JPH0754923A - Absorbing device for rotational shock of internal combustion engine - Google Patents

Abstract

PURPOSE: To enlarge the serviceable range of a device with a simple and inexpensive construction by connecting a rotatable flange to a plurality of flywheel mass bodies via a damping device and by concentrically guiding the flange to one flywheel mass body by a radially outside part. CONSTITUTION: This device 1 has a flywheel 2, divided into a plurality of flywheel mass bodies 3, 4. One flywheel mass body 3 is secured on the crankshaft 5 of an internal combustion engine by a screw 6, a friction clutch 7 is secured on the other flywheel mass body 4, and also a clutch circular plate 9 is arranged therebetween. The pressure plate 8 of the friction clutch 7 is energized toward the other flywheel mass body 4 by a conical spring 12 pivoted by a clutch cover 11. A plurality of damping devices 13, 14 arranged in series is arranged between both the flywheel mass bodies 3, 4. A radial projection 28 on the flange 29 is fastened between a plurality of circular plates 24, 25 constituting the input part of one flywheel mass body 3.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a device for absorbing the rotational shock of an internal combustion engine, which is rotatable relative to the action of at least two coaxially arranged damping devices. A force store having a flywheel mass, one of these flywheel masses being connected to the internal combustion engine and the other flywheel mass being connectable to the input of the transmission, the damping device being circumferentially effective. And / or of the type having friction or sliding members.

[0002]

SUMMARY OF THE INVENTION The object of the invention is to improve a device of the above-mentioned type, in particular with regard to its structure and wear resistance and function, and to expand the usable area of the device. Furthermore, it should be ensured by the invention that the device is inexpensive to manufacture.

[0003]

An object of the present invention is to provide an intermediate part which is rotatable with respect to both bounce masses, said intermediate part being connected to each of the bounce masses via a damping device. And the intermediate part is guided concentrically to one of the baffle masses via its radially outer extent.

[0004]

The centering of the intermediate part through its radially outer extent avoids that the functioning of the first damping device is disturbed by the friction of the other components. This is particularly advantageous for a damper pivot range in which the torque transmitted between the two mass bodies is relatively small. In this way, it can be ensured that only the friction damping action assigned to the first damping device whose frictional force or frictional moment can be set in a targeted manner is effective.

[0005]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT The device 1 for compensating for rotary shocks shown in FIGS. 1 and 2 comprises 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. Friction clutch 7 pressure plate 8 and bouncing mass 4
A clutch disk 9 is provided between and. This 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 directed 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. 2 is connected to and disconnected from the input shaft 10 of the transmission. A first damping device 13 and a second damping device 14 arranged in series with the damping device 13 are provided between the bounce mass body 3 and the bounce mass body 4. This damping device 14 allows a limited relative rotation with the flywheel masses 3, 4.

Both flywheel masses 3, 4 are rotatably supported by bearings 15 relative to each other. Bearing 1
Reference numeral 5 denotes a double-row angular roller bearing 16 having a divided inner race 17. The outer race 16a of the angular roller bearing 16 is arranged in the hole 18 of the flywheel mass body 4, and the divided inner race 17 is a cylindrical shape extending axially from the center of the flywheel mass body 3 to the opposite side of the crankshaft 5. It is arranged on the pin 19 of the.

Both race portions 17a of the inner race 17,
17b is axially clamped by a force store in the form of a disc spring 20. Connect the race part 17b to the end face 1 of the pin 19.
In order to secure on top of 9a, the securing disc 21 has a screw 21a.
It is fixed at. The securing disc 21 extends radially outward beyond the pin 19 and supports the race portion 17b in the axial direction. The disc spring 20 arranged between the race portion 17a and the flywheel mass 3 axially loads the race portion 17a toward the race portion 17b. In this case, the counterspring 20 is supported on the flywheel mass 3 in the radially outer region and in the radially inner region by the race part 17.
acts on a. With such a structure, the rolling elements of the angular type rolling bearing 16 are compressed between the rolling paths assigned to the rolling elements. The disc spring 20 exerts a force greater than the maximum force required to operate the friction clutch 7 so that the angular rolling bearing 16 remains clamped when the friction clutch 7 is operated. Advantageously, the force produced by the disc spring 20 is chosen 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 which the first damping device 13
And a second damping device 14 are received. Damping device 1
The input part of 4 is formed by a disk group, i.e. two mass disks 24, 25 which are non-rotatable with the flywheel mass body 3 and axially spaced from each other. The ring-shaped disc 25 is fixed to the end surface 22a of the additional portion 22 by the rivet 26 and limits the chamber 23 in the axial direction within the range 25a located inside. The disc 24 received in the chamber 23 has an axial projection formed by an integrally formed tongue 24a on the outer periphery. To prevent the disc 24 from rotating with respect to the disc 25, the tongue 24a engages a notch 27 in the disc 25. The notch 27 and the tongue portion 24a are configured so that the disc 24 can move in the axial direction with respect to the disc 25. A radial overhang 28 of a flange 29 is axially clamped between the two discs 24 and 25. For this purpose, an accumulator in the form of a disc spring 30 provided axially between the disc 24 and the flywheel mass 3 loads the disc 24 towards the disc 25. For this, the disc spring 30
Are supported by the flywheel mass 3 in the radially outer region and by the disc 24 in the radially inner region. 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 place, and the disc spring 30 is supported by the ring-shaped shoulder 31 of the bobbin mass 3 in the radial direction at the outer peripheral portion on the radially outer side. Friction linings are provided between the overhanging portion 28 of the flange 29 and both discs 24, 25. The friction lining comprises individual lining segments 32 bonded to the overhang 28. Between the overhanging portion 28 of the flange 29, the discs 24, 2
5 is provided with notches 33 and 34, and these notches 3
3, 34 are axially aligned with each other and store 35
Accepts. 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 power storage device 35 has a flange 29.
Serves as a limit stop for the overhang 28, which 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 turning 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 + 36a between the energy store 35 and the overhang 28. This play 36
+ 36a is expanded by a value by which the power storage device 35 is compressed,
The rotation angle allowed between the overhanging portion 28 forming the output portion of the damping device 14 and the disc 24 forming the input portion is defined.

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 either side of the flange 29.
have. The circular plates 37 and 38 are spacer pins 39.
Are non-rotatably connected to each other at an axial distance and are pivotally attached to the flywheel mass 4. Both discs 3
7, 38 are surrounded radially outside by ring-shaped disks 24, 25 of the damping device 14. Furthermore, in the illustrated embodiment, the disks 37 and 24 and 38 and 25 are at least approximately coplanar. Notches 37a, 38a and 39a are provided in a region radially inside the overhanging portion 28 of the disks 37 and 38 and the flange 29, and the shape of the coil spring 40 is formed in these notches 37a, 38a and 39a. The stored energy storage device is housed. Accumulator 40 is flange 2
It acts against the relative rotation between 9 and both discs 37, 38.

Further, the first damping device 13 is a friction device 13.
The friction device 13a has a and is effective over the total pivoting angle that can be provided between the two flywheel masses 3,4.

The friction device 13a is arranged axially between the disk 37 and the bobbin mass 3 and has a power store 41 formed by a disc spring. This accumulator 41 is a disc 27
Is held tightly between the pressure ring 42 and the pressure ring 42, whereby the friction ring 43 arranged between the pressure ring 42 and the flywheel mass 3 is tightened. 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 an overhang 42a which grips the head of the rivet 39, whereby the pressure plate is non-rotatably connected to the flywheel mass 4.

The flange 29 has a notch 44 opened inward on the outer peripheral portion on the outer side in the radial direction, and a spacer pin 39 projects axially through the notch 44. This notch forms a tooth 45 facing radially inward. This tooth 45 is
Seen in the circumferential direction--engage between the spacer pins 39 and cooperate to limit the angular displacement of this spacer pin 39 and the first damping device 13.

Notches 37a, 3 in both discs 37, 38
8a, the notch 29a of the flange 29, and the coil spring 40 provided therein are dimensioned and arranged so that a multistage damping characteristic line is formed over the outer periphery of the first damping device 13. .

In order to guide the flange 29 about the axis of rotation 47 and substantially concentrically to the flywheel masses 3, 4, the flange 29 is provided with a radial overhang 28 in the axial direction of the flywheel mass 3. The additional portion 22 is supported by the inner peripheral surface 22b.

From the inactive position shown in FIG. 2, the device according to the illustrated embodiment is designed such that, when a change in the moment occurs, the first bounce mass 3 together with the disk groups 24, 25 and the flange 29 is arranged. 2nd momentum mass 4 and disk group 3
7 and 38 are rotated against the action of the spring 40. In this case, the flange 29 and the disk group 37,
The damping action is gradually increased due to the different sizes of the window openings at 38 and. This relative rotation is carried out until the rotational moment generated by the contraction of the spring 40 reaches the friction moment transmittable 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 relative rotation of the flange 29 with respect to the second bounce mass is not performed until the spring 35 contacts the side surface of the overhanging portion 28. The flange 29 is first in the overhanging portion 28.
Permitting relative movement with the second mass body 4 together with the second mass body 3. In this case the spring has teeth 45
Is compressed until it contacts pin 39.

In the embodiment shown, in particular as can be seen from FIG. 2, the overhang 28 is arranged such that the overhang 28 bears against a spring 35 in order to limit the maximum pivot angle of the second damping device 14. ing. However, by appropriately changing the stopper contour of the overhanging portion 28, the tongue-like portion 2 is added to the additional portion.
4a can also be involved. In such an embodiment, the respective stopper contours of the overhanging portion 28 are defined by the energy storage device 35 and the tongue portion 2.
4a, viewed in the circumferential direction, the energy store 35 first receives the rotational shock and then limits the rotation between the two disks 24, 25 and the flange 29 together with the tongue 24a. Need to be configured. It is also possible to omit the energy store 35 and to engage only the tongue 24a in order to limit the angle of rotation between the input and the output of the second damping device.

In the embodiment shown in FIG. 3, a disc 125, which is non-rotatably connected to the first baffle mass 103 via a rivet connection 126, is formed radially outward, in the axial direction. It has an extending tongue portion 125a. The tongue 125 a extends toward the second bounce mass 104 and engages in a notch 127 provided in the outer periphery of the disc 124. The notch 127 and the tongue portion 125a are formed by the disc 124.
Are circumferentially fixed with respect to the disc 125, but are axially aligned with each other for the possibility of readjustment. Between the discs 124 and 125 forming the input of the second damping device 114, the second damping device 1
A flange 129 forming the fourteen outputs is tightened. 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 outputs of this first damping device 113 are connected to each other via the spacer pin 139 and the proof mass 104.
Is formed by two discs 137 and 138 that are non-rotatably connected. The second damping device 114 and the first damping device 113 include the axial addition portion 1 of the flywheel mass body 103.
The inner peripheral surface of 22 is arranged radially inward. A groove 131 is formed at the free end of the additional portion 122.
1, a disc spring 130 is supported in the radial direction and the axial direction. 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 disk 124 axially towards the disk 125, whereby the flange 129 is axially clamped between both disks 124, 125, The transmissible 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 222b of the additional portion 222 of the bobbin mass 203 in the axial direction and the overhanging portion 228 of the flange 229. A corresponding friction lining 248 is arranged. This 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 2
49 is placed on the overhanging portion 228 and
Grabbed. Lateral range 250, 25 of the cap 249
Reference numeral 1 denotes a projecting portion 228 of the flange 229 and the flange 229.
The discs 22 of the second damping device 214 arranged on both sides of the
4, 225 is axially tightened to generate 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 ranges 250 and 251 are provided in the overhanging portion 2.
On the side facing 28, arc-shaped raised portions 250a and 251a are provided. The raised portions 250 a and 251 a engage with the corresponding arcuate grooves 252 of the overhanging portion 228. In order to enable the cap 249 to be fitted over the overhanging portion 228 based on its inherent elasticity, the ridges 250a and 251a are formed on the overhanging portion 228 or the groove 25 when viewed in the circumferential direction.
It only extends over a portion of the two dimensions. 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 secured to the flywheel mass 203 and axially penetrates the discs 224, 225 to prevent rotation of the discs 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 with respect to the bounce mass 303. This guide shoe 3
49 grips the overhanging member 328, and the guide shoe 34
Radially extending side legs 353, 354 of the flywheel mass 30 for limiting the pivoting angle of the second damping device 314.
3 and a stopper 355 that 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 that axially penetrate the discs arranged on both sides of the flange 329. A range 349a connecting both legs 353 and 354 of the guide shoe 349 is provided with an axial additional portion 3 of the flywheel mass 303.
22 is guided between the outer peripheral surface of the overhanging portion 328 in the radial direction. The guide shoe 349 has a size larger than the protruding portion 328 when viewed in the circumferential direction. Therefore, on both sides of the overhanging portion 328, the overhanging portion 328 and the guide shoe 349 are
Play X exists between the side legs 353 and 354 of the.
Hard rubber block 3 in the space formed by play X
An accumulator in the form of 57 is provided. The hard rubber block 357 includes side legs 353, 354 and a stopper 355.
Attenuates the shock between and. The guide shoe 349 can be formed of metal or a friction or sliding material.

In FIGS. 7 and 8 both discs 424,
425 are fixedly connected to each other and to the bouncing mass 403 by spacer members in the form of spacer pins 455. A radial overhang 428 of the flange 429 engages between the two disks 424, 425. In this case the overhang 428 and both discs 424, 425
A friction lining 432 is provided between and.

As can be seen from FIG. 8, the disc 425 has a corrugated portion 425a extending in the circumferential direction between the fixing holes 455a of the spacer pin 455. This wavy portion 425a is shown in FIG.
As can be seen, it is biased with the disc 425 attached. Based on this bias, the flange 42
9 or its overhang 428 is clamped between the discs 424 and 425 and produces a friction moment during relative movement. In order to limit the turning angle of the second damping device 414, the energy storage device 435 is provided in the notches of the disks 424 and 425.
Is provided. This power storage device 435 has a flange 429
The overhanging portion 428 of the contact.

In the embodiment shown in FIGS. 9-11, the disks 524, 525 of the second damping device 514 on either side of the flange are U-shaped springs or springs distributed circumferentially. Flange 52 by clamp 530
9 via a friction ring 532. A U-shaped spring or spring clamp 530 axially grips the flange 529 and both discs 524, 525, with the discs 524, 5 with radially oriented spring legs 530a, 530b.
Load 25. 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 protrusion is a disc 52 in the axial direction.
The corresponding holes 555a and 555b of 4,525 are penetrated. The discs 524 and 525 are provided with notches 533 and 534 for receiving the energy storage device 535. This energy store 535 cooperates with the overhang 528 of the flange 529 to limit the pivoting angle of the second damping device 514.

As can be seen from FIG. 10, the discs 524, 52
The cutout 533 of the disc 524 is displaced from the cutout 534 of the disc 525 by the value Y in the circumferential direction in the assembled state. As a result, the power storage device 535 has the disk 524,
Axial constriction on one side or asymmetrically between 525. Due to the asymmetrical tightening of the force store 535, the disks 524, 525 are circumferentially tightened against the pin 555 which passes through the holes 555a, 555b. This tensioning significantly improves the function of the second damping device 514. Because play with this tension, for example disc 52
This is because the play between the holes 555a and 555b of 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 flanges 629 are axially aligned with each other in the area between the disks 624, 625 forming the input of the second damping device 614. Has hollow holes 656 and 657.
Disc-shaped friction linings 658 and 659 are received in the blind holes 656 and 657, respectively. The intermediate wall 660 of the flange 629, which is located between the two blind holes 656, 657, has a notch 661, through which a coupling member in the form of a rivet 662 passes. This coupling member has friction linings 65 facing each other in the axial direction.
8, 659 are connected in the axial direction. A constricted 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 axially expands or pushes apart both friction linings 658 and 659. This causes the friction linings 658, 659 to press against the corresponding discs 624, 625 frictionally coupled thereto.

Coupling rivets 662 allow for limited axial movement of both friction linings 658, 659 from the installed position shown in FIG. The limited axial movement of both friction linings 658, 659 provides wear compensation of the friction linings 658, 659 on the one hand and friction linings 658, 659 on the other hand with the second damping device 614 not yet installed. And a disc spring 663 is 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 and 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. In contrast, the friction lining 658 and the intermediate wall 66
An axial space exists between 0 and 0. Therefore, the friction lining 658 is axially moved within the blind hole 656 against the action of the disc spring 663.

[Brief description of drawings]

1 is a cross-sectional view of the device of the present invention.

2 is a partial view of the device shown in FIG. 1 as seen in the direction of arrow II.

FIG. 3 is a sectional view of one embodiment of a second damping device of the device of the invention.

FIG. 4 shows another embodiment of the second damping device of the device according to the invention.

5 is a cross-sectional view taken along line VV of FIG.

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 discs of the disc group of the second damping device of FIG. 7 in an unassembled state.

9 is a sectional view taken along line IX-IX in FIG.

FIG. 10 shows another embodiment of the second damping device of the device according to the invention.

FIG. 11 shows a modified embodiment of the second damping device of the device according to the invention.

[Explanation of symbols]

1 Rotational shock absorbing device, 2 Flywheel, 3,
4 Bounce mass, 5 Crankshaft, 6 Fixing screw,
7 friction clutch, 8 pressure plate, 9 clutch plate,
10 input shaft, 11 clutch cover, 12 disc spring, 13 first damping device, 14 second damping device, 15 bearing, 16 angular roller bearing, 17 inner race, 18 hole, 19 pin,
20 disc spring, 21 securing disc, 22 additional part, 2
3 chambers, 24, 25 discs, 26 rivets, 2
7 Notches, 28 Overhangs, 29 Flange, 3
0 disc spring, 31 shoulder, 32 lining segment, 33, 34 notch, 35 energy store, 36 play, 37, 38 disk, 39 spacer pin, 4
0 accumulator, 41 accumulator, 42 pressure ring,
43 friction rings, 44 notches, 45 teeth

Continuation of the front page (51) Int.Cl. ⁶ Identification number Reference number within the agency FI Technical display location F16F 15/129 9030-3J F16F 15/12 N (72) Inventor Paul Maucher, Federal Republic of Germany Saasbatcha am Bungert 23 (72) ) Inventor Ozwald Friedman, Germany Lichtenau Moselle Schitraße 59

Claims (4)

[Claims] 1. A device for absorbing the rotational shock of an internal combustion engine, comprising at least two coaxially arranged mutually-bounceable mass bodies against the action of a damping device. However, one of these flywheel masses can be connected to the internal combustion engine and the other flywheel mass can be connected to the input of the transmission, the damping device having a circumferentially effective energy store and / or friction. Alternatively, in a type having a sliding member, an intermediate portion (flange 29) rotatable with respect to both the flywheel mass bodies (3, 4) is provided, and the intermediate portion is provided for the both flywheel mass bodies. Attenuator (13, 1)
13 or 14, 114, 214, 314, 414,
514, 614) and the intermediate portion is radially outside the range (28, 228, 32).
Device for absorbing rotational shock of an internal combustion engine, characterized in that it is guided concentrically to one of the flywheel masses via a contact hole (8,428,528). 2. The device as claimed in claim 1, wherein the intermediate part (29) is guided concentrically with a flywheel mass (3) which can be connected to the internal combustion engine. 3. Device according to claim 1, wherein the intermediate part (29) is guided concentrically via its outer circumference. 4. The intermediate part (29) according to claim 1, wherein the intermediate part (29) is guided concentrically by the inner peripheral surface (22b) of the axial addition (22) of one of the flywheel masses. The apparatus according to item 1.