JPH0465256B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention comprises at least two coaxially arranged spring masses which are pivotable with respect to each other in a limited manner against the action of a damping device; One of these spring masses, a first spring mass, can be connected to the internal combustion engine, and the other spring mass, a second spring mass, can be connected via a friction clutch to the input of the transmission. The present invention relates to a torque transmission device having means for absorbing or compensating rotational shocks, in particular torque fluctuations, of an internal combustion engine, the friction clutch being actuatable via a disengagement device.

PRIOR ART A torque transmission device of the above type is known, for example from DE 28 26 274 A1. In this case, the spring mass which can be connected to the input part of the transmission is connected via a flange sleeve.
It is rotatably mounted on an axial projection of a spring mass connected to the crankshaft of the internal combustion engine. The arrangement of the flange sleeve is such that the radial flange of this sleeve receives the force necessary to disengage the friction clutch provided on the spring mass which can be connected to the input of the transmission and is connected to the internal combustion engine. This is done so that the energy is transmitted to the bouncy mass body. Due to this configuration, when the friction clutch is actuated, the radial flange of the flange sleeve is clamped with a high force between the two spring masses, so that a high frictional moment is created between the two spring masses. is caused. However, for many fields of use, such high frictional moments are disadvantageous. This is because this frictional moment interferes with the functioning of the damping device provided between the two bouncing masses. Interfering with the functioning of the damping device adversely affects the disengagement and engagement of the friction clutch. This means that the clutch disc is not released from the friction clutch over a large part of the working distance traveled by the disengagement device or the tip of the radially inner disc spring tongue. This means that the internal combustion engine and the transmission input are still connected. As a result of the disturbance of the function of the damping device over this range of travel distances, vibrations of large amplitude occur between the internal combustion engine and the transmission, which place high loads on the drive train and impair comfort. resulting in damaging noise and vibration.

Problem to be Solved by the Invention The object of the invention is to provide improved functionality compared to previously known torque transmission devices of the type mentioned at the outset and to enable use in an expanded field. It is an object of the present invention to provide a torque transmission device which can be more effectively and better adapted to the particular purpose of use and which can be produced particularly simply and inexpensively.

According to the invention, the object is achieved in a torque transmission device of the type mentioned at the outset, in which the spring masses are movable in the axial direction in a mutually limited manner in connection with the actuation of the friction clutch. It was resolved by this. The axial movability between the two bouncing masses can be used in a particularly advantageous manner to change the damping properties of the friction device acting between the two bouncing masses. It is particularly advantageous in this case that the mutual axial movement of the two spring masses takes place against the action of a force accumulator, which force accumulator is connected to the input of the transmission. The mass is adapted to exert a force opposite to the disengaging force of a friction clutch mounted on a flywheel mass connectable to the input of the transmission.

For many applications, it is also possible for the spring mass to be constructed in the form of a plate, with an axially limited approach movement possible for disengaging the friction clutch, and again axially limited for the engagement of the friction clutch. Advantageously, it is possible to move away from each other. However, for other applications, the torque transmission device may be such that the spring masses are able to move away from each other in an axially limited manner in connection with the disengagement of the friction clutch, and in which they are again axially limited in connection with the engagement of the friction clutch. It is advantageous if close movement is possible.

Particularly in the case of torque transmission devices in which the spring mass moves axially towards the disengagement of the friction clutch, a so-called friction clutch is fixed on a second spring mass which can be connected to the input of the transmission. Advantageously, it is a push-on friction clutch. However, in the case of torque transmission devices in which the spring mass undergoes a limited axially disengaged movement in connection with the disengagement of the friction clutch, the friction clutch fixed to the second spring mass is a so-called tension friction clutch. It is advantageous to have one. In this case, it is advantageous if both spring masses are loaded with at least one force accumulator in a direction toward one another. In the case of torque transmission devices in which a push-on friction clutch is fixed on the second spring mass, it is advantageous if both spring masses are loaded in a direction away from each other with at least one force accumulator. It is. It is particularly advantageous if the energy storage device is constructed by a disc spring.

Furthermore, according to one embodiment of the invention, it is advantageous if the mutual axial movement of the two spring masses is limited by a stop. Additionally, the spring masses are or can be frictionally or slidingly connected to each other by at least two frictional or sliding surfaces, such that the damping effect of said connection can be varied in conjunction with actuation of the friction clutch. It is advantageous. In this case, a change in the damping effect of the frictional or sliding connection can take place in relation to the axial movement of the two spring masses, that is to say as a result of said movement. It is particularly advantageous that upon disengagement of the friction clutch, the damping effect of the frictional or sliding connection is reduced. Depending on the intended use, it may be advantageous in this case for this damping effect to be eliminated completely or only partially.

According to a further embodiment of the invention, the frictional or sliding connection consists of a frictional or sliding lining provided between the two floating masses, which frictional or sliding lining is configured on both disks. are provided on mutually opposite end faces of the bouncing masses. In this case, it is advantageous if the friction or sliding linings are arranged in an arcuate manner and can move both spring masses towards or away from each other, if the friction clutch is not actuated. It is squeezed between the bouncing masses by the loaded force accumulator. In this case, it is advantageous if the torque transmission device is constructed in such a way that the load on the friction ring and thus its damping effect is removed when the friction clutch is disengaged. However, for many applications the load on the friction ring is reduced upon disengagement of the friction clutch due to the resulting axial movement between the two spring masses, and the friction clutch is disengaged. It is advantageous if the damping effect of the friction ring is maintained, even if it is reduced.

It is further particularly advantageous that the two spring masses are rotatably supported relative to each other via rolling bearings, one race ring being axially fixed to the second spring mass and the other race ring being axially fixed to the second spring mass. 1st
It is supported so as to be movable in the axial direction on an axial protrusion provided on the bouncing mass. In this case, the force accumulator, which loads the spring masses towards or away from each other, acts on an axially movable race ring of the rolling bearing, which acts on the spring mass receiving the race ring. It is advantageous if the race ring of the lever is prevented from pivoting.

The damping device may also consist of a circumferentially acting force accumulator and/or a frictional or sliding element, which force accumulator and/or frictional or sliding material is provided between the two spring masses. , it is advantageous if it is adapted to act in addition to the frictional or sliding coupling that changes in connection with the actuation of the friction clutch. This results in a large variation possibility for obtaining a predetermined damping characteristic and ensures perfect adaptation to the respective intended use.

Embodiment The torque transmission device 1 for absorbing or compensating rotational shocks shown in FIG. 1 has a flywheel 2 that is divided into two flywheel masses 3, 4. The spring mass 3 is fastened via a screw 6 onto a crankshaft 5 of an internal combustion engine (not shown). A so-called push-type friction clutch 7 is fixed onto the spring mass 4 via a screw (not shown). A clutch plate 9 is provided between the pressure plate 8 of the friction clutch 7 and the spring mass 4. This clutch plate 9 is received on an input shaft 10 of a transmission, not shown. The pressure plate 8 of the friction clutch 7 faces the spring mass 4,
It is loaded by a disc spring 12 which is pivotably mounted on the clutch cover 11. Friction clutch 7
By activating , the flywheel mass 4 and thus the flywheel 2 are connected and disconnected via the clutch plate 9 to the input shaft 10 of the transmission.

Between the two spring masses 3, 4 there is a damping device 1.
3 is provided. This damping device 13 acts against relative rotation between the two spring masses.

The two spring masses 3 and 4 are rotatably supported relative to one another via a bearing arrangement 14.
The bearing arrangement 14 consists of a rolling bearing 15 . The outer race 15a of the rolling bearing 15 is non-rotatably received in the receiving hole 16 of the propelling mass 4 and the inner race 15b on the extension 18 of the propelling mass 3 facing away from the crankshaft 5. There is. The rolling bearing 15 is held on the extension 18 of the spring mass 3 by a sheet metal profile 19. The sheet metal profile 19 is connected to the spring mass 3 via rivets 20 and grips the inner ring 15b from behind in the axial direction with its radially extending outer edge region 19a.

The damping device 13 has a force store in the form of a helical spring 21 and a friction element in the form of a friction ring 22 for damping the helical spring 21 .

The input part of the damping device 13 includes two discs 23 and 24.
It is formed by. These two disks 23,
24 are non-rotatably coupled to each other via spacer pins 25 at intervals in the axial direction. Disk 2
4 has a radially extending arm 24b on its outer periphery, which arm 24b rests on an end face 26 of a circular ring-shaped axial projection 27 of the spring mass 3 and is fixed thereto with a rivet 28. A flange-shaped component 29 is arranged between the two discs 23, 24. This component 29 forms the output of the damping device 13. Component 29
has a radially extending projection 30 on its outer periphery, which extends over both discs 2 of the component 29.
3,24. Radial overhang 3
0 rests on the end face 32 of the spring mass 4 and is fixed there via a rivet 33 to the spring mass 4. The radial projection 30 and the radial arm 24b are angularly offset from each other when viewed in the circumferential direction of the flywheel 2.

Notches 23 are provided in the discs 23, 24 and the component 29.
a, 24a and 29a are provided. The damping device 13 is installed in these notches 23a, 24a, 29a.
A coil spring 21 is received. In this case, the notches 23a, 24a, 29a and the coil spring 21 provided therein are arranged and designed so that a multistage damping characteristic line is obtained when viewed in the circumferential direction of the damping device 13. Further, the component 29 has an arcuate notch 29b. This notch 29
A spacer pin 25 passes through b. The relative rotation between the two spring masses 3, 4 is limited in that the spacer pin 25 rests in the end region of the arc-shaped recess 29b.

The friction ring 22 used for effecting frictional damping is clamped between the disc 24 and the radial region 31 of the component 29, with the friction clutch 7 not disengaged. This tightening is ensured by a force store in the form of a disc spring 34. This disc spring 3
4 is supported in the radially extending range of the shoulder 17;
A load is applied to the inner race 15b in a direction away from the crankshaft 5. As a result, the spring mass 4 and the components fixed thereon are loaded in a direction away from the spring mass 3.

Inner race 15 is used to ensure axial movement of the lifting mass 4 relative to the lifting mass 3.
b is received on the extension part 18 or the thin plate molding 19 so as to be movable in the axial direction but not to rotate. In order to prevent rotation of the race ring 15b, the thin plate molded body 19 has a protrusion 19 projecting in the radial direction.
It has b. This protrusion 19b is the inner race 15
It engages with the vertical groove 15c of b. In order to ensure that the partially worn friction ring 22 is tightened between the component 29 and the disk 24, the inner race 1
An axial rear adjustment play is provided between 5b and the radially extending outer edge region 19a.

The disc spring 34 is installed in such a way that the disc spring 34 is pivoted by a predetermined value X when the bias of the disc spring 34 is overcome. In the embodiment shown in FIG. is the distance in the direction. Depending on the intended use, this value X can vary from 0.1 mm to 2 mm.

The frictional moment produced by the friction ring 22 can be suitably varied by varying the properties of the disk springs 34 or 36.

From the position shown in FIG. 1, the torque transmission device 1 operates as follows.

With the friction clutch 7 engaged, the frictional moment generated by the friction ring 22 during a relative rotation between the two spring masses 3 and 4 is at a maximum. A disengagement device 35 disengages the friction clutch 7 by disengaging the radially inner disc spring tongue tip 1.
2a, the bias of disc spring 34 is gradually offset as the dissociation force increases. The frictional moment generated by the friction ring 22 therefore decreases as the release force increases. When the applied release force overcomes the bias of the disc spring 34, the disc spring 34 is pivoted and the spring mass 4
is moved towards the bouncing mass 3 by a value X. Due to this movement, the friction ring 22 fixed to the component 29 is separated from the disc 24, so that the friction ring 22 no longer produces a friction damping effect. Bearing 15 depending on the spring mass 4
is also moved axially. The bearing 15 must receive the force necessary to disengage the friction clutch 7.

In order to connect the friction clutch 7, a disengaging device 3 is used.
The axial force acting on the clutch cover 5 is gradually removed, and as a result, the disc spring 12, which is pivoted to the clutch cover 11, is pivoted based on the spring force. The clutch plate 9 is gradually tightened between the spring mass 4 and the pressure plate 8. If the force acting on the disc spring tongue tip 12a is less than the force produced by the biased disc spring 34, the bearing 15 and thus the spring mass 4 and the components fixed thereto bouncy mass body 3
is separated from by a value X. As a result of this movement, the friction ring 22 comes into contact with the disc 24 again, and due to the bias remaining in the disc spring 34, a friction moment is generated again between the masses 3 and 4.

In a variant embodiment of the invention, additional friction or sliding elements act between the spring masses 3 and 4. This friction or sliding element ensures frictional damping between the two spring masses 3, 4 even when the friction clutch 7 is disengaged. Such means can be formed by a Belleville spring 36, as shown in phantom in FIG. This plate spring 36 is arranged on the opposite side of the flange-shaped component 29, facing the friction ring 22. This disk spring 36 is clamped between a flange-like component 29 and a disc 23 and is prevented from rotating relative to this disc 23 or to the spring mass 3, and is secured against both spring masses 3 and 4. During the relative rotation between them, the disc spring 36 rubs against the flange-shaped component 29 in the radially inner region. The friction moment generated by disc spring 36, in contrast to the friction moment generated by friction ring 22, is maintained even when friction clutch 7 is disengaged. Depending on the design of the disc spring 36, the frictional moment generated by the disc spring 36 changes due to the movement between the two spring masses 3 and 4 when the friction clutch is engaged and disengaged.

If necessary, the disk spring 34 can be omitted, since the disk spring 36 also tensions the two spring masses.

The difference between the torque transmission device shown in FIG. 2 and the torque transmission device shown in FIG. 1 is that a so-called tension friction clutch 107 is fixed to the spring mass 4. The friction ring 122 is arranged on the opposite side of the component 29, and the disk spring 134 is clamped between the inner ring 15b and the radially extending outer edge region of the sheet-metal profile 19.

Due to the bias of the plate spring 134, the bearing 15 and thus the spring mass 4 and the components fixed thereon are pushed towards the spring mass 3. As a result, the friction ring 122 fixed on the component 29 is squeezed between the component 29 and the disc 23. There is an axial play between the radially extending area of the shoulder 17 and the inner race 15b, which adjusts when the friction ring 122 wears out, i.e. the axial movement of the spring mass 4 relative to the spring mass 3. is becoming possible.

Also in this case, when the bias of the disc spring 134 is overcome, the disc spring 134 is pivoted or compressed by a predetermined value X, and the friction ring 1
22 is mounted in such a way that it separates from the disc 23 upon disengagement of the friction clutch.

In the embodiment shown in FIG. 2, an additional disc spring 136 can also be provided which generates a frictional moment even when the friction clutch is disengaged. If such a spring 136 is provided, the disc spring 134 may be omitted depending on the circumstances.

Next, the function of this torque transmission device will be explained from the position shown in FIG.

When the friction clutch 107 is engaged, the maximum frictional moment generated by the friction ring 122 acts upon the relative rotation between the two spring masses 3 and 4. When the inner disc spring tongue tip 112a is loaded in a direction away from the spring mass 3, the bias of the disc spring 134 is gradually offset as the release force increases, and the friction created by the friction ring 122 moment is reduced. When the releasing force developed in the tongue tip 112a exceeds the bias of the disc spring 134, the disc spring 134 is pivoted or compressed and the spring mass 4 is moved away from the spring mass 3 by a value X. This movement is caused by component 2
The friction ring 122 fixed to the friction disk 23
to prevent frictional damping from occurring.

When the friction clutch 107 is engaged, the force exerted on the tongue tip 112a is less than the force of the biased disc spring 134;
The spring mass 4 and thus the component 29 and the friction ring 122 fixed thereon are connected to the spring mass 3
be moved towards. This brings the friction ring 122 back into contact with the disc 23 and creates a frictional moment.

Of course, disc springs 34, 36 or 1 allow a relative axial movement of both spring masses 3, 4.
By a suitable adjustment between 34, 136 and the course of the disengaging force of the friction clutch 7, it is possible to influence the course of the friction change between the disengaging and connecting processes. For many applications, it is advantageous for disc spring 34 or 134 to have a biasing force somewhat greater than the maximum operating force required to actuate the friction clutch. In this case, while operating the friction clutches 7, 107, the friction ring 22
Alternatively, the friction moment generated by 122 may be reduced but not completely eliminated.

[Brief explanation of the drawing]

The drawings show a plurality of embodiments of the present invention, and FIG. 1 is a sectional view of the torque transmission device of the present invention;
FIG. 2 is a sectional view of one embodiment of the torque transmission device of the present invention. 1...torque transmission device, 2...flywheel, 3, 4...
Thrust mass body, 5... crankshaft, 6... screw, 7...
Friction clutch, 8... Pressing plate, 9... Clutch plate, 1
0... Input shaft, 11... Clutch cover, 12... Belleville spring, 13... Damping device, 14... Bearing device, 15... Rolling bearing, 16... Receiving hole, 17... Shoulder, 18... Addition part, 19... Thin plate molded body part , 20...Rivets, 2
1... Coil spring, 22... Friction ring, 23, 24
...Disk, 25...Spacer pin, 26...End face, 27
...Protrusion, 28...Rivet, 29...Flange-like component, 30...Protrusion, 31...Range, 32...End face, 33...Rivet, 34...Disc spring, 35...Dissociation device, 36... Disc spring, 107... Friction clutch, 1
22...friction ring, 134...disc spring, 136...disc spring.

Claims (1)

[Scope of Claims] 1. A torque transmission device having means for absorbing or compensating rotational shocks, comprising at least two coaxially arranged spring masses that are rotatable relative to each other against the action of a damping device. one of these spring masses, a first spring mass, can be connected to the internal combustion engine and the other spring mass, a second spring mass, can be connected to the input of the transmission via a friction clutch. In a torque transmission device having means for absorbing or compensating rotational shocks, in particular torque fluctuations, of an internal combustion engine, of the type that can be coupled to a friction clutch and that the friction clutch can be actuated via a release system, in which the spring masses 3, 4 are With the energy storage device,
Torque transmission, characterized in that the spring masses holding the clutch, axially tensioned elastically with respect to each other, are loaded in a direction opposite to the direction of the force effective for releasing the clutch. Device. 2. Torque transmission according to claim 1, wherein the axial tension between the spring masses exerted by the force accumulator is smaller than the axial force exerted when releasing the clutch. Device. 3. Torque transmission device according to claim 1, wherein the spring masses are axially movable relative to each other in relation to the actuation of the friction clutches 7, 107. 4. The spring masses are movable axially in relation to the disengagement operation of the friction clutch 7 toward each other and are again axially limited in their movement away from each other when the friction clutch 7 is engaged. A torque transmission device according to any one of claims 1 to 3, which is movable. 5. The spring masses are movable in an axially restricted manner away from each other in connection with the disengaging operation of the friction clutches 107, and are again axially restricted in their movement toward each other during the engaging operation of the friction clutches. A torque transmission device according to any one of claims 1 to 3, which is possible. 6. Torque transmission device according to claim 1, characterized in that a push-release clutch 7 is fixed to the second spring mass 4. 7. Torque transmission device according to one of claims 1 to 3 or claim 5, in which a pull-release clutch 107 is fixed to the second spring mass 4. 8. In accordance with one of the claims 1 to 3, or in which the two spring masses 3, 4 are loaded in close proximity to each other via at least one force accumulator 134, 136. The torque transmission device according to item 2 or 7. 9. Any one of claims 1 to 4 or 4, in which both spring masses 3, 4 are loaded in directions away from each other by at least one force accumulator 34, 36; The torque transmission device according to item 6. 10. Claim 1, in which the power accumulators 34, 36; 134, 136 are formed by disc springs.
9. The torque transmission device according to any one of items 9 to 9. 11. Torque transmission device according to any one of claims 1 to 10, wherein the axial movement amount X of both spring bodies 3, 4 relative to each other is controlled by stoppers 17, 19a. . 12 the spring masses 3, 4 are or can be frictionally or slidingly connected to each other via at least two frictional or sliding surfaces;
12. Torque transmission device according to claim 1, wherein the damping effect of the coupling can be varied in conjunction with the actuation of the friction clutch. 13. Torque transmission device according to claim 11, wherein the damping effect of the frictional or sliding connection is variable as a function of the axial displacement distance X of the two spring masses 3, 4 relative to each other. 14. Torque transmission device according to claim 12 or 13, in which the damping effect of the frictional or sliding connection is reduced when the friction clutch 7, 107 is disengaged. 15. Torque transmission device according to claim 12 or 14, wherein the damping effect of the friction or sliding connection is removed when the friction clutch is disengaged. 16. A frictional or sliding connection is formed by at least one frictional or sliding lining 22, 122 provided between the two floating masses;
A torque transmission device according to claim 12 or 13. 17. A friction or sliding lining is provided between the end faces of the two disk-shaped floating masses which face each other and are at least approximately the same diameter when viewed in the axial direction. The torque transmission device according to range 16. 18. Torque transmission device according to claim 16 or 17, characterized in that the friction or sliding linings 22, 122 are provided in an annular arrangement. 19 The friction or sliding lining 22, 122 is
Patent 7, 107 is tensioned between the two spring masses 3, 4 by means of an accumulator which loads them towards or away from each other when the friction clutch 7, 107 is not actuated. A torque transmission device according to any one of claims 16 to 18. 20. The torque according to any one of claims 1 to 19, which removes the tensioning force applied to the friction rings 34, 36; 134, 136 when the friction clutches 7, 107 are disengaged. transmission device. 21 The tensioning force of the friction rings 22, 122 is applied to the friction clutches 7, 10 between the two spring masses 3, 4.
21. The torque transmission device according to any one of claims 1 to 20, wherein the torque is reduced when the torque transmission device 7 is disengaged. 22 Both spring masses 3, 4 are rolling bearings 1
22. Torque transmission device according to any one of claims 1 to 21, wherein the torque transmission device is rotatably supported relative to each other via 5. 23. Torque transmission device according to claim 22, wherein one bearing race ring 15a is axially fixed to at least one of the spring masses 4. 24. Claim 2, wherein one bearing race ring 15b is axially movable on an axial extension 18 provided on one of the spring masses.
The torque transmission device according to item 2 or item 23. 25 Force accumulator 3 for loading the spring masses 3, 4 towards each other or away from each other
4,134 acts on an axially movable ring 15b of the rolling bearing 15, which is prevented from rotating relative to the spring mass 3 receiving this ring. The torque transmission device according to any one of items 1 to 24. 26 Force accumulator 2 in which the damping device 13 acts in the circumferential direction
1 and/or a friction or sliding member 36,136, which is arranged between the two spring masses 3,4. Claims 1 to 23 are additionally effective for variable friction or sliding member connections 22, 122.
The torque transmission device according to any one of the preceding paragraphs.