RU2235930C2 - Device for damping torsional vibration - Google Patents

Abstract

FIELD: mechanical engineering.

SUBSTANCE: device has first link (133) for transmitting torque between the primary member (102) of the flywheel and inlet member (120), and second link (111a) for transmitting torque between the outlet member (121) and secondary member (103) of the flywheel. The space between inlet (120) and outlet (121) members receives accumulator (107) of energy made of a spring which is located at a less radial distance from the axis than that of each of the two links (133), 111a) for transmitting torque. For receiving accumulators of energy (107), input (120) and/or outlet (121) members have two ports.

EFFECT: decreased sizes of flywheel.

73 cl, 19 dwg

Description

The invention relates to a device for damping torsional vibrations, comprising input and output parts mounted rotatably with respect to each other.

The present invention was based on the task of creating a device of the kind described above, which can be manufactured in a particularly simple, rational and economical manner, so that they can also be used in large-volume engines with a small displacement. In addition, it is necessary to reduce wear and, thereby, increase the service life of such devices, and this is also in the dry execution of the device. Another objective of the invention is to improve the functioning or principle of operation of such devices.

According to one feature of the invention, this problem can be solved due to the fact that the input and output parts of the device contain at least one element of the flywheel, between which there is a damper. A particularly preferred way the device can be used between the engine and the gearbox of the car, the input part can be connected to the engine and the output part to the gearbox. In this case, it may be especially appropriate if the output part carries friction clutch, and a clutch disc is placed between the friction surface of this output part and the friction clutch pressure plate. This clutch disc can be connected directly to the input shaft of the gearbox.

For the assembly and operation of the device according to the invention, it may be particularly advantageous if it contains two flywheel elements, and the damper provided between them contains at least a first coupling for transmitting torque between the input part and at least one input element and the second communication for transmitting torque between the output element and the output part. This kinematic connection can be rigid, i.e., for example, by means of a geometric closure, or pliable, i.e., e.g., by means of a frictional closure.

For the assembly and operation of the device, it may be particularly advantageous if at least one energy accumulator is located at a shorter distance from the axis than each of the two torque transmission links, which can preferably be formed by coil springs. The kinematic relationships of the input and output elements with the corresponding elements of the flywheel can be preferably radially offset relative to each other. Moreover, of both elements of the absorber, one can be kinematically connected with the corresponding element of the flywheel with a frictional closure, and the other with a geometric closure, and the connection with the frictional closure can be located radially outside the connection with the geometric closure. In some cases, a reverse arrangement may be appropriate. By connecting with a frictional closure, the transmitted torque between the two elements of the flywheel can be easily limited. The limitation of the torque can be carried out through a safety friction clutch with at least one slip level.

For the assembly of the device and its functioning, it may be further preferable if one of the two elements of the flywheel, namely the input and output, is formed by a disk-shaped part, and the other by at least two annular parts rigidly connected to each other, which are axially at least partially placed between each other a disk-shaped part. In this case, the ring-shaped parts are mounted at a certain axial distance from each other by means of spacers. In this case, the spacers can pass through oblong in the direction of the periphery of the recess of the disk-shaped part, due to which the necessary backlash for the damper can be formed.

Although the secondary or gearbox side of the flywheel element can be made in the form of a massive part supported radially inside directly by the support, in many cases it is preferable if at least one of the ring-shaped parts or the disk-shaped part serves to radially support both elements of the flywheel. For this, one of the ring-shaped parts or the disk-shaped part can be provided radially inside with an axial protrusion, through which the bearing is supported. In this case, the axial protrusion can be made directly radially inside in one piece with the corresponding part or it can be formed as a separate part, fixed accordingly. The fastening can be carried out in this case, for example, by means of a rivet or welded joint.

For supporting both elements of the flywheel with respect to each other, it may also be preferable if at least one of them is provided radially inside with an axial protrusion for supporting both elements. This axial protrusion can be made in one piece with the corresponding element of the flywheel. For this, however, a separate part, coaxially connected to the corresponding element of the flywheel, can also find application in a preferred way. For the operation of the blanking device, it may be particularly advantageous if at least one hysteresis device is provided between the two elements of the flywheel, acting in parallel with the energy accumulators. This hysteresis device can be formed simply by a friction device. For assembly of the device, it may be preferable if the hysteresis device is located radially outside the energy accumulators. To save space, the hysteresis device can be located radially between the kinematic connections of the input and output elements of the damper with the corresponding element of the flywheel. The hysteresis device may suitably be located radially outside the connection of the disk-shaped part and / or the ring-shaped parts with one of the elements of the flywheel. In some cases, it may be appropriate if the hysteresis device is at least substantially radially outside the structural space formed by both annular parts. In some cases, it may be preferable, however, if the hysteresis device is located inside the structural space formed by both ring-shaped parts, and in this case, in addition, it may be preferable if the hysteresis device is located radially outside the energy accumulators. The hysteresis device can be performed without backlash, and, however, in most cases it is especially preferable if the hysteresis device has a backlash, due to which it can be inactive in a certain range of rotation angles. In a preferred manner, the hysteresis device can create so-called inertial friction. This means, therefore, that when reversing the direction of rotation between both elements of the flywheel, the hysteresis device remains inactive at a certain angle of rotation. The hysteresis device can, however, also interact with at least one energy accumulator, which causes at least a partial return of the friction elements of the hysteresis device, as a result of which, when reversing the direction of rotation, the hysteresis effect can be saved.

According to an improvement of the invention, the hysteresis device can be configured to create hysteresis or friction damping that varies in angle of rotation, and it may be preferable if, as the angle of rotation increases, based on a neutral or defined position, the hysteresis or friction effect increases. The latter can be carried out, for example, by means of ramp ramps, which are molded onto the parts forming the friction device. Such slopes can advantageously be provided on frictionally engaged parts, which slopes can be formed directly by the friction surfaces.

To ensure the compact design of the device, in particular in the radial direction, it can be especially appropriate if the disk-shaped part extends radially inward at most to the outer sections of the fastening means for mounting the device on the motor output shaft. Energy accumulators may advantageously be placed in the recesses of the disk-shaped part, made in the radially internal sections of this part. To save radial structural space, it is particularly preferable if these recesses are open radially inward. It is further preferred that at least one of the annular parts extends radially inward at most to the radially external portions of the fastening means, since this also ensures a compact design.

For the operation and assembly of the device, it may be further preferable if one flywheel element connected to the engine has a radial flange-like portion, on which a disk-shaped part is fixed by means of radially outer sections, at least the radial sections of the flange-shaped portion and the disk-shaped part are axially removed from each other , and in the free space formed due to this, a hysteresis device is located. To this end, spacers may be provided at least in the area of the attachment points between the flange-shaped portion and the disk-shaped part. The spacers can be formed in this case by at least one annular additional mass, which can be preferably made in the form of a sheet shaped part.

The input or output element of the absorber can be kinematically coupled to the flywheel element in a preferred manner by means of at least a two-stage torque limiter. The individual stages of the torque limiter can advantageously act in parallel with each other, at least one of the stages having a slip moment which is lower than the rated torque of the drive motor. The sum of the torques transmitted by the individual steps ensures, however, the transmission of the torque given by the engine without slipping.

It may further be preferable if the torque limiter is located at a radial height of the friction surface of another, i.e. from the side of the gearbox, flywheel element. For assembling the device, it may be preferable if the torque limiter contains at least one energy accumulator tensioned to create a creeping moment, in particular a disk spring part, and this energy accumulator is at least partially pressed against the friction clutch another flywheel element.

For assembly and installation of the device, it may be particularly preferred if the friction clutch and the intermediate clutch disc are made in the form of a node with the output element of the damper. With this design, the damper is first connected to the flywheel element on the engine side, and then assembled together with another flywheel element. It may be particularly preferable if recesses are made in one element of the flywheel to obtain connections between the output element of the damper and another element of the flywheel. These compounds can be made advantageously by rivets. For assembly of the device, it may be preferable if the connecting elements are located on a radial section of the friction surface of another element of the flywheel.

To ensure the compact design of the device, it can be especially preferred if, when viewed in a radial direction from the inside out, the assembly sequence is as follows:

- radial support between both elements of the flywheel;

- fasteners for connecting to the engine;

- energy accumulators;

- torque limiter and / or hysteresis device;

- at least one axial protrusion on the flywheel element from the engine side.

Preferably, the flywheel element on the engine side can have at least one mass ring, which can be formed preferably by folding sheet material, to increase the inertial mass radially outside. However, a mass ring may also be provided, which is integral with the flywheel element on the engine side, which has a radially inwardly directed flange portion with radially inward recesses for introducing fixing means, in particular screws. It may also be preferable if the flywheel element on the engine side contains a mass ring radially outwardly bearing a starting gear ring and / or marks for controlling the engine. The ring gear and / or marks can be made integrally with the corresponding mass ring.

It may be particularly advantageous if the hysteresis device is provided with an axially-tensioned energy accumulator, for example a part in the form of a disk spring, which axially presses both elements of the flywheel against each other. This is preferable, in particular when using a plain bearing, since in this case no additional axial safety device is required. The hysteresis device can be made with the possibility of acting on the entire rotation angle between both elements of the flywheel and creating the so-called main friction.

It may be especially suitable for assembling the device if at least the other element of the flywheel and the damper are made with the possibility of mounting in the form of a pre-assembled unit with the element of the flywheel on the engine side. Preferably, the assembly may further comprise a friction clutch and a clutch disc.

The hysteresis device acting between the two elements of the flywheel may advantageously comprise at least one friction ring radially positioned externally by means of the annular surface of one of the parts. Instead of a single closed friction ring, individual segment-shaped friction elements can also be used, radially directed radially from the outside by the ring-shaped surface of one of the parts and resting on this surface, if necessary, under the action of centrifugal force, due to which friction, depending on the centrifugal force, can be created.

If the device contains a torque limiter, it may be particularly preferred if it contains an axially-tensioned part in the form of a disk spring or membrane, which at least partially supports the axial friction clutch casing and axially captures the friction clutch actuating force. In this case, the casing can be screwed on with a disc spring part. By maintaining the actuating force of the friction clutch with an axially tensioned part, the torque transmitted by the torque limiter can be changed depending on the engagement of the friction clutch. This can, in particular, achieve a reduction in the transmitted torque with the friction clutch switched off.

For mounting the device, it may be especially preferred if the flywheel element having a friction surface, together with the friction clutch and the clutch disc, forms a pre-assembled assembly. The clutch casing and another element of the flywheel can be made with the possibility of connection with screws screwed in from the side facing away from the friction surface of another element of the flywheel. To obtain the connection, the clutch casing may have threaded holes for screws directly. Corresponding threads may also be formed by set nuts. Such a pre-assembled assembly may be adapted to be connected to the damper outlet element in a preferred manner with screws axially screwed in from the clutch side.

It may be particularly preferable if one of the ring-shaped parts forming the input element of the absorber has both a radially external and a radial inside the energy accumulators a strong connection with the flywheel element from the engine side, since this can provide a rigid, at least axially direction design. In this case, the annular part can be fixed radially outside on the corresponding element of the flywheel by means of riveted joints and pulled together with this element of the flywheel radially inside by fastening means for mounting the device on the engine.

For assembling the device, it may be further preferable if the torque limiter located between the output element of the damper and the other element of the flywheel contains at least one axially tensioned energy accumulator in the form of a disk spring or membrane, which is made with the possibility of at least partial weakening when dismantling the friction clutch and re-tensioning when installing the friction clutch. Due to the similar design, when dismantling the friction clutch, the torque limiter cannot transmit any or almost no torque, and thus, the flywheel element from the gearbox side cannot be rotated relative to the flywheel element from the engine side. The latter is preferable, in particular, when the fastening means for mounting the assembly on the engine output shaft are accessible or can be screwed in only through holes made in the flywheel element from the gearbox side. It has also been found to be particularly advantageous for the invention if five energy accumulators, which can be formed by coil springs, are provided for at least approximately the same diameter. The use of five energy accumulators distributed in the direction of the periphery with a radial overlap has the advantage that a sufficiently large power or a sufficiently large volume of springs can be provided to provide at least acceptable damping of torsional vibrations, while at the same time the details can be made sufficiently rigid with respect to their strength with the possibility of transmitting also relatively high torque. A number of energy storage units of five is preferred, in particular when they are located on a small diameter. This small diameter is ensured in the embodiment according to the invention due to the fact that the energy accumulators are provided very close to the fastening means for mounting the assembly on or near the engine. With this arrangement, it is preferable if the support between both elements of the flywheel is provided radially inside these fastening means.

The invention is explained in more detail using figures 1-17, depicting:

- figure 1: General view of a torsional vibration damper made according to the invention with breaks;

- figure 2: section along the line II-II of figure 1;

- Fig.3-13a: partial sections of other dampers of torsional vibrations according to the invention;

- Fig.14: a partial section along the line XIV-XIV Fig.13;

- Fig.17-17: options for a torsional vibration damper according to the invention.

The device for damping torsional vibrations depicted in Figs. 1 and 2 is formed by the so-called two-mass flywheel 1. This two-mass flywheel 1 includes a primary mass 2 fixed to the output shaft of an engine, in particular an internal combustion engine of a car, and a secondary mass 3. Masses 2, 3 mounted coaxially and with the ability to perform rotational movements together with each other and with respect to each other around the axis of rotation 5 by means of a support 4. In the embodiment of FIGS. 1 and 2, the support 4 includes a rolling bearing 6, providing both both the axial and axial movements of the secondary mass 3 relative to the primary mass 2.

The primary mass 2 is kinematically connected with the secondary mass 3 through a damper 8 containing compressible energy accumulators 7.

On the secondary mass 3, a friction clutch is mounted through the clutch disc. The secondary mass 3 has a friction surface 9 for the friction lining of the clutch disc and radially outside the attachment point 10. In the area of the attachment points 10, threaded holes 11 are made for screwing the clutch casing. In the depicted exemplary embodiment, positioning pins 12 are provided on the outer periphery of the secondary flywheel 3, which, when mounting the friction clutch, enter the corresponding holes of the clutch casing.

In the illustrated example, both the primary 2 and secondary 3 flywheels are massive, mainly made of castings. At least one of the masses 2, 3 can, however, at least partially also consist of sheet parts.

The primary fly mass 2 carries outside the starting gear ring 13 and is provided radially outside with an axial annular protrusion 14, forming an inertial mass. Inside the axial protrusion 14 is placed secondary flywheel 3.

Radially inside, the primary flywheel mass 2 is provided with an axial protrusion 15, on which a bearing 6 is mounted, also located in the central recess 16 of the secondary mass 3. The inner axial protrusion 15 is formed in the illustrated embodiment by a separate part 17, which contains a radial flange section adjacent to the axial protrusion 15 18. In the depicted exemplary embodiment, the axial protrusion 15 passes through the central recess of the primary mass 2, and the flange section 18 covers behind the primary mass 2 on the side facing away from the damper 8. On the radially inner sections of the primary mass 2 and the flange section 18, recesses are made through which the fastening means axially pass in the form of screws 19. When the quenching device 1 is screwed onto the engine output shaft, the flange section 18 is axially clamped between the end surface of the output shaft and the radially inner sections of the primary mass 2. Part 17 can, however, be made and positioned so that the radial flange section 18 is sandwiched between the radially inner sections of the primary mass 2 and the heads nt, i.e. on the other axial side of the primary mass 2, and in this case, changes may be required on the radially internal sections of the primary mass 2 and, if necessary, on the adjacent parts.

In the illustrated embodiment, the primary mass 2 forms the input, and the secondary mass 3 forms the output of the quenching device 1.

The damper 8 contains the input 20 and output 21 elements. The input element 20 is formed by a disk or flange-like part. The output element 21 comprises two disk- or ring-shaped parts 22, 23 located axially spaced apart from each other, between which, at least partially, a flange-like part 20 is placed.

Both ring-shaped parts 22, 23 are held at an axial distance from each other and are firmly connected to each other by spacers in the form of fingers or rivet elements 24. The ring-shaped part 23 is adjacent directly to the rear side of the secondary mass 3. In the secondary mass 3 there are made countersink through holes 25 serving for connecting the annular parts 22, 23 by means of rivet elements 24 with a secondary mass 3. To do this, the rivet elements 24 axially pass axial protrusion 26 through the through holes 25, and on the protrusion groin 26 is molded head 27, located on the countersink portion of the through hole 25. In the illustrated embodiment, rivet elements 24 are located at least partially on the radial portion of the friction surface 9. The back side of the secondary mass 3 is made in such a way that, if you look around the circumference of at least between the joints 28, radial channels 29 are formed between the secondary mass 3 and the adjacent annular part 23. Radially inside the joints 28 in the secondary mass 3 are made axial passages 30, which, among other things, are also connected with the channels 29, due to which the flow of cooling air can circulate on the rear side of the secondary mass 3.

The primary mass 2 has recesses 31, which serve to obtain sites 28 connections, i.e. rivet joints 28. A flow of cooling air can also circulate through these recesses, which is indicated by arrows without reference numbers.

The joints 32 between the flange-like part 20 and the primary mass 2 are located radially outside the joints 28. The connection between the primary mass 2 and the flange-like part 20 is made by means of riveted joints 33. The flange-shaped part 20 has countersinks 34 in which corresponding rivet heads of the riveted joints 33 are placed, due to which an axially compact construction is possible.

The installation of the damper 8 between both masses 2, 3 is carried out due to the fact that rivets 32 are first made between the flange-like part 20 and the primary mass 2, and then the output element 21 with the secondary mass is riveted, for which, as already mentioned, recesses 31 are required.

As can be seen from figure 1, the axial passages 30 are formed by elongated slotted recesses, which are made in the area of the energy accumulators tangentially or in the direction of the periphery in the form of coil springs 7. In the illustrated embodiment, five energy accumulators 7 are provided uniformly distributed around the periphery. The coil springs 7 are made straight in the illustrated example. The use of five energy accumulators 7 turned out to be particularly preferred with respect to the spring power placed in the system. The use of five coil springs 7 provides, on the one hand, a sufficiently large angle of rotation between the primary 2 and secondary 3 masses for good damping of torsional vibrations, and on the other hand, the parts accommodating the springs 7, in particular, 20, 22, 23 can be due to This is made rigid enough to transmit a relatively high torque.

As can be seen further in combination with FIG. 1, the spacers or rivets 24 pass axially through the elongated recesses 35 of the flange-like part 20. In the illustrated embodiment, segmented or arched recesses 35 extend in the extent of the energy accumulators 7, namely, radially outside them. The recesses 35 overlap, therefore, when viewed in the axial direction, with axial passages 30, that is, when viewed in the radial direction of the device 1, they extend at least approximately in the same angular range as the passages 30.

The rotation limit in the angle between the input 20 and output 21 elements can occur in the block by springs 7 or due to the stop of the rivet elements 24 at the ends of the recesses 35.

The flange-like part 20, protruding radially outwardly from both ring-shaped parts 22, 23, has a radially inside recess or cut-out 36 for accommodating energy accumulators 7. These recesses or cutouts 36 are thus made so that they are open radially inward, whereby between the two adjacent springs 7 only the jumpers or arms 37 are directed radially inwardly. The flange-like part 20 or arms 37 extend radially very close to the screw heads 19a. As can be seen, in particular, from FIG. 2, when viewed in the radial direction, the coil springs 7 are also practically adjacent to the screw heads 19a, i.e. located at a relatively short distance from them. The lateral disks or ring-shaped parts 22, 23 also have cutouts or recesses 38, 39 for the springs 7. In the depicted exemplary embodiment, the recesses 38, 39 are closed radially inward, namely due to jumpers 38a, 39a of a relatively small radial width. These jumpers 38a, 39a provide the necessary strength to the disks 22, 23 made of relatively thin material in order to ensure the transmission of a relatively high torque. The lateral disks 22, 23 can, however, be made in such a way that the recesses 38, 39 are open radially inward, namely, similar to the cutouts 36 of the part 20.

Between the primary 2 and secondary 3 masses there is a hysteresis device 40, which in the illustrated embodiment is formed by a friction device. In the depicted exemplary embodiment, the hysteresis device 40 is located radially between the joints 28 and 32 axially between the flange-like part 20 and the radial sections 41 of the primary mass 2. In order to ensure sufficient axial free space for this, an axial ledge 42 is made in the primary mass 2, forming here a cylindrical surface 43. The friction device includes, as shown, either a friction ring 44, or individual segmented friction pads 44 distributed over the periphery, which can also be arranged annularly. When using separate friction pads or friction shoes between them, when viewed in the direction of the periphery, there may also be gaps.

The friction ring or friction pads 44 are made and arranged to be radially supported on the cylindrical surface 43. Due to this, in particular when using separate friction pads, friction can be created depending on the centrifugal force or speed. A similar centrifugal force-dependent friction can occur, however, when using a closed friction ring 44, since due to the intrinsic elasticity of the material, the friction ring can expand under the action of centrifugal force. In the depicted exemplary embodiment, the friction ring 44 is pressed against the flange-like part 20 by means of a part 45 in the form of a Belleville spring tensioned between the friction ring 44 and the radial section 41 of the primary mass 2, as a result of which it is clamped and can only rotate due to the overlap of the frictional closure resulting from this . The axial arrangement of the friction element 44 and the energy accumulator 45 may, however, also be reversed.

The control or rotation of the friction element in the form of a friction ring 44 is carried out by means of a disk-shaped part 22. As can be seen, in particular, from figure 1, the disk-shaped part 22 has for this purpose a plurality of protrusions or consoles 46 located at the periphery which radially coincide respectively with the bulges or protrusions 47 of the friction ring 44. The distance along the angle between the protrusions 47 and the extension along the angle of the consoles 46 are agreed in the illustrated embodiment in such a way that between the consoles 46 and the protrusions 47 there is a play of 48 turns. In this case, the backlash 48 of the rotation hysteresis device 40 is inactive when reversing the direction of rotation between the two masses 2, 3. There is, therefore, the so-called inertial friction. As can be seen further in combination with figure 1, both ring-shaped parts 22, 23 are made equally, and installed mirror-symmetrical. The annular part therefore contains, radially outside the cantilever 46, which does not, however, perform a control function here.

The fastening means 19 can advantageously be integrated into the blanking device 1, so that the screws 19 need not be specially prepared at the automobile plant, and in addition there is no additional cost for the placement and positioning of these screws 19. The fastening means or screws 19 can be tightened through recesses or passages 49 made in the secondary mass 3.

In the illustrated embodiment, the annular parts 22, 23 are kinematically connected with the secondary mass 3, and the flange-shaped part 20 is connected with the primary mass 2. The kinematic connection of these parts 20, 22, 23 with masses 2, 3 can be realized, however, and vice versa. Further, the joints 32, 28, when viewed in the radial direction, can also be reversed, and for this it is preferable if at least one of the ring-shaped parts 22, 23 in this case has a large radially external extension, and the flange-shaped part is made in radial direction, respectively, less. Since the joints 32 are then radially inside the joints 28, at least one of the ring-shaped parts 22, 23 must have corresponding elongated recesses (similar to the recesses 35 of the part 20) in order to provide the necessary play of rotation for the corresponding fasteners or rivet joints .

According to another embodiment (not shown), the joints 32 and 28 or the rivet joints 33 and 24 can be provided at least at approximately the same diameter, in which case the connecting means 33 are respectively offset in the periphery relative to the connecting means 24. B In such an embodiment, it is preferable if both the flange-like part 20 and the ring-shaped parts 22, 23 contain radially outside the cantilevers or protrusions in the area of which connections 28, 32 are provided. Between the cantilevers of the part 20 and the cantilever The parts of the parts 22, 23 should be the corresponding crank play, which at least corresponds to the crank play provided by the damper 8 between the two masses 2, 3.

In the depicted exemplary embodiment, radially outside the connection points 28, 32, the preferred places 10 are provided for securing the friction clutch.

By using the relatively small diameter of the support 4 and the location of the fastening means 19 at a small radial distance around this support 4, as well as the location of the energy accumulators 7 at a small radial distance from the fastening means 19, a compact design of the blanking device 1 is provided, at least in the radial direction . To reduce the radial and axial dimensions of the quenching device 1, it is further preferable to arrange the locations 28, 32 of the connections radially outside the energy accumulators 7. The hysteresis device 40 also practically does not require additional structural space, since it is located in the place where at least an axial structural space is necessary for other parts, for example struts 24 and ring-shaped part 22. In addition, by arranging the friction device 40 on a large diameter, it is possible to create high friction hysteresis without the need to take into account the high wear of the corresponding parts, since the specific pressure or tension can be maintained at least within an acceptable value.

The torque transmission device 101 shown in FIG. 3 consists of a primary 102 and a secondary 103 flywheel elements mounted to rotate with respect to each other by a support 104 against the action of the damper 108. The support 104 includes a sliding bearing 106, which provides radial displacement and axial bearing of both flywheel elements 102, 103. In the illustrated example, the bearing 106 is made in the form of a sleeve 106a with an annular radial protrusion 106b. Acting as an axial support, the annular protrusion 106b can also be performed separately from the sleeve portion 10 6a and is provided on another radial diameter portion between two parts that, on the one hand, are connected to the first element 102 and, on the other hand, to the second flywheel element 103 .

The absorber 108, as shown by comparison with FIG. 2, has a structure similar to the absorber 8, i.e. it contains an input element formed by a flange-like part 120, which is radially outside rigidly connected by means of rivets to the primary flywheel element 102, as well as two side disks 122, 123 kinematically connected to the secondary flywheel element 103 and rigidly connected to each other by means of rivet elements 124. These the rivet elements 124 do not serve here, however, for a rigid connection with the secondary element 103 of the flywheel, since this connection is carried out by screws 111a, serving simultaneously for fixed Figure 4 of the clutch module 150. The joints of both the output member 121 and the friction clutch 151 with the secondary flywheel member 103 are therefore located at least approximately the same diameter and radially outwardly displaced relative to the joints 133.

The annular part 123 has pocket-like bulges 139 for accommodating energy storage batteries 107. Lateral, when viewed in the direction of the periphery, sections of the pockets 139, also extending in the axial direction, form support or load zones for the energy accumulators 107. The implementation of the closed pocket-like bulges 139 gives rigidity to the annular part 123. The annular part 123 further serves to support the clutch module 150, which consists of at least a flywheel element 103, a clutch disc 168 and a friction clutch 151. For this, the annular part 123 is provided radially inside an annular protrusion 152 with an inner cylindrical surface 153 that accommodates the sleeve-like portion 106a of the sliding bearing 106 and is connected to it either rigidly or with the possibility of sliding. The radial annular section 106b of the bearing 106 is axially clamped between the front surface 154 of the axial protrusion 152 and the radial section 155 forming the axial protrusion 115 of the part 117. The part 117 is made and is located similarly to the part 17 in FIG. 2.

In the depicted exemplary embodiment, the axial protrusion 152 is formed by an annular part 156 of an L-shaped section. The radial annular section 157 adjacent to the axial protrusion 152 is rigidly connected to the side disk 123, namely, by rivet joints 158. The rivet elements necessary for this in the illustrated embodiment are molded integrally from the radial section 157. Additionally or alternatively, parts 123, 156 can also be welded together.

The primary element 102 of the flywheel is made in the form of a sheet structure and includes a sheet bearing part 159, centered on the part 117, an annular flange-like portion 160 and an axial sleeve-shaped portion 161 adjacent to it radially outside, the radial portion 160 is provided with an axial protrusion 142, the hysteresis radially inside of which device 140 is located similarly to the hysteresis device 40 in FIG.

Inside the sleeve-like portion or axial protrusion 161, a clutch module 150 is placed axially gripped from above at least partially by the axial protrusion 161.

To increase the moment of inertia of the primary flywheel element 102, additional inertial masses 162, 163 are provided on the sheet bearing part 159. The inertial mass 162 is formed by an initially flat annular sheet-like part, and then folded perpendicular to the plane, i.e. in the axial direction, with the formation of two parallel to each other layers 162a, 162b. The annular inertial mass 162 formed as a result of this is placed and fixed radially outside on the axial protrusion 161, namely, mainly by welding and / or friction closure. In the depicted exemplary embodiment, the inertial mass 162 simultaneously forms marks 164 used to control the engine, for example, the moment of ignition and / or injection. The inertial mass 163 is provided on the side of the support part 159 facing the engine and is also initially formed by a flat ring-shaped sheet part, which is then folded accordingly, namely in the radial direction, with the formation of three layers lying one on the other 163a, 163b, 163c, at least partial radial overlap. The radially oriented inertial mass 163 comprises a starting gear ring 113 radially outside integrally formed with it. At least the sections of the inertial mass 163 forming the gear ring 113 are mainly hardened, for example by inductive hardening. The inertial mass 163 is connected to the supporting part 159 by means of riveted joints 133, which at the same time connect the flange-like part 120 of the damper 108 to the supporting part 159.

In contrast to the embodiment of FIG. 2, in the embodiment of FIG. 3, the friction part 109a of the flywheel is not itself centered, therefore, on the bearing 106, and this centering is carried out, as already mentioned, by the part 123 of the damper 108.

As can be seen from figure 4, the clutch module 150 consists of a friction clutch 151, which is firmly connected by screws 165 to the ring-shaped mass 103a of the secondary flywheel element 103. Between the friction surfaces of part 103a and the clutch pressure plate 166, friction linings 167 of the clutch plate 168 are sandwiched. A Belleville spring 170 is tensioned between the casing 168 and the pressure plate 166. The screws 165 are placed on the rear side of the annular back pressure disk 103a and screwed onto the casing 169. The screws 111a and 165 are therefore screwed in from axially opposite directions.

The centering of the clutch casing 169 relative to the counter-pressure disk 103a can be carried out by means of screws 165, and in this case they are made in the form of fitting screws. The screws 165 comprise, therefore, a guide rod adjacent to the head, which is positioned and positioned in the corresponding recess of the back pressure disk 103 a.

However, normal screws 165 can also be used, in which case fitting pins 165a can be further provided, as shown in FIG. 4, for centering the position of the clutch housing 169 relative to the back pressure disk 103a.

As can be seen from Figs. 3 and 4, the pressure disk 166 has on its radially outer portion radially inwardly convexities 166a, 166b that radially intersect with the friction linings 167 and create a structural space for the sections of the casing 169 that accommodate the fixing screws 111a and 165. This a particularly small make-up diameter is provided, which, in turn, provides a radially compact design of the friction clutch 151 or the entire damping device 101. As can be seen from FIG. 3, the protuberances 166a of the pressure plate 166 can also accommodate portions of the screw heads 111a.

The blanking device 201 shown in FIG. 5 is similar to the device 101 in FIG. 101 in FIG. 3, so only fundamental differences should be described. Between the axial protrusion 215 of the primary flywheel element 202 and the axial protrusion 252 there is a rolling bearing 206, made similar to the rolling bearing 6 in FIG. 2. The rivet elements 224 are made similarly to the rivet elements 24 in FIG. 2 and, unlike the rivet elements 124 in FIG. 3, serve simultaneously to connect the friction surface 209 of the annular part 203a of the secondary flywheel element 203 with the output damper element 221.

Friction clutch 251, similarly to that shown in FIG. 3, is screwed onto part 270, which, however, is not integral with the part of output element 221, but forms a separate part in comparison with the annular side disk 223. The ring-shaped part 270 has a radially external ring-shaped screwing section 271 on which threaded holes for screws 211a are made and a radially internal ring-shaped section 272 axially sandwiched between the part 203a and the radially outer section 223a of the disk-shaped part 223, whereby a frictional rotational connection with the power is formed a short between the part 270 and the flywheel element 203. In order to create a frictional closure, the at least radially outer portion 223a of the side disc 223 and / or the annular part 270 are preferably elastic deformed and tensioned. The part 270 is therefore installed with the possibility of rotation relative to the part 203a of the flywheel element 203 against the mentioned frictional closure, so that in the presence of unacceptably high moments and, if necessary, depending on the operating state of the friction clutch 251, the part 270 together with the friction clutch 251 can slip relative to annular part 203a, which leads to a limitation of the transmitted torque. Since in the on state of the friction clutch 251, the disk spring 273 tensioned between the pressure plate 266 and the clutch cover 269 creates a significantly greater axial force acting on the part 270 than in the off state of the friction clutch 251, the torque transmitted between the annular part 203a and the friction clutch 251, more than the last off. The position of the cup spring 273 in the off state of the friction clutch 251 is shown by a dashed line. The quenching device 201 is designed in such a way that, at least when the friction clutch 251 is turned off and when torque fluctuations occur, lying, for example, above the rated engine torque, the friction clutch 251 with the part 270 mounted on it can slip relative to the annular part 203a of the secondary flywheel element 203.

Figure 6 shows another embodiment of the support 304, and the placement of the rolling bearing 306 on the axial protrusion 315 is carried out in the same way as described in connection with figures 2 and 5. The outer ring 306b of the bearing is located inside the axial protrusion 352 formed by the annular part 356 L-shaped section. The radial annular portion 355, similar to the radial portion 156 in FIG. 3, is rigidly connected to the annular side disc 323 by riveted joints 358. The joint can also be made by welding. A radial portion 355 is provided on the side of the disk 323 facing the screws 319. The disk 323 has radially inside segments 323a that extend radially inward beyond the axial protrusion 356 and serve as axial support for the outer bearing ring 306b. Through these segments 323a, the secondary flywheel element is axially supported by the bearing 306 and thereby relative to the primary flywheel element. The radial support of the secondary element of the flywheel is carried out by means of an axial protrusion 352.

The extinguishing device 401 shown in Fig. 7 contains primary 402 and secondary 403 flywheel elements, which, as was described similarly in conjunction with Fig. 3, are directed coaxially to each other and axially supported by a support 406, as well as kinematically connected by the damper 408. The primary element 402 of the flywheel also comprises a carrier part 459 made of sheet material with an annular flange-shaped portion 460 made in one piece with an axial sleeve adjacent to it radially outside 461. A flange-like portion 460 carries radially outside two additional inertial masses 462, 463, which are provided on both sides of the flange-shaped portion 460 and are connected with rivets 433. Inertial masses 462, 463 formed by folding the original flat sheet material. The annular inertial mass 462 has an L-shaped cross-section, the radial flange 462a consists of two layers lying on top of each other, and the axial flange 462b is made single-layer. An additional inertial mass 462 is provided radially inside the sleeve-like axial protrusion 461. The flange-shaped input element 420 of the damper 408 is axially adjacent to the side of the radial flange 462a facing away from the flange-shaped section 460 and is rigidly connected to rivet primary element 402 by rivets 433. Due to the location of the additional mass 462 of the radial section 462a between the flange-shaped portion 460 and the flange-shaped inlet element 420 of the damper 408, an axial free space occurs in which the hysteresis device 440 is olozheno similar hysteresis device 40 in Figure 2 or 140 in Figure 3.

An additional mass 462 is provided at the free end of the axial portion 462b with a mark 464 for controlling the engine. The friction clutch 451 and the secondary flywheel element 403 are located radially inside the radial protrusion 462b of the additional mass 462.

Figure 3-7 and the following figures in relation to the individual parts shows the various section planes, actually offset relative to each other in the direction of the periphery. This is necessary to explain the many design features. In this regard, it should be mentioned that in the side disks 123, 223, 323, 423, as well as in the radial sections 155, 255, 355, 455 and, if necessary, in the corresponding clutch plate 168, as well as in the clutch plate spring, recesses for screwing fastening means for connecting the damping device to the engine output shaft. In this regard, reference should be made to DE-OS 4117579, 4117582 and 4117571.

The extinguishing device shown in FIG. 8 comprises a damper 508, which has a structure substantially similar to that of damper 8 in FIG. 2, and is likewise rigidly connected to the primary 502 and secondary 503 elements of the flywheel, namely by means of rivet joints 533, 524. Primary the flywheel element 502 is made in the form of a sheet structure as opposed to the primary mass 2 in FIG. 2, made in the form of a massive part, which is, for example, cast or forged and at least partially machined.

The support 504 between both elements 502, 503 of the flywheel is carried out similarly to the design in figure 2. Therefore, the secondary mass 503a, which forms the main component of the secondary flywheel element 503, rests directly through the bearing 506, made here in the form of a rolling bearing, on the axial protrusion 515 of the primary flywheel element 502.

In the same manner as in FIG. 1, in the construction of FIG. 8, an additional inertial mass 562 is clamped or secured between the inlet element 520 of the absorber and the radial flange portion 560 of the carrier part 559. The additional mass 562 is made in the form of an annular sheet shaped part formed initially flat sheet blank. The additional mass 562 has an L-shaped cross-section, with the radial 562a and axial 562b of the shelf made in two layers. The additional mass 562 is located radially inside the outer sleeve-like axial protrusion 561 of the sheet carrier 559 and can also be centered on it. The centering of the additional mass 562 can be carried out by means of an axial protrusion 561.

Under the action of centrifugal force, at least the axial portion 562b of the additional mass 562 can radially rely on the axial protrusion 561, made more stable.

The friction clutch 551 located on the flywheel secondary element 503 is formed by a so-called self-regulating friction clutch, which can compensate for the wear that occurs at least on the friction linings 567 of the clutch disc 568 so that the disc spring 573 has, during the service life of the friction clutch 551, at least approximately the same operating range, and thereby the characteristic of the shut-off force, remained practically constant during the life of this friction clutch.

For the implementation of such self-adjusting friction clutches, reference should be made to DE-OS 4239291, 4306505, 4239289 and 4322677.

The friction clutch 551 is connected to the secondary mass 503a in the same way as described in conjunction with FIG. 5, so that the friction clutch 551 can slip relative to the secondary mass 503a, at least with the friction clutch 551 turned off and high torque peaks. Slip or torque limiting mechanism 574 includes an annular or membrane-shaped spring element 570, acting similarly to a cup spring. The spring element 570 in an unmounted state is straightened conically or in the form of a truncated cone similar to a Belleville spring, with the imaginary vertex of the cone pointing to the left, i.e. in the direction of the radial sections 560. When mounting the damping device 501, namely, in the manufacture of rivet joints 524, the spring element 570 is pulled into the depicted position so that it radially inside relies on the radially outer edge section 523a of the part 523, and radially further outward on the radial plot 503b of secondary mass 503a. Radially further from the outside, the friction clutch housing 569 551 is screwed to the spring member 570.

The tension of the spring element 570 is designed so that it creates an axial force that is predominantly greater than the maximum disengaging force that occurs during the life of the friction clutch 551. Due to this, the casing 569 is axially rigidly supported by the spring element 570. The slipping moment of the torque limiting device 574 may to be calculated the less, the greater the applied axial force 270 is coordinated with the maximum shut-off force necessary to bring The action of the friction clutch 551.

The annular part 270 described in connection with FIG. 5 can be made in the same way as described in combination with the spring element 570, in the form of a part like a membrane or a disk spring, which in an unmounted state is straightened in the form of a truncated cone.

The oscillation damping device 601 illustrated in FIG. 9 includes a primary 602 and a secondary 603 flywheel elements mounted to rotate with respect to each other by means of a support 604, similar to that shown in FIGS. 2 or 8. The primary flywheel element 602 comprises a carrier part 659 made from an initially flat sheet material. A sheet piece 659 of relatively large thickness, for example of the order of 4-7 mm, has a portion 661 radially outside formed by folding the raw material and made in two layers, both layers 661a, 661b being practically adjacent to each other. A defined gap or cavity may also be provided between the two layers 661a, 661b. The radially outer portion 661 of the carrier part 659 is made annular and forms, basically, an axial protrusion, significantly increasing the moment of inertia of the part 659.

Detail 659 carries a separate additional mass 663 made of an annular L-shaped section. The additional mass 663 covers the portion 661, the inner contour of the additional mass 663 and the outer contour of the portion 661 are coordinated with each other with the possibility of centering the part 663 on the part 659. The additional mass 663 is also made in the form of a sheet shaped part, and in the illustrated example the two-layer is made only axially passing shelf 663b. The radial shelf 663a has only one sheet layer, however, depending on the required moment of inertia, it may also have at least two layers. The axial shelf 663b may have more than two layers. An additional mass of 663 is molded from an initially flat round billet. Radially outside, the sheet mass 663 has a seat 663c in which the starting gear ring 613 is placed. The radial shelf 663a of the additional mass 663 is radially inside rigidly connected to the part 659 with rivets 633. The rivets 633 simultaneously serve for rigidly connecting the input element 620 of the damper with the part 659. The damper 608 comprises two side discs 622, 623, the side disc 622 having several peripherally recessed pockets or pockets 624 that extend axially in the direction of the side disc 622 and abut against the front portion 624a him. Rivet elements 633 are provided in the area of these pockets 624. Recesses or pockets 624 form spacers that hold the side discs 622, 623 at a certain axial distance from each other. The recesses 624 pass through cutouts 635 made in the flange-shaped output element 621 of the damper 608. The cutouts 635 and the recesses 624 are matched to each other with the possibility of compressing the energy accumulators 607 of the damper 608. The rotation between the input 620 and the output 621 is limited by stopping the recesses 624 at the lateral ends cutouts 635, i.e. in the same way as described in combination with cutouts 35 and rivet elements 24 in FIGS. 1 and 2. Parts 621, 622, 623 have bore holes or recesses in which springs 607 are placed in the same way as described in combination with other figures.

Between the output element 621 of the absorber 608 and the secondary element 603 of the flywheel or a friction clutch mounted on it there is a torque limiting device 674 made in the form of a two-stage safety friction clutch. The device 674 therefore comprises a first slip step 674a and a second slip step 674b parallel to it, which are arranged radially one above the other in the illustrated embodiment, the first slip step 674a being radially inside the second slip step 674b.

Slip stage 674a includes an energy accumulator 675 in the form of a Belleville spring, which is radially outer portion located on a bowl-shaped part 676, capable of axially strong connection with the secondary element 603 of the flywheel or axially firmly connected during installation of the corresponding friction clutch with its casing. The radially outer portion of the disk spring part 674 is rigidly connected to the element 676 by means of a geometrical closure, for example by means of a gear connection 677. The disk spring part 675 loads the outer ring-shaped section 621a of the output element 621, whereby the latter axially clamps with friction between the secondary mass of 603 and a battery of 675 energy. Parts 675, 621, 603 can be directly pulled together, however, between at least two of these parts can also be provided with a friction lining or friction layer. If necessary, at least one of these parts, at least in the friction zone, can be phosphated.

The radially outer friction step 674b also comprises an energy accumulator 678 in the form of a disk spring, which is axially tensioned between the support sections 676a, 603a of both parts 676, 603 radially offset from one another. In the illustrated embodiment, the energy accumulator 678 in the form of a disk spring is supported by sections 676a, 603a through the friction lining. In some cases, these friction linings, however, may not be necessary, and due to the corresponding shaping of the engaged parts, they rely directly on each other, and here also at least one of the parts, at least in the friction zone, can have a coating, for example, may be phosphated or solid nickel plated.

The external slip step 674b has a kinematic relationship 679 with the internal friction step 674a. The kinematic connection 679 is formed by teeth entering into each other, made, on the one hand, on the radially inner section of the part 678, and on the other hand, on the radially outer section of the part 621. The teeth are aligned with each other with the formation of a backlash, so that the inner step 674a of friction can act on a certain angle of rotation between both elements 602, 603 of the flywheel. This angle of rotation is advantageously at least 10 °, however, it can be significantly larger, for example 20 ° or more. In some cases, however, it may be preferable if there is a relatively small angle of rotation, i.e. less than 10 °.

Detail 676 is depicted in an axial position in which energy accumulators 675, 678 have a predetermined tension.

When assembling the damping device 601, when the cup-shaped part 676 is connected to the clutch cover during mounting of the corresponding friction clutch, the part 676 can be axially displaced and take the position shown in FIG. 9 only after the friction clutch is mounted. Prior to mounting the friction clutch, the part 676 is displaced to the left by the energy accumulators 675, 678, namely since the energy accumulators 675, 678 are then in at least partially weakened state. In this state, energy accumulators 675, 678 in the form of disk springs are straightened conically or in the form of a truncated cone, with the imaginary tip of the cone pointing to the right. In this embodiment, the damping device after dismantling the friction clutch, the secondary flywheel element 603 can be rotated relative to the primary flywheel element 602 with little or no resistance to rotation, due to which the holes 649 made in the secondary flywheel element can be brought into axial position using fasteners means 619 and, thus, if necessary, the screws 619 can be screwed in using a tool. This greatly facilitates the replacement of extinguishing device 601.

In the embodiment of FIG. 10, the vibration damping device 701 comprises primary 702 and secondary 703 flywheel elements mounted to rotate with respect to each other by means of support 704 with sliding bearing 706. The sliding bearing 706 is arranged in the same way as described in connection with FIGS. 3 or 7. This sliding bearing can also be used to form the support 604 in FIG. 9, however, the adjacent parts must be adjusted accordingly.

Bearing 706 consists of a sleeve-shaped inner ring 706a and an outer ring 706b, made and placed in the same way as described in connection with the bearing ring 106 of FIG. 3. A significant difference from the plain bearing 106 in FIG. 3 is the use of an inner sleeve 706a worn on an axial protrusion 715 of the primary flywheel element 702. The sleeve-shaped inner ring 706a of the plain bearing can be pressed onto the protrusion 715 or fixed on it by additional means, for example, by notching or flipping the free end of the protrusion 715. The inner ring 706a can be ordered from the supplier of plain bearings in the form of a finished part together with the outer ring 706b. This has the advantage that the axial sections 715a of the axial protrusion 715 accommodating the sliding bearing 706 do not require extremely precise machining, in particular grinding or fine turning. Due to the use of the inner bearing ring 706a, in many cases it is sufficient if the sections 715a are only deep drawn and, if necessary, calibrated.

The damper 708 located between both elements of the flywheel 702, 703 is made similarly to that shown in FIGS. 3 or 5. The lateral disks 722, 723 radially outside the energy accumulators 707 are, however, cup-shaped towards each other and in the outer radial zone at least partially fit to each other. In the adjoining sections 722a, 723a, both discs 722, 723 are connected to the secondary mass 703 via rivet joints 724. The side disc 722 has recesses or pocket-like sockets 722b formed in the area of the rivet joints 724. These sockets 722b pass axially through the cutouts 720a of the flange-like input element 720 quencher. The side discs 722, 723 form the output element 721 of the damper. The recesses 720a are made with respect to the recesses 722b with the possibility of forming the angle of rotation necessary for the damper 708 between the input 720 and the output 721 elements. The cutouts 720a and the recesses 722b are consistent with each other, therefore, similarly to what has been described in connection with the cutouts 35 and the rivet elements 24 in FIGS. 1 and 2. The sheet carrier 759 is made similar to part 659 in FIG. 9. Similarly, as in FIG. 7, an additional mass 762 is located between the supporting part 759 and the absorber inlet 720. The axial shelf 762a of the additional mass 762 axially extends beyond the axial protrusion 761 of the part 759 and carries a ring 713 forming an initial gear ring on the axially protruding portion. , or a profiled ring 713a to control the engine.

Between both elements 702, 703 of the flywheel there is also a hysteresis device 740, acting similarly to the hysteresis devices already described. Next, between the flange-like part 720 and the disk-shaped part 722, an energy accumulator is tensioned in the form of a Belleville spring 775, which creates the main friction or main hysteresis that acts along the entire angle of rotation of the damper 708. Due to the location of the energy accumulator 775 and its axial tension, the secondary flywheel element 703 is pushed to the primary flywheel element 702 or attracted to it. The axial tension force formed by the part 775 in the form of a Belleville spring between both elements 702, 703 of the flywheel is caught by the radial section 706b of the sliding support 706. The spring part 775 can complement or replace the depicted part also in another place of the device 701 damping torsional vibrations, namely between two parts mounted with the possibility of rotation in relation to each other.

Figure 11 shows a variant of the bearing, which, in principle, can find application in all forms of execution. The support 804 is thus made in such a way that the bearing 806, made in the example specifically shown in FIG. 11 in the form of a sliding bearing, is located radially inside the axial protrusion or the landing place 815 of the primary flywheel element 802. An axial protrusion 852 formed on the flywheel secondary element 803 extends radially inside the seat or axial protrusion 815. A bearing 806 is located between the two seats or bearings 815, 852.

The torsional vibration damping device 901 depicted in FIG. 12 includes a primary 902 and a secondary 903 flywheel elements mounted to rotate with respect to each other in the same way as described, for example, in combination with FIGS. 2, 8 and 9 The damper 908 and the torque limiter 974 are arranged, configured and act similarly to the damper 608 and the torque limiter 674 in FIG. The lateral disk 922 differs, however, from the disk 622 in FIG. 9 in that it has radially inwardly directed portions 922a axially clamped between the screw heads 919a of the screw 919 and the radially inner portions of the carrier part 962 made from a sheet. Radiator 906 radially outside of the energy storage batteries 906 the disk-shaped part 922 is firmly connected to the carrier part 962 by means of riveted joints 933. The disk-shaped part 922 therefore has, both radially outside and radially inside the energy accumulators 906, a strong connection to the carrier nd component 962. Since both parts 962, 922 are axially spaced from each other between the radially external and radially internal joints, a box-shaped profile is formed, if viewed in cross section, which provides increased rigidity of the assembly consisting of parts 962, 922, in particular in axial direction, so that the carrier part 962 can be made of a material of lesser thickness. To increase the rigidity of the side disks 922, 923, the seats of the energy accumulators 906 provided therein can be made in the same way as described in connection with the side disc 123 in FIG. 3.

According to one embodiment, one of the side disks of the absorber located between the elements of the flywheel may not be needed if the necessary places for loading and moving the landing places of the energy accumulators are performed directly on the corresponding element of the flywheel or one of its parts. Thus, for example, in the embodiment of FIG. 12, a lateral disk 922 may not be needed if the corresponding spring seats 906 are squeezed into the carrier part 962. These seats can be made, for example, similar to the seats 139 of the side disk 123 in FIG. 3. Consequently, pocket-shaped seats for the spring 906 can be squeezed out in the carrier part 962, and these pocket-shaped seats can be formed by depressions and bulges made in the sheet material of the part 962.

The embodiment of the torsional vibration damping device 1001 shown in FIGS. 13 and 14 includes a primary 1002 and a secondary 1003 flywheel elements. The primary element 1002 of the flywheel comprises a bearing part 1059 made of sheet material, bearing an outer ring gear 1013 radially outwardly from the outside. Further, an additional ring-shaped mass 1062 is fixed to the bearing part 1059. Fastening between the bearing part 1059 and the additional mass 1062 is carried out by means of rivet elements 1033 formed in one the whole in the bearing part 1059. The radially inner sections of the bearing part 1059 are made with the possibility of connection with screws 1019 with the output shaft of the engine.

Both flywheel elements 1002, 1003 are rotatably mounted to each other by means of a sliding support 1004 in the same way as described in connection with FIGS. 3, 7, 10 and 11. Between the radially inner portions 1059a of the carrier part 1059 and the heads 1019a screws is an annular part 1080 serving as a washer under the heads 1019a of screws. The annular part 1080 extends radially inward beyond the screw heads 1019a and forms a support portion 1080a on which the radial annular portion 1006b of the bearing 1006b can be axially supported. In the depicted exemplary embodiment, the radially inner portion 1080a may axially rest against the radial shoulder 1015a of the axial protrusion 1015. If the part 1080 in the axial direction is sufficiently rigid, such a support is not required. Part 1080 is partially cut out in the region of the screw heads 1019a, so that part 1080 has substantially flat portions in this region. As can be seen from FIG. 13, the annular portion 1080a is axially offset relative to the further parts of part 1080 located further radially outside. Part 1056 is made and rigidly connected to side disk 1023 in the same way as described in connection with part 156 and side disk 123 in FIG. 3. On Fig depicted recesses 1081, 1082 in the side disk 1023 and parts 1056 necessary to tighten and loosen the screws 1019. The screws 1019 are installed in the device 1001 damping torsional vibrations without falling out. If the clutch plate 1068 and the friction clutch 1051 are supplied together with the flywheel elements 1002, 1003 as a mounting block, then corresponding recesses or cut-outs for screwing in the screws 1019 should be provided in the clutch plate 1068 and the tongues 1073a of the spring disk 1073.

The damper 1008, located between both elements 1002, 1003 of the flywheel, contains two annular parts or two side discs 1022, 1023, which extend radially at an axial distance from each other and place an annular part 1021 between them. Detail 1021 forms radially directed consoles or tabs 1037, serving to load the energy accumulators 1007 formed by the coil springs. Both side discs 1022, 1023 are interconnected by rivet elements 1033, which in the illustrated example are made in the form of flat rivets, which provides a radially compact design. The side discs 1022, 1023 have recesses or seats 1038, 1039 of the landing batteries 1007 energy. The cutouts 1036 made between the consoles 1037 in the part 1021 are open radially inward (Fig. 14). Radially outwardly, part 1021 has axially bent consoles 1083 that serve to secure part 1021 to a carrier part 1059. Axial consoles 1083 are riveted with part 1059 due to the fact that at least one rivet head 1084 is made on their free end. On figa shows a section of such a rivet connection, namely in the direction of arrow A in Fig.13.

As can be seen from FIG. 14, the consoles 1083 pass axially through elongated cutouts 1035 in the side disk 1022. For a non-torque absorber 1008 between sections 1083a of consoles 1083 axially passing through part 1022 and end edges of recesses 1035 viewed in the direction of the periphery in one direction of rotation there is a play of 1085 crankshaft, and in another there is a clearance of 1086. A larger play of 1085 cranks serves here for the traction mode, and a smaller play of 1086 serves for the pusher driving mode of the car equipped with a quenching device.

As can be seen from FIG. 14, the riveted joints 1033, 1083 are offset relative to each other in the peripheral direction, so that the joint 1033 is between the two joints 1083, and vice versa.

Between the output element 1021 of the damper 1008 formed by both side disks 1022, 1023 and the secondary mass 1003a of the flywheel element 1003, a torque limiting device 1074 is located. To form this device 1074, the secondary mass 1003a extends radially to the inner portion 1003b between the two side discs 1022, 1023. Connecting means or rivet elements 1033 are provided radially inside the portion 1003b. On the side facing the friction surface 1009 of the secondary mass 1003a, the radially inner portion 1003b forms or limits an axial bearing surface 1087, which is axially offset back relative to the friction surface 1009, namely, preferably by an amount that at least corresponds to having the thickness of the material of the lateral disk 1023 that is formed in this zone. The axial ledge 1088 forming the supporting surface 1087 further limits the cylindrical inner surface 1089. As can be seen from FIG. 13, the axial ledge 1088 and the radially outer portions 1023a of the lateral disk 1023 are aligned so that the secondary the mass 1003a rests on the radially outer portions 1023a of the side disc 1023 in both radial and axial directions. For radial support is the axial section 1089 of the ledge 1088, based on the outer periphery of the section 1023a.

To create the frictional closure required for the torque limiting device 1074, an energy accumulator is provided in the form of a Belleville spring 1075 tensioned between the side disk 1022 and the secondary mass 1003a. To this end, the cup spring 1075 is supported by a radially outer portion 1090 of the side disk 1022 and loads the support cams 1091 of the secondary mass 1003. The support sections 1091 are provided in the illustrated embodiment with a larger diameter than the support sections 1090. Due to the tension of the cup spring 1075, the support surface 1087 is pressed to the radially outer portion 1023a of the side disc 1023, so that a friction closure connection occurs at this point. A second friction closure connection is formed between the disk spring 1075 and the cams 1091. Preferably, the disk spring 1075 can be rotatably connected by a corresponding geometrical closure to the side disk 1022, whereby slippage always occurs between the secondary mass 1003a and the disk spring 1075.

As can be seen from FIG. 13, the arrangement of the secondary mass 1003a axially between the two side disks 1022, 1023 provides an axially compact design. The radial arrangement of the joints 1033, 1084 provided for at least approximately the same diameter provides a radially compact design. The compact design is also ensured by the location of the support 1004 in close proximity to the screws 1019, as well as the location of the support 1004 radially inside these screws 1019. The use of the support 1006 provides further radial reduction of the required structural space.

A significant difference of the embodiment shown in FIG. 15 of the vibration damping device 1101 from the devices already described is that the secondary flywheel element 1103 together with the damper 1108 can be connected in block form to the primary flywheel element 1102. To this end, the absorber inlet element 1120 has threaded holes 1190 radially outwardly into which screws 1191 axially supported by the primary flywheel element 1102 can be screwed from the side facing from the secondary flywheel element 1103. Advantageously, the mounting block, connected by screws 1191 to the primary flywheel element 1102, may also comprise a friction clutch 1151 and a centered clutch disc 1168. Further, the mounting block containing at least the secondary element 1103 of the flywheel and the damper 1108 may already contain a bearing 1106, made in Fig.15 in the form of a sliding bearing. In this case, the mounting block is put on the axial protrusion 1115 of the primary flywheel element 1102 and is rigidly connected to it with screws 1191.

Such an assembly allows the primary installation of the primary flywheel element 1102 on the engine output shaft by means of fasteners 1119, so that additional access to the parts of the damper 1108 or the secondary flywheel element 1103 is not required to provide access to the screws 1119.

As can be seen from FIG. 15, a hysteresis device 1140 is also provided, acting similarly to those already described. Before assembling both elements of the flywheel 1102, 1103, the friction ring 1144 and the energy accumulator axially loading it in the form of a part 1145 like a disk spring are pre-mounted on the primary flywheel element 1102. In the unassembled state of both elements of the flywheel 1102, 1103, the friction ring 1144 is protected from falling out by means of stops 1144a on the primary flywheel element 1102.

In the oscillation damping device 1201 shown in FIG. 16, the principle of operation of which is similar to those already described, the hysteresis device 1240 is located radially outside the damper energy accumulators 1207 1208 and axially between the side disks 1222, 1223, which form the damper output element 1221 here, however, they can also form its input element, as shown, for example, in Fig.9. The hysteresis device includes a friction ring or segmented friction shoes 1244, which are in friction meshing, on the one hand, with the side disk 1223, and on the other hand, with an energy accumulator made in the form of a piece 1145 like a Belleville spring. Radially inside, part 1145, like a Belleville spring, axially rests on a side disk 1222. Between the output element 1220, made in the form of a flange-like part, and the side disk 1222, an additional energy accumulator is formed, which is formed by the part 1275 in the form of a disk spring and creates the main damper 1208 around the entire angle of rotation friction. The control of the friction ring 1244 or the segmented friction elements forming it is similar to that described in connection with the friction ring 44 in FIGS. 1 and 2. The hysteresis device 1240 therefore has a backlash, so that when reversing the direction of the relative rotation between both elements 1202, 1203 flywheel created by a hysteresis device 1240 frictional damping at a certain angle of rotation stops or disappears.

The embodiment of the vibration damping device 1301 shown in FIG. 17 is made with respect to the principal construction of the damper 1308 and the friction or hysteresis device 1340 similarly to the damping devices and hysteresis devices in FIGS. 3, 5 and 7, 8. The primary flywheel element 1302 is made in the form of a sheet structure. Both elements 1302, 1303 of the flywheel are mounted coaxially and rotatably with respect to each other by means of a support 1304, made similarly to the support 1004 in FIG. 13. The damper 1308 differs from the damper in FIGS. 3, 5 and 7, 8, in particular in that the lateral disk 1323 forming the output element 1321 of the damper 1308 is kinematically coupled to the ring-forming part by means of a friction clutch or torque limiting device 1374 1303a secondary element 1303 flywheel. The torque limiting device 1374 between the two flywheel elements 1302, 1303 has the same or even the same effect as the device 674 or 974 between the flywheel elements 602, 603 or 902, 903. The torque limiting device 1374 is also configured with two slip stages 1374a and 1374b and contains two energy accumulators 1375, 1378 in the form of Belleville springs arranged and tensioned similarly to the energy accumulators 675, 678 in FIG. 9. The energy accumulator 1378 in the form of a disk spring is in direct frictional engagement with parts 1308a, 1376. Part 1376 is made cup-shaped and is firmly connected to the annular massive part 1303a. As you can see, part 1376 is made, when viewed in cross section, similarly to part 676 in Fig.9. The cup-shaped part 1376 holds the energy accumulators 1375, 1378 in the form of cup springs in an axially tensioned position, namely, in the same way as described in connection with FIG. 9 for energy accumulators 675, 678.

The construction of FIG. 17 can be assembled in a particularly simple and preferred manner. The assembly can be carried out in such a way that the damper 1308, consisting of at least both side disks 1322, 1323, the flange 1320 provided between them and the springs 1307, is assembled in the form of an initial assembly, and when assembling the initial assembly, the cup-shaped part 1376 and at least the energy accumulator 1375 must be axially inserted between the side disk 1323 and the flange-shaped part 1320. The initial assembly thus formed can then be connected to the primary flywheel element 1302, for example by means of rivet joints 1333. Up to the formation of this connection or connections 1333 necessary to form a hysteresis device 1340 parts axially position or mount accordingly between the flange-like part 1320 and the primary element 1302 of the flywheel. The support flange 1355 before this mounting step may already be connected to the side disc 1323. Due to this partial mounting, an initial assembly is formed comprising at least a primary flywheel element 1302, a hysteresis device 1340 and a damper 1308, as well as a bowl-shaped part 1376 and, at least the energy accumulator 1375 of the torque limiting device 1374. For the final assembly of the device 1301, the annular part 1303a having a friction surface for the clutch disc can be firmly connected to the cup part 1376 by means of rivet joints 1350. Rivet joints 1350 between the cup part 1376 and the annular massive part 1303a can be made similar to rivet joints between the parts 1059 and 1021 described in connection with FIGS. 13, 13a.

Before mounting the part 1303a, it is necessary to pre-mount or insert the element 1378 in the form of a disk spring and, if necessary, friction rings axially resting on the part 1303a.

For the final installation of the block 1301 or for the manufacture of rivet joints 1350, the cup-shaped part 1376 and the annular massive part 1303a are first axially pulled towards each other, due to which the axial tension of the energy accumulators 1378, 1375 in the form of disk springs occurs. This tension determines the transmitted torque of the torque limiting device 1374 or the slip moment of the slip steps 1374a, 1374b. For the manufacture of rivet joints or tension between the parts 1374, 1303a, the part 1376 is supported or axially loaded by means of a mating holder or support tool 1380 adjacent to the side of the part 1376 facing away from the energy accumulators 1375, 1378. For this, the primary fly mass 1302 has several axially distributed peripherally holes 1381 through which axial protrusions 1382 axially extend, exerting axial force on the cup-shaped part 1376. The annular part 1303a is also axially supported or loaded and a tool (not shown), so that the energy accumulators 1378, 1375 are held in axial tension and rivet joints 1350 can be made. They are made by crimping (not shown).

Instead of rivet joints, eachekana between parts 1376 and 1303a can also be used.

Additionally or alternatively, the tongues of the part 1376 axially passing through the holes or axial passages or free spaces of the part 1303a can be bent lengthwise on the side of the part 1303a facing away from the damper 1308 radially or in the direction of the periphery, so that they axially extend from the rear in some places, the part 1303a and, thereby, axially fixed the part 1376 on the part 1303a.

Alternatively or additionally, the part 1376 can also be connected to the part 1303a by means of welded joints, for example by laser welding, these connections can be made directly between the two parts 1376, 1303a, or at least one or also several parts, for example sheet parts, which are connected to the part 1376, namely, so that they provide an axial bearing of the part 1376 on the part 1303a.

An alternative mounting option for the device of FIG. 17 is that a torque limiting device 1374, which also includes a side disk 1323, is pre-mounted on an annular massive part 1303a, and a flange 1320 is mounted on a primary flywheel element 1302, the side disk 1322 and the details of the hysteresis device 1340 should be appropriately nested. After that, both formed source nodes are assembled at an intermediate arrangement of springs 1307 and connected by rivets 1385. For this, however, at least part 1303a must have holes 1386, indicated by a dashed line in Fig. 17. The primary element 1302 of the flywheel also has holes 1387, coaxial with the rivets 1385. Through the holes 1386, 1387 can be introduced crimps necessary for the formation of heads 1385a, 1385b of the rivets.

The invention is not limited to the embodiment as described. On the contrary, in the framework of the invention, numerous modifications and modifications are possible, in particular such variants, elements and combinations and / or materials that are inventive, for example, due to the combination or modification of individual features or elements or process steps described in the general description and examples execution, as well as the claims contained in the drawings, and due to the combined features lead to a new object or new steps in the method or sequences of steps of the method, also if they relate to manufacturing methods, tests and processing.

Claims (73)

1. A device for damping torsional vibrations, containing input and output parts installed with the ability to perform rotational movements together with each other and with respect to each other, and at least one damper located between these parts and providing resistance at least at least some of their rotational movements with respect to each other, and the damper contains at least one energy accumulator, characterized in that the input and output parts respectively contain primary and secondary The primary flywheel, the damper further comprises at least one input element receiving torque from the primary flywheel, and an output element mounted to rotate with respect to this at least one input element and to transmit torque to the secondary flywheel and at least one energy accumulator is located between the parts of the at least one input element and the output element, malleably counteracting the rotation of the at least one input element and the output one element in relation to each other, the device contains a first connection for transmitting torque between the input part and at least one input element and a second connection for transmitting torque between the output element and the output part, and at least one energy accumulator is located at a smaller distance along the radius from the axis than each of these two connections for transmitting torque. 2. The device according to claim 1, characterized in that the input part contains means for receiving torque from the primary engine, and the output part contains means for transmitting torque to the transmission or power transmission of the car. 3. The device according to claim 1, characterized in that the input element has a friction surface, the device further comprising a friction clutch having a pressure disk, a clutch disk located between the pressure disk and the friction surface, and means for moving the pressure disk relative to the friction surface in a plurality of positions, in at least one of which the pressure plate ensures that the clutch plate is pressed against the friction surface, thereby obtaining torque from output part. 4. The device according to claim 1, characterized in that it contains a friction connection between at least one of the flywheels and the corresponding input or output element. 5. The device according to claim 1, characterized in that a geometric circuit is provided between one of the flywheels and the corresponding input or output element. 6. The device according to claim 1, characterized in that the flywheels are mounted to rotate about a common axis, and one of the links for transmitting torque is located at a different radius along the axis than the other of these links. 7. The device according to claim 1, characterized in that the flywheels are mounted for rotation about a common axis, while the device further comprises a friction connection between one of the flywheels and the corresponding damper element and provides a geometric circuit between the other flywheel and the corresponding damper element, moreover, the geometric the closure is located at a smaller radius along the axis than the friction link. 8. The device according to claim 1, characterized in that it contains means for limiting the amount of torque that can be transmitted between the flywheels, and the restrictive means contains a friction coupling between one of the flywheels and the corresponding damper element. 9. The device according to claim 1, characterized in that the flywheels are mounted for rotation about a common axis, while the device further comprises a primary engine having a rotating output node, and a connection for transmitting torque between this node and the primary flywheel, this connection located at a smaller distance along the radius from the axis than the specified at least one energy accumulator. 10. The device according to claim 1, characterized in that the flywheels are mounted to rotate about a common axis, the device further comprising means for attaching the input part to the rotating output node of the primary engine and means for centering the flywheels with respect to each other, and the centering the tool is located at a smaller radius along the axis than the fastening means. 11. The device according to claim 10, characterized in that the centering means includes a radial bearing. 12. The device according to claim 1, characterized in that the input and output elements are mounted rotatably about a common axis, and one, input or output, of these elements contains two annular parts connected to each other without rotation relative to each other a friend, and another, input or output, of these elements contains a disk-shaped part, and at least some part of this disk-shaped part is located between the annular parts, when viewed in the direction of the axis. 13. The device according to p. 12, characterized in that it contains means for centering the flywheels with respect to each other, and the centering means comprises a radial bearing, including some part of at least one of the annular parts. 14. The device according to p. 12, characterized in that it contains means for centering the input and output parts with respect to each other, and the centering means comprises a bearing including a substantially cylindrical part, which is a radially internal part, at least one of the annular parts or disk-shaped parts. 15. The device according to claim 1, characterized in that it contains means for centering the input and output parts with respect to each other to ensure that they rotate about a common axis, the damper includes a part protruding towards the axis and representing a part of the centering facilities. 16. The device according to clause 15, wherein the part of the centering means is a separately manufactured part, which is attached to one, input or output, of the elements. 17. The device according to claim 1, characterized in that the flywheels are mounted to rotate about a common axis, while there is provided a means for centering the input and output parts with respect to each other, at least one of which is input or output parts includes a part protruding towards the axis and representing a part of the centering means. 18. The device according to 17, characterized in that the part is a separately manufactured part, which is attached to the flywheel of at least one of these parts. 19. The device according to claim 1, characterized in that the damper comprises a hysteretic shock absorbing device operating in parallel with said at least one energy accumulator. 20. The device according to claim 19, characterized in that the hysteretic shock absorbing device includes a device that creates friction. 21. The device according to claim 19, characterized in that the flywheels are mounted for rotation about a common axis, wherein said at least one energy accumulator is located at a smaller radius along the axis than the hysteretic shock absorbing device. 22. The device according to claim 19, characterized in that the flywheels are mounted for rotation about a common axis, and the damper contains a first connection between the input element and the primary flywheel, as well as a second connection between the output element and the secondary flywheel, the first connection being on the other the distance along the radius from the axis than the second bond, and the hysteretic shock absorbing device is located at an intermediate distance along the radius from the axis compared to the distances from it to the indicated bonds. 23. The device according to claim 19, characterized in that the flywheels are mounted for rotation about a common axis, and the damper comprises a first connection between the input element and the primary flywheel, as well as a second flywheel connection between the output element and the secondary flywheel, wherein the hysteretic shock absorbing device is located at a greater distance in radius from the axis than each of these two bonds. 24. The device according to claim 19, characterized in that the hysteretic shock-absorbing device also includes a device that creates friction, and the specified device that creates friction, made in such a way as to provide a change in the hysteresis during rotation of the input and output parts relative to each other . 25. The device according to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, the device further comprising means for fastening the input part to the rotating input node of the primary engine, said fastening means being located at a predetermined distance radius from the axis, and one, input or output, of the elements includes two annular parts connected to each other without providing the ability to rotate them with respect to each other, as well as with one of the of the aforementioned parts, while the other, input or output, of these elements contains a disk-shaped part located between the ring parts, when viewed in the direction of the axis, and connected to the other of these parts, the disk-shaped part having an extreme radially inner part located on the same or at a greater distance along the radius from the axis than the specified specified distance along the radius. 26. The device according A.25, characterized in that the disk-shaped part has at least one window for part of at least one energy accumulator, and this one window is made in the extreme radially internal part of the specified disk-shaped parts. 27. The device according to p. 26, characterized in that at least one window faces the axis with its open side. 28. The device according to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, the device further comprising means for attaching the input part to the rotating output node of the primary engine, said fastening means being located at a predetermined distance radius from the axis, and one, input or output, of the elements includes two annular parts connected to each other without providing the ability to rotate them with respect to each other, as well as with one of the indicated parts, while the other, input or output, of these elements contains a disk-shaped part located between the annular parts, when viewed in the direction of the axis, and connected to the other of these parts, and at least one of these annular parts includes itself, the radially outermost part located at the same or greater radius radius from the axis than the specified radius radius. 29. The device according to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, and one, input or output, of the elements includes two ring parts connected to each other, while the other, input or output, from these elements includes a disk-shaped part located between the annular parts, when viewed in the direction of the axis, and at least one of these annular parts has at least one window for part of at least one battery nergii. 30. The device according to claim 1, characterized in that said parts are mounted to rotate about a common axis, the input element contains two ring parts, and the output element contains a disk-shaped part located between the ring parts, when viewed in the direction of the axis, and at least one energy accumulator is located at a predetermined distance along the radius from the axis, and the disk-shaped part has at least one elongated hole in the circumferential direction of the disk-shaped part, located at a large a distance along the radius from the axis than the specified predetermined distance along the radius, and the damper additionally contains fastening means protruding through this hole and connecting the ring parts to each other. 31. The device according to claim 1, characterized in that the primary and secondary flywheels are mounted for rotation about a common axis, the device further comprises means for attaching the first-mentioned flywheel to the primary engine, and one, input or output, of the elements includes a disk-shaped part, while the first-mentioned flywheel contains an elongated wall essentially in the radial direction with respect to the axis, said disk-shaped part has a part radially outer, ha The object further comprises fixing means by which a radially outer part of the disk-shaped part is attached to said wall, this wall and said disk-shaped part include parts that are spaced apart from each other in the direction of the axis, the device further comprising also a hysteretic shock-absorbing device, at least a part of which is located between the parts of the wall and the discovers spaced apart from each other heat parts. 32. The device according to p. 31, characterized in that it contains spacer means inserted between the wall and the disk-shaped part, at least in the area of the mounting means. 33. The device according to p, characterized in that the spacer means contains a mass ring. 34. The device according to claim 1, characterized in that the primary and secondary flywheels are mounted for rotation about a common axis, and the damper additionally contains a multi-stage, torque-limiting connection between one, input or output, of the elements and one of the flywheels. 35. The device according to claim 1, characterized in that it contains a modular unit including a secondary flywheel, a friction clutch pressure plate located so as to abut the secondary flywheel, and a clutch disk located between the secondary flywheel and the pressure disk, the damper additionally contains an output element that provides support for the modular unit. 36. The device according to claim 1, characterized in that the secondary flywheel is mounted for rotation about a given axis and has a friction surface located at a given distance along the radius from the axis, while the device further comprises means for limiting the amount of torque that the input part can transmit to the output part, and this limiting means is located with a gap relative to the axis at such a distance from it along a radius that, at least, in magnitude approaches specified radius distance. 37. The device according to claim 1, characterized in that the secondary flywheel is mounted for rotation about a given axis, the device further comprises a friction clutch configured to connect it to the secondary flywheel, and means for limiting the magnitude of the torque, which can be transferred between the input and output parts, and the specified means for limiting the magnitude of the torque also includes means for creating a torque that causes slippage, which includes It is a resilient element that provides energy storage when connecting the friction clutch to said flywheel. 38. The device according to clause 37, wherein the elastic element is a cup spring. 39. The device according to claim 1, characterized in that the primary and secondary flywheels are mounted for rotation about a common axis, moreover, one of the flywheels has at least one hole, and the damper further comprises means for attaching the output element to the other of these flywheels, while access to the specified fastening means is provided through the specified at least one hole. 40. The device according to § 39, characterized in that the mounting means comprises at least one rivet. 41. The device according to p. 39, characterized in that the other of these flywheels is made with the presence of a friction surface located at a predetermined distance along the radius from the axis, and said at least the hole overlaps the friction surface when viewed in the direction axis. 42. The device according to claim 1, characterized in that the primary and secondary flywheels are mounted for rotation about a common axis, the device further comprising a radial bearing located between the flywheels, means for attaching the first-mentioned flywheel to the rotating output unit of the primary engine, located at a greater distance along the radius from the axis than the radial bearing, and the specified energy accumulator is located at a greater distance along the radius from the axis than the specified fastening means, as well as the device further comprises means for limiting the amount of torque that can be transmitted between the input and output parts, a hysteretic shock-absorbing device operating between these parts, at least one of which is said restrictive means or said hysteretic shock-absorbing device is located at a greater distance in radius from the axis than the energy accumulator, and, in addition, the device further comprises at least one axial extension, provided tripped on the first flywheel mentioned and located at a greater distance along the radius from the axis than either of the two — said restrictive means or said hysteretic shock-absorbing device. 43. The device according to claim 1, characterized in that the input and output parts are mounted rotatably with respect to a common axis, and the primary flywheel has a radially outer part including at least one mass ring having several folded layers sheet material. 44. The device according to item 43, wherein the sheet material is a metal sheet material. 45. The device according to item 43, wherein the flywheel contains an elongated wall, essentially in a radial direction with respect to the axis, which is integral with the said at least one mass ring. 46. The device according to item 45, wherein the wall has at least one hole for fastening means for securing the specified flywheel to the rotating output node of the primary engine. 47. The device according to item 44, wherein the primary flywheel contains a second part and means for attaching at least one mass ring to this second part. 48. The device according to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, and the primary flywheel is mounted with the possibility of receiving torque from the primary engine, and the primary flywheel has a radially outer part, which is a mass ring, while the device further comprises a starter gear located on the specified mass ring. 49. The device according to p, characterized in that the starter gear is integral with the mass ring. 50. The device according to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, and the primary flywheel is mounted with the possibility of obtaining torque from the engine of the car, and the primary flywheel contains a radially outer part remote with respect to to the axis, and includes at least one mass ring with marks for controlling the engine. 51. The device according to p. 50, characterized in that the labels are integral with at least one mass ring. 52. The device according to claim 1, characterized in that the primary and secondary flywheels are mounted for rotation about a common axis, and at least one of these flywheels is installed with the possibility of its movement in the axial direction relative to the other of these flywheels , the device further comprises a hysteretic shock absorbing device, made with the possibility of working in parallel with the specified at least one battery of energy, and also includes at least th least one elastic member tending to displace said at least one of the flywheels in an axial direction towards the said other flywheel. 53. The device according to paragraph 52, wherein the at least one elastic element is a disk spring. 54. The device according to claim 1, characterized in that the primary and secondary flywheels are mounted rotatably with respect to a common axis, said first flywheel being configured to be connected to a rotating output unit of the primary engine, the device further comprising a modular unit including said second handwheel and damper, this modular unit being configured to be connected to the first of these flywheels. 55. The device according to item 54, wherein the modular block contains a friction clutch that carries the second handwheel mentioned on the second, and the clutch disc is located between the second of these flywheels and the pressure plate of the specified friction clutch. 56. The device according to claim 1, characterized in that it further comprises a hysteretic shock-absorbing device operating in parallel with at least one energy accumulator and containing at least one friction ring surrounding some part of one of the input or output, parts. 57. The device according to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, while the device further comprises a hysteretic shock absorbing device operating in parallel with the specified at least one energy accumulator, one input or output, from these parts has an annular guide surface centered on the axis, surrounding itself and directing the movement of the elements that create friction. 58. The device to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, one of these parts provides torque transmission to the other of these parts, while the device further comprises a friction clutch having a housing and a spring, and which carries the output part, and means for limiting the magnitude of the torque that can be transmitted between these parts, and the specified limiting means contains at least one elastic element, which th is loaded in the direction of the axis to assist the spring, and means for attaching the elastic element to the specified housing. 59. The device according to p, characterized in that said at least one elastic element is a disk spring. 60. The device according to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, and the secondary flywheel has a friction surface facing in the opposite direction with respect to the specified first flywheel, and a side facing the same flywheel wherein the device further comprises a modular unit including a second flywheel, a friction clutch adjacent to the friction surface, and a clutch disc located between the friction surface and the section leniem, the clutch has a casing and further comprises fastening means for attaching the housing to one thing - to said second flywheel or quencher - and having access to said side of said second flywheel. 61. The device according to p. 60, characterized in that the said fixing means is made with an external thread, and the housing has one hole with an internal thread for said external thread. 62. The device according to claim 1, characterized in that the primary and secondary flywheels are mounted for rotation about a common axis, the secondary flywheel having a friction surface facing in the opposite direction with respect to the output element, and a side facing the output element, with this device further comprises a modular unit including the second flywheel mentioned, a friction clutch adjacent to this friction surface, and a clutch disc located between the friction surface and friction clutch, and the clutch has a housing, and further comprises a mounting means for securing the modular unit to the specified output element, and this mounting means has access to it from the friction surface of the second flywheel. 63. The device according to item 62, wherein the fastening means includes threaded fasteners located parallel to the axis at a distance from it. 64. The device according to claim 1, characterized in that the input and output parts are mounted rotatably with respect to the common axis, the primary flywheel being configured to be connected to the rotating output node of the primary engine, the input element has two ring parts adjacent to the primary to the flywheel, said at least one energy accumulator comprises first and second means for connecting at least one of the ring parts to the primary flywheel, wherein the first connecting means about disposed at a greater radial distance from the axis than the said energy accumulator member and the second connecting means is located at a smaller radial distance from the axis than the element of the energy accumulator. 65. The device according to item 64, wherein the first connecting means comprises at least one rivet, and the second connecting means provides a connection of the primary flywheel with the specified output node. 66. The device according to claim 1, characterized in that the input and output parts are mounted for rotation about a common axis, and the damper contains five energy accumulators arranged in series in a row along the ring, which are located at the same distance from the axis, surrounding it from all sides . 67. The device according to p, characterized in that the energy accumulators are located at least basically at the same distance along the radius from the axis. 68. The device according to claim 1, characterized in that the primary and secondary flywheels are mounted for rotation about a common axis, while the device further comprises a friction clutch adjacent to the secondary flywheel and receiving torque from it, and a torque limiter operating between the output element and the secondary flywheel, and the clutch is made so that it can be connected to the secondary flywheel and disconnected from it, and the torque limiter contains at least one elastic element that is loaded in the direction of the axis when connected to the secondary flywheel, and which dissipates at least part of the energy when the clutch is disconnected from the secondary flywheel. 69. The device according to p, characterized in that at least one elastic element is a disk spring. 70. The device for damping torsional vibrations according to claim 1, characterized in that the flywheels are mounted for rotation about a common axis, and means are provided for attaching the input part to the rotating output unit of the primary engine and means for centering the flywheels with respect to each other, the centering means is located at a third distance along the radius from the axis, and the fastening means is located at a fourth, greater distance from this axis. 71. The device for damping torsional vibrations according to claim 1, characterized in that the flywheels are mounted for rotation about a common axis, and means are provided for fastening the input part to the rotating output node of the primary engine, the fastening means including a part radially outer located at a predetermined distance along the radius from the axis, the energy accumulator includes an extreme inner part in the radial direction, located at a third distance along the radius from the axis, and The predetermined distance along the radius from the axis approaches in value to the third distance along the radius. 72. The device according to p, characterized in that the energy accumulator is a coil spring. 73. A device for damping torsional vibrations, containing input and output parts installed with the ability to perform rotational movements together with each other and with respect to each other, and at least one damper located between these parts and providing resistance at least at least some of their rotational movements with respect to each other, and the damper contains at least one energy accumulator, characterized in that the input and output parts are rotatably mounted relative to with respect to the axis, there is provided means for fixing the input part to the rotating output unit of the prime mover, the mounting means including a radially outer part located at a predetermined radius along the axis, and the damper comprises an input element and an output element, one of these elements includes at least one annular part connected to one, input or output, of these parts, and the other of these elements contains at least one disk-shaped a part connected to another, input or output, of these parts, at least one of these parts includes an extreme inner part in the radial direction, located at a second distance along the radius from the axis, and the specified radius distance from axis approaches in its value to the second distance along the radius, while at least one of these parts has at least one window for part of at least one energy accumulator, and this is at least one window fulfilling it is located in the extreme radially inner part of the aforementioned at least one of the parts, and at least one window faces its axis with its open side.

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