9 to 11, the disks 524, 525 on both sides of the flange of the second damping device 514 are provided with circumferentially distributed U-shaped springs or springs. Flange 52 by clamp 530
9 through a friction ring 532. A U-shaped spring or spring clamp 530 grips the flange 529 and both disks 524, 525 axially and uses radially inwardly directed spring legs 530a, 530b to effect the disks 524,5.
Load 25. In order to prevent the rotation of the disks 524, 525, the bounce mass 503 is provided with an axial projection in the form of a pin 555. This projection is formed in a disc 52
4,525 corresponding holes 555a, 555b. Disks 524 and 525 are provided with notches 533 and 534 for receiving energy storage device 535. This energy storage 535 cooperates with the overhang 528 of the flange 529 to limit the rotation angle of the second damping device 514. As can be seen from FIG. 10, the disks 524, 52
In the state in which 5 is assembled, the notch 533 of the disk 524 is shifted by a value Y in the circumferential direction with respect to the notch 534 of the disk 525. This causes the energy storage device 535 to turn the disk 524,
Between 525, it is axially constricted on one side only or asymmetrically. The disks 524, 525 are circumferentially tightened against the pin 555 passing through the holes 555a, 555b by the asymmetric contraction of the energy storage device 535. This tensioning significantly improves the function of the second damping device 514. Because playing with this tension, for example the disc 52
This is because the play between the holes 555a and 555b of the 4,525 and the pin 555 is compensated, so that there is always a damping action during relative rotation. In the embodiment of the second damping device 614 shown in FIG. 11, the flange 629 is axially aligned with one another in the area between the disks 624, 625 forming the input of the second damping device 614. The bag holes 656 and 657 are provided.
One disk-shaped friction lining 658, 659 is received in each of the blind holes 656, 657. The intermediate wall 660 of the flange 629 between the blind holes 656 and 657 has a notch 661 through which a connecting member in the form of a rivet 662 extends. This coupling member is composed of axially opposed friction linings 65.
8,659 are connected in the axial direction. A contracted disc spring 663 is provided between the friction lining 658 and the intermediate wall 660 when viewed in the axial direction. The disc spring 663 causes the two friction linings 658 and 659 to axially expand or push apart. As a result, the friction linings 658, 659 are pressed against the corresponding disks 624, 625 which are frictionally connected thereto. The coupling rivets 662 allow both friction linings 658, 659 to be moved axially to a limited extent from the installed position shown in FIG. The limited axial movement of both friction linings 658, 659 on the one hand compensates for the wear of the friction linings 658, 659, and on the other hand the friction linings 658, 659 without the second damping device 614 already attached. And the disc spring 663 are axially fixed to the flange 629, which greatly simplifies the mounting of the second damping device 614. When assembling the second damping device 614, both friction linings 658 and 659 are axially tightened between both disks 624, 625 against the spring force of the disc spring 663. Further, as can be seen from FIG. 11, the friction lining 659 is supported directly on the intermediate wall 660 in the axial direction. On the other hand, the friction lining 658 and the intermediate wall 66
There is a space in the axial direction between zero. Accordingly, the friction lining 658 is moved axially in the blind hole 656 against the action of the disc spring 663.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view of the device of the present invention. FIG. 2 is a partial view of the device shown in FIG. 1 as viewed in the direction of arrow II. FIG. 3 is a cross-sectional view of one embodiment of a second damping device of the device of the present invention. FIG. 4 shows another embodiment of the second damping device of the device of the present invention. FIG. 5 is a sectional view taken along the line VV of FIG. 4; FIG. 6 shows a further embodiment of the second damping device of the device according to the invention. FIG. 7 shows another embodiment of the second damping device of the device according to the invention. FIG. 8 shows the disks of the disk group of the second damping device of FIG. 7 in an unassembled state. FIG. 9 is a sectional view taken along the line IX-IX of FIG. 10; FIG. 10 shows another embodiment of the second damping device of the device of the present invention. FIG. 11 shows a variant embodiment of the second damping device of the device according to the invention. [Explanation of Signs] 1 Device for absorbing rotational shock, 2 Flywheel, 3,
4 Moment mass, 5 crankshaft, 6 Fixing screw,
7 friction clutch, 8 pressure plate, 9 clutch plate,
Reference Signs List 10 input shaft, 11 clutch cover, 12 disc spring, 13 first damping device, 14 second damping device, 15 bearing, 16 angular rolling bearing, 17 inner race, 18 holes, 19 pins,
20 disc springs, 21 securing disk, 22 additional parts, 2
3 rooms, 24,25 disks, 26 rivets, 2
7 Notch, 28 overhang, 29 flange, 3
0 disc spring, 31 shoulder, 32 lining segment, 33,34 notch, 35 energy storage, 36 play, 37,38 disk, 39 spacer pin, 4
0 energy storage, 41 energy storage, 42 pressure ring,
43 Friction ring, 44 Notch, 45 teeth

Continued on the front page (72) Inventor Paul Maucher, Saas-Bascha am Bungelt, Germany 23 (72) Inventor, Osuvald Friedman, Germany Lichtenau Moses Rustrasse 59 (56) References JP-A-55-20964 (JP, A) JP-A 54-7008 (JP, A) JP-A 50-25907 (JP, A) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16F 15/131, 15/123 F16F 15/129

Claims (1)

(57) [Claims] A device for absorbing rotational non-uniformity, comprising a drive plate (3) connectable to a drive shaft, for example a crankshaft (5) of an internal combustion engine, and a flywheel (4), the flywheel (4).
Can be coupled to an input shaft (10) of a force transmission device, for example, a transmission, and is disposed coaxially with the drive plate (3);
The flywheel (4) is rotatably held on the drive plate (3) via a rolling bearing (16), and the flywheel (4) has a flywheel body extending in the radial direction. 3) and arranged substantially parallel to the drive plate (3), the spring device (13), the torque limiting device (14), and the hysteresis device (13a) include the drive plate (3) and the flywheel. (4), a spring device (13) extends in a circumferential direction between the drive plate (3) and the flywheel (4), and the torque limiting device (14) is provided with the torque limiting device (14). ) Is adjusted so that slip occurs only in the event of a transiently high torque applied, so that the hysteresis device (13a) generates frictional forces during the relative movement between the drive plate (3) and the flywheel (4). Provided in the spring device 13) and a torque limiting device (14) are arranged in series with each other and as a vibration damping system between the drive plate (3) and the flywheel (4), and the hysteresis device (13a) is connected to the spring device (13). Torque limiter (1
Characterized in that the hysteresis device (13a) has a power storage device (41) acting in the axial direction of the device, which is effective in parallel with the series connection with 4). A device for absorbing speed. 2. The energy storage device (41) is formed by a disc spring;
The device according to claim 1. 3. Hysteresis device (13a) is friction ring (43)
The device of claim 1, comprising: 4. 4. The device according to claim 3, wherein a pressure ring (42) is provided in the axial direction between the friction ring (43) and the energy storage device (41). 5. The flywheel (4) has a ring-shaped component (37), and a hysteresis device (13a) is disposed axially between the ring-shaped component (37) and the drive plate (4), The device according to claim 1. 6. 2. The device according to claim 1, wherein the drive plate (3) has an axial extension (19) and the hysteresis device (13a) is arranged on (or around) the extension (19). 7. 2. The device according to claim 1, wherein the drive plate (3) has an axial extension (19), on which the rolling bearing (16) is received. 8. 2. The device according to claim 1, wherein the hysteresis device (13a) is arranged in a radially extending area of the rolling bearing (16) and the drive plate (3) when viewed in the axial direction of the device.