JPH0444138B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention includes a drive disc and a driven disc received between cover discs that are axially and non-rotatably coupled to each other. are movable in the circumferential direction relative to each other and each with respect to the cover disk, and independently of each other in the circumferential direction with respect to the cover disk; The present invention relates to a torsional vibration damper which is supported via a respective damping spring group consisting of circumferentially acting damping springs received in circumferential recesses which are distributed over the area.

Torsional vibration dampers of this type are used in conjunction with torque converters or fluid clutches in motor vehicle drive systems with automatic transmissions to compensate for occurring inconsistencies, shock loads and the like. Moreover, it is useful for avoiding torsional vibrations from the moment they occur.

A two-stage torsional vibration damper for use in motor vehicle drives with torque converters is described in DE 30 47 039 A1. In this case, the driving disk driven by the torque converter and the driven disk non-rotatably connected to the driven shaft are accommodated between the cover disks and a damping spring acts on them in the circumferential direction. is supported by. In this case, between the driving disc and the cover disc and between the cover disc and the driven disc,
A relatively large relative movement is achieved due to the presence of circumferentially distributed spring groups of damping springs connected in series with each other in each stage. In this case, a radially oriented driver is arranged between the damping springs which are received in the circumferential recess of each spring group. This driver is connected in one stage partly to the drive disc and partly to the cover disc which receives the drive disc therebetween, and in the other stage is supported so as to be movable in the circumferential direction. , the transmission of rotational torque from the driving disc to the driven disc and the damped relative movement between these discs and the cover disc, and thus the relative movement between the driving disc and the driven disc. enable.

An object of the present invention is to provide a vibration damper which has a simple structure and can effectively suppress periodic excitation of torsional vibration.

This object is achieved according to the invention in a torsional vibration damper of the type mentioned at the outset, in which the drive disc and the cover disc and between the cover disc and the driven disc are This was achieved by providing one friction stage in each case, which is effective when relative movements occur.

That is, according to the configuration of the present invention, the damping effect provided by the friction stage is superimposed on the vibration damping effect performed by the damping spring, so that the vibration excitation force is quickly damped, and as a result, torsional vibration is suppressed at the time it occurs. become.

According to one embodiment of the present invention, the damping springs of each damping spring group are connected in parallel with each other;
Both damping spring groups are connected in series with each other, and when a rotation angle occurs between the driving disk and the driven disk, the damping spring groups assigned to both disks cooperate. I'm starting to work. When connected in series, the composite spring characteristic line has a flatter course than the characteristic line of single springs connected in parallel, so in this type of configuration, when the turning torque is small, can also produce significant rotation angles. In this case, it is advantageous if the damping springs of each damping spring group have the same spring stiffness.
On the other hand, the damping springs of different damping spring groups have different spring stiffnesses.

By appropriately designing the achievable spring travel and spring stiffness of the damping springs of each damping spring group,
From a certain rotation angle between the drive disk and the driven disk, a characteristic curve course that differs from the initial range can be provided. This is achieved in that the cooperation of the damping springs of the different damping spring groups is released after a predetermined rotation angle has been reached. The cooperation of the damping springs of different damping spring groups connected in series in the initial rotation angle range is complete after the damping springs of one damping spring group reach a predetermined rotation angle range. This occurs because only the damping springs of the other damping spring group do not permit any relative movement between the associated disc and the cover disc, and thus between the driven disc and the driving disc. It goes without saying that if the damping springs of one of the damping spring groups are blocked before this second rotation angle range, only the characteristic line of the damping springs still involved in the rotation becomes effective. According to a further embodiment of the invention, the relative movement of the drive and/or driven disk with respect to the cover disk is limited to a predetermined rotational angle by a circumferentially acting stop. , when this stop comes into play, a non-rotatable connection is created in the relevant direction of rotation between the associated disc and the cover disc, and the damping spring acting between these discs is interrupted. be done.

In contrast, in a further embodiment of the invention, the springs of at least one damping spring group are prestressed. In this case, a characteristic curve that gradually decreases is obtained. The unpreloaded or weakly preloaded damping springs of one of the damping spring groups act alone for the time being in the initial rotational angle range, and the course of the rotational torque depends on the specific spring stiffness. Determined in relation to the rotation angle that occurs accordingly. When the spring force of the damping springs of this damping spring group reaches the preload force of the damping springs of the other damping spring group based on tightening, the damping springs of both damping spring groups act in parallel connection and can be achieved. The rotation angle is given as the sum of the rotation angles occurring in the individual damping spring groups. The characteristic line of the rotational torque in relation to the rotational angle has a flatter course, and the overall characteristic line in the rotational angle range in which the damping springs of both damping spring groups cooperate Compared to the initial rotation angle range in which only the non-preloaded damping springs of the damping spring group act, the rotation angle gradually decreases.

In another embodiment of the invention, a third group of damping springs is provided. In this case, the third damping spring group becomes effective after a predetermined rotation angle is achieved between the drive disc and the cover disc or between the cover disc and the driven disc. Since it is configured,
These additional damping springs are connected in parallel with damping spring groups that are still active after reaching a predetermined rotation angle. As a result, the rotation resistance is significantly increased, leading to a steeper course of the rotation torque characteristic line as a function of the rotation angle. In this case, the damping springs of the damping spring group, which become effective only after a predetermined rotational angle has been reached, are fixedly connected to the cover disc and are mounted on the drive or driven disc. It is advantageous if the damping spring group is accommodated in an arcuate recess which extends on each side by a predetermined length in the circumferential direction. By virtue of the fact that the damping spring is received in a circumferential recess that extends the length of the spring on both sides in the circumferential direction, said damping spring is located between its end face and the edge circumferentially limiting the arcuate recess. It comes into contact with the edge of the notch for the first time after traveling through the space. This edge acts as a stop for a damping spring, which is connected in parallel to the damping springs of the damping spring group that are still active.

According to a further embodiment of the invention, only after a predetermined pivot angle has been reached between the drive disc and the cover disc and/or between the cover disc and the driven disc is the A load friction stage is provided which is activated. This loaded friction stage is confined between spring-loaded discs movable relative to each other in the circumferential direction, movable in the axial direction and rotatable without friction through a predetermined angle relative to one of said discs. It has a friction disc supported on. In this case, after having been driven through a friction-free rotation range, the friction disk is fixedly connected to one of the aforementioned disks, for example to the driven disk.

Furthermore, according to a further embodiment of the invention, a friction step is provided which acts directly between the driving disk and the driven disk, so that in the event of a relative rotation, the driving disk and the cover disk In addition to the frictional effects between the plates and between the cover disk and the driven disk, a direct friction is produced between the drive disk and the driven disk.

In one embodiment of the torsional vibration damper according to the invention, each friction stage is provided with at least one friction ring crimped onto one friction surface of the discs movable relative to each other in the circumferential direction. It is being In at least one friction stage, this friction ring is limited to one friction surface of the discs which are movable relative to each other in the circumferential direction by means of a pressure disc which is supported in a limited and axially movable manner. In contrast to the press-fit, the pressure plate is mounted non-rotatably under spring force on the other disc with which it cooperates in the friction stage. A Belleville spring can be used in each case to press the pressure disc or the friction ring.

The invention will now be explained with reference to the drawings: In the torsional vibration damper illustrated in FIGS. Disk 1
2 are connected so as to be relatively unrotatable. Drive disc 1
2 are received between cover discs 13, 14 which are arranged at an axial distance from each other and are connected to each other in a non-rotatable and axially non-movable manner.
Spacer pins 15, which are riveted to the cover disks, are used to effect the connection between the cover disks. The spacer pins 15 are arranged circumferentially distributed near the outer edge of the cover disk and pass through arc-shaped elongated holes 16 provided in the drive disk. The spacer pin 15 can move within the circumferential length of the elongated hole 16, and thus the cover discs 13, 14 and the drive disc 12 can rotate relative to each other. .

The spacer pins 15 are shifted in the circumferential direction with respect to the elongated holes 16 that pass through them, and are distributed in the circumferential direction.
Mutually aligned circumferential notches 17, 18, 1 provided in the cover discs 13, 14 and the drive disc 12
A damping spring 20 is received at 9 . By this damping spring 20, the driving disk 12 and the cover disk 13,
14 are mutually supported in the circumferential direction. Damping spring 2
0 is the circumferential notch 17,1 in the cover disc
8 are bent towards the outside in each case, and the damping spring is gripped at least partially from above so that the drive disc 12 and the cover disc 13,
It is held in 14 window-shaped circumferential notches. Friction rings 22, 23 are arranged radially inside the damping spring 20 on both sides of the drive disk. In addition to forming the first friction stage, these friction rings also form a first damping stage in cooperation with the damping springs 20 which are distributed in the circumferential direction. The friction ring 23 cooperates directly with the inner friction surface of the inner cover disc 14, whereas the other friction ring 22 cooperates with the cover discs 13, 14 in a non-rotatable but limited axial direction. a pressure disk 24 movably coupled to
The disc spring 25 is supported by the outer cover disc 13 and is pressed to the drive disc via the disc spring 25 . The pressure disc 24 has a first contact in the region of the spacer pin 15 which axially and non-rotatably connects the cover discs to one another.
It has a radially outwardly extending section 26 which partially grips the spacer pin 5 from above as shown.

A driven disk 30 is received radially inwardly of the drive disk 12 and coaxially therewith between the cover disks 13, 14. The driven disc 30 is non-rotatably connected on the boss side via internal teeth 32 to corresponding external teeth 33 of a driven shaft 34 indicated by a dashed line in FIG. Circumferential cutouts 3 provided in the cover discs 13, 14 and the driven disc 30, distributed in the circumferential direction and aligned with each other
A damping spring 40, which also acts in the circumferential direction, is received in 6, 37, 38 and is retained by bending outward the outer edge of a circumferential recess provided in the cover disc. There is. This inner damping spring 4
0, the driven disk 30 and the cover disk 13,
14 are mutually supported elastically in the circumferential direction. As in the case of the driving disc, in the area of the boss-side edge of the driven disc there are friction rings 4 on both sides of the driven disc.
2,43 are arranged. Whereas the friction ring 42 acts directly between the driven disc and the corresponding friction surface of the front cover disc 13, the friction ring 43 is guided with limited axial movement. It is also pressed onto the other side of the driven disk 30 via a pressing disk 44 which is non-rotatably connected to the cover disk. The clamping force is provided by a disc spring 45 supported by a load friction disk 48, which will be discussed in more detail below in relation to the third damper.

The load friction disk 48 is arranged coaxially with respect to the driven disk 30 and movable in the axial direction between the driven disk and the inner cover disk 14 . In the area of the circumferential recess provided in the driven disk 30 and the cover disks 13, 14 for receiving the damping spring 40 of the second damping stage, the load friction disk 48 is likewise provided with a circumferential cutout. A directional notch 49 is provided. However, since the circumferential dimension of this circumferential notch is larger than the circumferential notches provided in the driven disk and the cover disk, the load friction disk is such that the damping spring 40 is It has a predetermined circumferential movement with respect to the aforementioned disk without coming into contact with a direction limiting surface. This load friction disk 48 cooperates with two damping springs 50 to form a third damping stage. Both damping springs 50 are arranged symmetrically with respect to each other.
Other circumferential notches 51, 52 in the cover discs 13, 14 between the damping springs 40 of the damping stages of
and extends through aligned circumferential notches 53 and 54 in driven disc 30 and load friction disc 48, respectively. Circumferential notches 53, 54 in driven disk 30 and load friction disk 48
extends in the circumferential direction beyond the circumferential dimension of the damping spring 50, so that the damping spring 50
Only after the cover discs 13 and 14 have rotated by a predetermined amount, does it come into contact with the circumferential limiting surface of the circumferential notch 53 in the driven disc, and then the predetermined rotation described above. It becomes effective only after the angle of movement has occurred.

A friction ring 56 is arranged between the load friction disk 48 and the inner friction surface of the inner cover disk 14 . A pressure disk 44 belonging to the second friction stage is arranged between the load friction disk and the inner cover disk, and this pressure disk is inserted into a circumferential recess provided in the inner cover disk 14. By virtue of being non-rotatably connected to the cover disc via the axially oriented tongue 46 which engages positively, the load friction disc 48 is pressed against the friction ring 56 . are pressed against the corresponding friction surfaces of the inner cover disc 14.

On the other hand, when facing the driven disk 30, the load friction disk 48 is freely rotatable over a predetermined circumferential angular range. In this case, the tongue 57 oriented in the axial direction of the load friction disk is connected to the driven disk 3.
0, which engages in a circumferential cutout 53 extending beyond the damping spring 50 on both sides. This tongue piece 57 hits a stopper after the load friction disk rotates by a predetermined amount with respect to the driven disk, and then stops the load friction disk and driven disk from rotating in the respective rotation direction. bring about union. The damping spring 50 has a load friction disk 48 and an inner cover disk 14.
A third damping stage is formed in cooperation with a friction ring 56 provided between the friction surface and the friction surface.

During operation of the torsional vibration damper 10, the drive part 11
When a torque is introduced via the drive disc 12 from Driven disk 30
A rotation is generated between the two. The damping springs 20 and 40 of the first and second damping stage, which are installed without being preloaded, then act with a correspondingly soft spring characteristic in series connection. This is illustrated by the flat curve of characteristic line 60 in the characteristic diagram of FIG. Of course, greater pivoting occurs in damping stages where the damping spring has a lower stiffness. This damping stage consists of a drive disk 12 and a cover disk 1.
3, 14 with a damping spring 20. The damping spring 20 of this damping stage is tightened by the pivoting of the drive disc 12 relative to the cover discs 13, 14, and the spacer pin 15 connects the two cover discs to each other non-rotatably and axially immovably. When brought into contact with the end of the arc-shaped elongated hole 16 in the drive disk, the damping springs of the first damping stage are cut off and only the damping springs of the second damping stage become effective. In the characteristic diagram of FIG. 3, the first damping stage extends over the rotation angle range from 0° to 23°,
Between the rotation angles 23° and 38° after the first damping stage has been switched off, only a relative movement between the driven disc 30 and the cover discs 13, 14 takes place in the region of the second damping stage. Not possible. In this case, only the damping spring 40 is active, so that the characteristic curve 61 has an upward slope in the region of the second damping stage. When the rotation angle between the driving disk 12 and the driven disk 30 reaches 38 degrees, the damping spring 50 of the third damping stage comes into contact with the circumferential limiting surface of the window-like cutout of the driven disk. The damping springs 50 of the third damping stage act in parallel with the damping springs 40 of the second damping stage.
By connecting the damping spring 40 of the second damping stage in parallel with the damping spring 50 of the third damping stage in this way, the characteristic line 62 is strongly raised. This characteristic line 62 connects to the characteristic line 61 of the second damping stage at a rotation angle of 38° and acts until the entire damping spring of the second and third damping stage is blocked at a rotation angle of 42°. do.

As described above, in addition to the damping spring acting when rotation occurs between the drive disk 12 and the cover disk and between the cover disk and the driven disk, the damping spring acts on the drive disk and the driven disk. The friction stage assigned to each damping stage also acts when the disc moves relative to the cover disc.
This means that in the region of the first damping stage with a relatively soft damping spring 20, a relative movement occurs during the initial rotation, in particular between the drive disc 12 and the cover discs 13, 14, and the friction ring 22, Friction occurs in the range of 23. drive disc 12 and cover disc 13,
When a predetermined amount of rotation is achieved during 14, the spacer pin 15 that connects the cover discs to each other comes into contact with the end of the arc-shaped elongated hole 16, and the gap between the drive disc 12 and the cover disc is This prevents subsequent relative movement from occurring. The friction that occurs as a result of the rotational movement therefore initially takes place only in the area of the friction rings 42, 43 forming the second friction stage. The load friction disk 48 includes the drive disk 12 and the cover disk 13,1.
4, the circumferential notch 5
3 until the axially oriented tongue 57, which engages in is held stationary relative to the cover disc. The third friction stage becomes active after the tongue 57 of the load friction disk has abutted against the aforementioned stop. In this case, the load friction disk, which is frictionally connected to the corresponding friction surface of the inner cover disk 14 via the friction ring 56, performs a relative rotation with respect to the above-mentioned inner cover disk. Friction disc 56 of the third friction stage
The friction movement that takes place in the area is superimposed on the friction movement that occurs in the area of the second friction stage. As shown on the tension side of the characteristic diagram in FIG. 3, the same frictional movement takes place when the rotational torque is reduced and the discs movable in the circumferential direction relative to each other rotate back. must be The same relationship as for the tension side of the characteristic line also applies to the push side.

The embodiment shown in FIGS. 4 and 5 is a three-stage torsional vibration damper in which the same components as the embodiment of FIGS. 100 is added.

In order to introduce the torque from the drive part 111 shown in dash-dotted lines, the drive disk 112 is also required in this case.
is used. This drive disk 112 is axially and non-rotatably connected to cover disks 113,1.
Accepted between 14 and 14. A driving disk 11 is used to transmit torque to a driven shaft (not shown).
This driving disk 11 is arranged coaxially with respect to 2.
A driven disc 130 is used that extends radially inward from 2. This driven disc 130 is likewise received between the cover discs. A boss flange 13 in which the driven disc is provided with simple internal teeth 132 on the boss side and, instead of cooperating with corresponding teeth on the driven shaft, has a keyway 132' corresponding to the boss area of the driven disc.
1 may be integrally formed.

As in the first embodiment, the circumferential notches 117, 118, 119 of the driving disc 112, the cover discs 113, 114, and the driven disc 130 and the cover discs 113, 114 are aligned with each other. Damping springs 120, 140 are received. The damping springs 120, 140 support the driving disk and the driven disk relative to the cover disk in the circumferential direction. However, in contrast to the first embodiment, the first damping stage is assigned to the driven disc 130, whereas the second damping stage is assigned to the drive disc 112. Therefore, the circumferential cutouts 136, 13 are distributed in the circumferential direction on the cover discs 113, 114 and the driven disc 130.
7,138 in which a total of four damping springs 140 of the first damping stage are received, whereas the drive disc 1
In the region 12, three damping springs 120 of the second damping stage are arranged in each of the two halves. Between the damping spring groups of three damping springs 120 of the second damping stage are cover discs 113, 11.
A damping spring 150 of the third damping stage is arranged within the circumferential notches 151 and 152 of No. 4. These damping springs 150 extend through window-like circumferential recesses 153 in the drive disk 112 . Drive disc 11
The arc-shaped circumferential notch 153 of 2 extends beyond the length of the damping spring 150 of the third damping stage, so that the damping spring 150 is longer than the damping spring 1 of the second damping stage.
20, the drive disk 112 tightens and rotates the damping spring 120 of the second damping stage;
It is only when the damping spring 150 of the third damping stage hits the circumferential limiting surface of the arc-shaped circumferential notch 153 in the drive disk that it becomes effective in one or the other direction of rotation.

As in the case of the first embodiment, at the beginning of the rotational movement occurring between the driving disk and the driven disk, the first
and the damping spring of the second damping stage are connected in series, so that the rotation that occurs between the driving disc and the driven disc under load will not be affected by this serially connected damping spring. The resultant force of the damping spring acts. The common operating range of the damping springs of the first and second damping stages is in this embodiment up to a rotation angle of 32°. This is shown by the characteristic line in FIG. In this case, the relatively soft damping spring of the first damping stage has a circular arc in the driven disc 130, which connects the cover discs 113, 114 non-rotatably and axially immovably to each other. A spacer pin 115 movable in the circumferential direction within the elongated hole 116 abuts the end of the elongated hole,
This causes the driven disk to be tightened in the respective direction of rotation until it locks against the cover disk. This stops the action of the first damping stage, and subsequent angular movements take place only between the drive disk 112 and the cover disk. By blocking the damping spring 140 of the first damping stage as described above, only the damping spring 120 of the second damping stage acts for angular movements exceeding a rotation angle of approximately 32°. . This action takes place until, after reaching a rotation angle of approximately 38 DEG, the damping spring 150 of the third damping stage is connected in parallel to the damping spring 120 of the second damping stage and acts. Therefore, the characteristic line 161 of the second damping stage in the rotation angle range between 32° and 38° is the second
It is determined solely by the spring stiffness of the damping spring 120 of the damping stage. On the other hand, the characteristic line 1 of the third attenuation stage
62 exhibits a steep rise. This characteristic line is the second
and the parallel action of damping springs 120 and 150 of the third damping stage, and thus by the resultant spring force resulting as the sum of the individual spring constants.

In the second embodiment as well, friction is superimposed on the spring action in the individual damping stages. However, in contrast to the first exemplary embodiment, in this case the friction ring 122 is present only in the radial overlap region between the drive disk 112 and the driven disk 130.
Although this friction ring 122 cannot rotate,
However, it is pressed against the drive disk 112 by a disc spring 125 acting between the pressure disk and the driven disk 130 via a pressure disk 124 which is axially movably connected to the driven disk 130. be done. Otherwise, when the cover disk and drive disk rotate relative to each other, friction is effective between the drive disk and the cover disk at the outer edges, and the driven disk near the boss area is The arrangement is such that friction is effective between the disc and the cover disc.

In contrast to the first embodiment, this embodiment does not have an additional load friction disk that becomes active only in the third damping stage, although this load friction disk could also be provided in this embodiment. . In this case, a frictional effect occurs before or after the damping spring of the third damping stage becomes effective, in connection with the limited rotation of the load friction disc relative to the driven disc, so-called This creates friction.

In the embodiment shown in FIGS. 7 and 8, the introduction of the load also takes place via a drive disk 212 from a drive part 211, which is only shown in dashed lines.
This drive disk 212 is also in this case a cover disk 2 which is non-rotatably and axially fixedly connected to one another.
13,214. Drive disc 2
A driven disk 230 with a hub portion 231 is received between the cover disks radially inside 12 . This driven disk is in the form of a driven shaft 2, which is also shown only in dash-dotted lines and is not shown in the drawings.
It is combined with 34. Similar to the second embodiment, the damping spring 240 of the first damping stage is arranged as an inner spring ring between the driven disc 230 and the cover discs 213 and 214.
3, 214 are received in mutually aligned circumferential notches 236, 237, 238.
The pivotability of the driven disc relative to the cover disc is limited by spacer pins 215 that axially and non-rotatably connect the cover discs to each other. This spacer pin 215 extends through an arc-shaped elongated hole 216 in the driven disc, and when a predetermined rotation angle is obtained between the driven disc 230 and the cover discs 213, 214, the spacer pin 215 extends It comes into contact with the circumferential limiting surface of the hole. This results in a non-rotatable connection between the driven disc and the cover disc in the respective direction of rotation,
Consequently, the damping spring 240 of the first damping stage becomes ineffective. The damping spring 220 of the second damping stage acts between the drive disc 212 and the cover discs 213, 214 in the same way as in the embodiment shown in FIGS. Unlike the embodiment, it is preloaded and installed.

Due to the preloading of the damping spring 220 of the second damping stage, when a load is applied the spring force of the damping spring 240 of the first damping stage is first applied to the damping of the second damping stage based on the tension of the spring. Until the preload force of the spring 220 is reached, a rotational movement occurs between the driven disc 230 and the cover discs 213, 214. Therefore, in the initial rotation, only the damping spring 240 of the first damping stage is active, so that the course of the characteristic line 260 shown in FIG. 9 in the range between 0° and 3° corresponds to the damping of the first damping stage. It is determined solely by the spring stiffness of spring 240. When the rotation angle between the driving disk 212 and the driven disk 230 increases, the damping spring 220 of the second damping stage is connected in series with the damping spring 240 of the first damping stage and acts on it. As a result, the resultant spring force due to the series connection becomes effective. The combined spring characteristic due to the series connection has a flatter profile than the individual spring characteristics of the damping springs 220, 240 of both damping stages, so that angular movements exceeding a rotation angle of about 3° are not possible in FIG. Determine the flat course of the characteristic line 261 shown in FIG. This characteristic line 261 extends approximately 14° in the exemplary embodiment shown. By using a prestressed damping spring on one of the damping stages, a tapering characteristic curve can therefore be realized.

The series connection of the first and second damping springs is such that when the angular movement between the drive disk 212 and the cover disks 213, 214 progresses, the drive disk 212 and the cover disk 21
3,214, the stopper becomes effective at a rotation angle of about 14 degrees. In this case, a non-rotatable connection is created between the drive disk and the cover disk in the respective direction of rotation. After the damping spring 220 of the second damping stage has been cut off in this way, any further angular movement is prevented by the damping spring 24 of the first damping stage acting alone in the initial rotation range.
The stopper, which acts only against the action of 0 and between the cover disk and the driven disk, abuts, so that the driven disk cannot also rotate with the cover disk in the respective direction of rotation. This is done until it is combined with the
This stop consists of a spacer pin 215 which axially and non-rotatably connects the cover discs 213, 214 to one another. This spacer pin 215
represents the arc-shaped long hole 216 in the driven disc 230.
It extends through the In FIG. 9, a characteristic line 26 with a steep slope continues from a flat central characteristic line 261.
2 shows the operating state after the rotation of the drive disk relative to the cover disk is locked.

In this embodiment as well, a friction ring 222 is disposed in the first variation range between the driving disc 212 and the driven disc 230;
3 is located between the drive disc and the inner cover disc 214. A further friction ring 242 is brought into contact with the driven disk 230 radially inside the damping spring 240 of the first damping stage. This friction ring 242 is pressed by a disk spring 245 via a pressure disk 244 which is non-rotatably connected to the outer cover disk. Therefore, when the driven disc 230 rotates with respect to the cover discs 213 and 214, the area between the friction ring 242 on the boss side of the driven disc and the driven disc 230 and the driving disc 212 Friction occurs in the area of the friction ring 222. As a second friction stage, the drive disk 212 is connected to the cover disk 2.
Friction ring 22 between the drive disc and the rear cover disc 214 when pivoted relative to 13, 214
Friction occurs in the range 3. Similarly, if an angular movement occurs between the driving and driven discs, friction will occur in the area of the friction ring 222 acting between the two discs. In the operating range represented by characteristic line 262 in the range between approximately 14° and 15.5° with a steep rise, the friction ring received between the driving and driven discs 222 and the area of the friction ring 242 on the driven side boss side. It is clear that this causes friction to be superimposed on the effectiveness of the damping spring in the entire operating range of the torsional vibration damper.

[Brief explanation of drawings]

The drawings show a plurality of embodiments of the present invention, in which FIG. 1 is a partial plan view showing a first embodiment of a torsional vibration damper having three damping stages, and FIG. 3 is a characteristic diagram showing the course of the rotation torque as a function of the rotation angle for the pulling and pushing sides; FIG. 4 is a diagram of the three-stage torsional vibration damper. A partial plan view of the second embodiment, FIG. 5 is a sectional view taken along the - line in FIG. 4, and FIG. 6 is a characteristic line corresponding to FIG. 3 of the torsional vibration damper of FIGS. 4 and 5. Figure 7 is a partial plan view of a two-stage torsional vibration damper, Figure 8 is a sectional view taken along the - line in Figure 7, and Figure 9 is a torsional vibration damper in Figures 7 and 8. FIG. 3 is a characteristic diagram corresponding to FIG. 3 of the device. 10... Torsional vibration damper, 11... Drive part, 1
2... Drive disk, 13, 14... Cover disk, 15...
Spacer pin, 16...long hole, 17, 18, 19...
Circumferential notch, 20... Damping spring, 22, 23... Friction ring, 24... Pressing disc, 25... Belleville spring, 26
...Division, 30... Driven disc, 32... Internal teeth, 33...
External tooth, 34... Driven shaft, 36, 37, 38... Circumferential notch, 40... Damping spring, 42, 43... Friction ring, 44... Pressing disk, 45... Belleville spring, 46... Tongue piece, 48... Load friction disk, 49...circumferential notch,
50... Damping spring, 51, 52... Circumferential notch, 5
3, 54...Circumferential notch, 56...Friction ring, 5
7... Tongue piece, 60... Characteristic line, 61... Characteristic line, 62...
Characteristic line, 110... Torsional vibration damper, 111... Drive part, 112... Drive disk, 113, 114... Cover disk, 115... Spacer pin, 116... Elongated hole, 117, 118, 119... Circumferential notch, 1
20... Damping spring, 122, 123... Friction ring,
124... Pressing disk, 125... Belleville spring, 130... Driven disk, 131... Boss flange, 132... Internal teeth, 136, 137, 138... Circumferential notch, 1
40... Damping spring, 150... Damping spring, 151,1
52...Circumferential notch, 160...Characteristic line, 161...
Characteristic line, 162 Characteristic line, 210 Torsional vibration damper, 211 Drive part, 212 Drive disk, 2
DESCRIPTION OF SYMBOLS 13,214...Cover disc, 215...Spacer pin, 216...Long hole, 217,218,219...Circumferential notch, 220...Dampening spring, 222,223
... Friction ring, 230 ... Driven disk, 232 ... Internal tooth, 234 ... Driven shaft, 236, 237, 238
... Circumferential notch, 240 ... Damping spring, 244 ... Pressing disk, 245 ... Belleville spring, 260 ... Characteristic line, 26
1...Characteristic line, 262...Characteristic line.

Claims (1)

Claims: 1 each having a drive disk and a driven disk received between cover disks which are axially and rotationally relatively immovably connected to each other;
The driving disc and the driven disc are movable in the circumferential direction relative to each other and each relative to the cover disc, and the driving disc and the driven disc are movable in the circumferential direction.
Via each damping spring group of circumferentially acting damping springs received in circumferential recesses distributed circumferentially in the cover disc, the drive disc and the driven disc, In a torsional vibration damper which is supported in the circumferential direction on the cover disk independently of each other, the drive disk 12, 112, 212 and the cover disk 13, 14, 113, 114;
3,214 and the cover disc 13,14;1
13, 114; 213, 214 and driven disk 3
0, 130, 230, and friction stages 23, 4 which act on the basis of the relative movement between these discs.
2; A torsional vibration damper, characterized in that one each of 223 and 242 is provided. 2 damping springs 20, 40, 50 of each damping spring group;
12. The torsional vibration damper according to claim 1, wherein 120, 140, 150; 220, 240 are connected in parallel with each other and both damping spring groups are connected in series with each other. 3 damping springs 20, 40, 50 of each damping spring group;
The torsional vibration damper according to claim 1 or 2, wherein 120, 140, 150; 220, 240 have the same spring hardness. 4 Damping springs 20, 40, 5 of different damping spring groups
Torsional vibration damper according to any one of claims 1 to 3, wherein 0; 120, 140, 150; 220, 240 have different spring hardnesses. 5 Cover disks 13, 14; 113, 114; 213, of driving disks 12, 112, 212 and/or driven disks 30, 130, 230;
The relative movement relative to 214 is at least one circumferentially acting stop 15, 16; 115,
116; 215, 216 to a predetermined rotation angle. 6. The stopper 15, 115, 215 is fixedly connected to the cover disc and the drive disc 12, 1
12, 212 and driven discs 30, 130, 23
6. The torsional vibration damper according to claim 5, wherein the torsional vibration damper is engaged with an arcuate notch (16, 116, 216) extending over a predetermined angle at or at 0.0. 7. A pin 15 that connects the cover discs to each other, the stopper passing axially through the arc-shaped notch 16, 116, 216 in the driving disc 12, 112, 212 or the driven disc 30, 130, 230; 1
15,215. The torsional vibration damper of claim 6. 8 Damping spring 2 of at least one damping spring group
0,120,220 or 40,140,24
8. A torsional vibration damper according to any one of claims 1 to 7, wherein the torsional vibration damper is preloaded to 0. 9 Drive disc 12, 112 and cover disc 13, 1
4; Between 113 and 114 or cover disc 1
3, 14; 113, 114 and driven disk 30, 1
A damping spring group is provided which becomes active only after the rotation between the two ends of the spring reaches a predetermined angle of rotation.
A torsional vibration damper according to any one of claims 1 to 8. 10 Damping springs 50, 150 of the damping spring group, which act only after a predetermined rotation angle is reached, are non-rotatably connected to the cover disks 13, 14; 153, and the notches 53, 153 are received in the driving discs 12, 112 or the driven discs 30, 13.
extending in the circumferential direction beyond the length of the damping springs of the damping spring group by a predetermined extent on both sides at 0;
A torsional vibration damper according to claim 9. 11. A load friction stage is provided between the drive disc 12 and the cover disc and/or between the cover disc and the driven disc 30, which becomes active only after a predetermined rotation angle is reached. A torsional vibration damper according to any one of claims 1 to 10. 12 Drive disk 112, 212 and driven disk 13
Claims 1 to 11 are provided with a friction stage acting directly between the
A torsional vibration damper according to any one of the preceding clauses. 13 in each friction stage at least one friction ring 22, 23, 42, 43, 56 pressed against the friction surface of a disc movable relative to each other in the circumferential direction;
22; 222, 223, 242 are arranged. Torsional vibration damper according to any one of claims 1 to 12. 14 A circle in which the friction rings in at least one friction stage are movable relative to one another in the circumferential direction via pressure discs 24, 44, 48; 124; 244 which are mounted with limited axial movement. A patent in which the pressure disc is pressed against one friction surface of the plates, while the pressure disc is loaded with a spring force and is non-rotatably supported on the other of the cooperating discs in the friction stage. A torsional vibration damper according to claim 13. 15 The loaded friction stage has a spring-loaded friction disc 48 which is axially movable between discs movable relative to each other in the circumferential direction and between these discs. It is rotatably supported on one side by a predetermined rotation angle without friction, but after advancing by a predetermined rotation angle, it is unrotatably coupled to the disk in the respective rotation direction. , a torsional vibration damper according to claim 13. 16 One disc spring 25, 45; 125; 2 for crimping the pressure disc or friction disc in each case
16. The torsional vibration damper according to claim 14 or 15, wherein the torsional vibration damper uses a vibration damper having a diameter of 45.