ITMI992721A1 - TORQUE TRANSMISSION DEVICE FOR THE CONNECTION OF A CRANKSHAFT OF A HEAT ENGINE WITH A MOTORCYCLE SOCKET PART - Google Patents

Description

DESCRIPTION

The invention relates to a torque transmission device for the axial elastic connection of a crankshaft of a heat engine with a drive part of a drive chain, in particular a friction clutch or a liquid clutch, as a FOttinger clutch, with hydrodynamic converter, at least consisting of a disc part that can be connected to the crankshaft, on which an annular component is arranged in a radially external area, which forms the connection with the gripping part of motorcycle.

Similar torque transmission devices are known per se and are referred to as Flexible Flywheel, since the execution of the first disc part takes place in an axially flexible manner and therefore axial and / or shaft bending vibrations can be filtered at least partially. at the elbows.

In order to limit the maximum deviation of the axially flexible disc part, an arrangement is proposed in the patent publication DE - OS 4402 257 which provides axially between the flexible disc part and the thrust plate an intermediate piece, which after passing an axial clearance forms a stop for the thrust plate and thereby limits the axial path of the disc part. After the complete use of the clearance, such an arrangement is therefore also axially very rigid and, particularly in high speed ranges, almost completely transmits vibrations from the crankshaft to the clutch and to further components of the motor vehicle. In the event of a missing axial stop, the perfect actuation of the clutch is impaired by the axial elasticity that influences the disengagement process. An axially stiffer design of the disc part reduces axial damping.

It is therefore the object of the invention to propose an arrangement of a torque transmission device which has an improvement in the axial vibrations produced by the crankshaft for the entire speed range used of the vehicle. Furthermore, it is the object of the invention to configure a corresponding torque transmission device in a simple and easily mountable manner, and to use components which can be used without significant wear throughout the life of the vehicle.

The task is solved by means of a torque transmission device, which connects the crankshaft of a heat engine in an axially elastic manner with a drive part of a drive chain, in particular of a friction or friction clutch. a liquid clutch, such as a Fttinger clutch or hydrodynamic converter, and consists of at least a first disk part connectable to the crankshaft, which can be axially flexible, and of an annular-shaped component, fixed in a fixed or axially flexible to a radially external zone of the first disc part, component which forms the connection with the drive part, where the first disc part is clamped with the annular component by means of a second axially elastic disc part either by tabs made on the first component, or between the annular component and the second disk part, an axially acting frictional engagement is generated for m by means of a component preferably metal, elastic in the radial direction.

For such an arrangement, it may be advantageous for a damping device to be formed between the first disc part and the annular component, which by means of a springing part and a friction part suppresses axial vibrations and / or bending vibrations of the first part. disk. It may therefore be advantageous to provide the contact surface of the clamped parts - that is, of the annular-shaped component and of the second disc part - for micro-friction, so that by means of the axial deviation of the first disc part and an axially springing action of the second part of the disc elastic disc and at the same time by means of a friction component in the microzone between the annular component and the second part of the disc, a damping of the axial vibrations transmitted by the heat engine through the crankshaft to the first part of the disc can take place.

For this purpose, the second disk part can advantageously be clamped by means of an axial front surface with a front side facing the first part of the flywheel of the annular component. Similarly, the second part of the disc in further embodiments can be clamped by means of an axial front surface with a front side, not facing the first part of the flywheel, of the annular component.

The fastening of the second disc part can take place on the first disc part or on the annular shaped component, in this case a fastening together with the first disc part on the crankshaft is particularly advantageous, where an additional reinforcing piece can be arranged axially between the crankshaft and the first part of the disc or the first part of the disc can be axially arranged between the crankshaft and the reinforcement piece, and / or the second part of the disc can be arranged between the screw heads for fixing the first part of the disc and the component following axially, wherein the second part of the disc can also simultaneously serve as a reinforcing ring.

Furthermore, according to the inventive concept, the second disc part can be provided radially outside the screwing of the crankshaft of the first disc part, where it may be particularly advantageous to house the second disc part together with the annular component on the first. part of disk. For this purpose, the second part of the disc for axial support and / or for carrying out an engagement by friction may have on the annular component tongues broadened radially inwards, which are enlarged on their inner contour in the circumferential direction. , in particular to increase the friction surface of the tabs.

It may also be advantageous to make the second disc part axially resiliently, for example as a snap ring or with snap ring segments, which, distributed along the circumference, can be combined by means of the fastening means for the annular component and the first part of disc, to form a closed elastic ring. Thanks to an alternate fixing along the circumference, on the first part of the disc and on the annular component in this case independently or in addition to the axially elastic characteristics of the first part of the disc, an axially elastic connection can be obtained between the first part of the disc and the component. annular in shape, which, with corresponding design alternatively or in addition to the first disc part, can effect a damping, and the elasticity of the first disc part can be configured to a large extent freely. It is understood that the snap ring can be made to a large extent within the scope of its material characteristics and can also be implemented rigidly as a fastening ring. The tabs can be applied in one piece with the snap ring or as discrete components with the fastening means, where for the adaptation of the axial clamping and / or frictional engagement of the tabs with the annular component, the tabs can be fixed with the fastening means, which connect the elastic ring with the first part of the disc and / or with the annular component.

According to a further inventive concept, the first and second disc parts can be combined, since at least one, preferably more tabs distributed along the circumference are axially extracted from the first disc part, which are axially applied to the annular component and / or form a frictional engagement with the latter, where the tabs can be extracted radially from the outside towards the inside radially and / or vice versa.

The axially elastic connection of the first disc part and the annular component by means of the snap ring can be limited by an axial stop at least in one direction. For this purpose, the starter crown can be provided radially to the outside. Furthermore, in the case of a relative axial movement of the first disc part with respect to the annular shaped component, an additional frictional engagement can be provided between an axial shoulder on the outer periphery of the first disc part and the outer circumference of the annular shaped component.

According to a further inventive concept, the snap ring can be integrated in the first disc part, since in the first disc part in the area of the fastening means, which can be rivet connections in particular, divisions are provided - preferably with a part in the circumferential direction - of the disc material, whereby the axial elasticity can be increased in this area. For example, divisions can be applied radially inside and / or radially outside the fastening means or tabs are cut out and / or withdrawn in the circumferential direction and / or radially outwards and / or inwards, in which they are the fixing means for joining the annular component are housed. In this case, the tabs extracted in the circumferential direction can be oriented in the pulling and / or pushing direction.

Such arrangements can not only be advantageous for the execution of the axial elasticity of the torque transmission device, but also in particular can serve for the thermal insulation of the annular component from the first part of the disc. Particularly when the torque transmission device is used in connection with a friction clutch, in which the annular component can serve as a thrust plate or as a thrust plate, very high temperatures may be present in the annular component. , which can negatively influence the material characteristics, for example the elastic characteristics, of the first component at least for the entire duration of the torque transmission device.

Furthermore, the second disc part as a component determining the frictional engagement and / or axially clamping the first disc part and the annular component, depending on the fastening on the first disc part or on the annular component may constitute an engagement of friction with the annular component or with the first part of the disc.

It can also be of advantage if the second disc part has less axial stiffness than the first disc part.

According to the inventive concept, moreover, the second part of the disc can have tongues oriented radially outwards, which are distributed along the periphery and are axially tightened with the annular component, where the tongues of the cup spring can also determine a frictional engagement with the annular shaped component.

Furthermore, it may be advantageous to provide a torque transmission device for connecting a crankshaft of a heat engine with a drive part of a drive chain, consisting of at least a first axially flexible disc part, connectable with the crankshaft, on which an annular component is arranged in a radially external area, which forms the connection with the drive part, and where the second disc part is integrally housed in rotation on the shaft elbows and is in frictional engagement with the annular shaped component and the element forming the frictional engagement is an annular shaped component, which has elastic characteristics in the radial direction and is in frictional engagement on the circumference with the component annular in shape respectively with the second part of the disc.

This element can be formed as a corrugated ring, which has corrugations oriented radially outwards, and serves as a friction disk between the second part of the disk and the annular component, where the crests of the corrugations on the outer periphery are in frictional engagement with the inner periphery of the annular shaped component and the outer sides of the corrugation hollows on the inner periphery are in frictional engagement with the outer periphery of the second disc part. The cross section of the corrugated ring can in this case be for example rectangular, circular or the like.

A further embodiment can provide a radially springing disc part, housed on the crankshaft, which on its outer contour is directly in frictional engagement with the inner circumference of the annular component.

the torque transmission device can be provided for a friction clutch, where the annular component can form a thrust plate for the clutch, and by means of friction linings and a thrust plate a torque, which can be coupled and decoupled from the heat engine, is transmitted to a gearbox input shaft. Furthermore, in other embodiments, the annular-shaped component can be formed as a solid ring, on which a hydrodynamic converter or a Fottinger clutch is arranged integrally in rotation.

Advantageously, on the annular-shaped component, a starting crown is housed on its external circumference, for example on at least three axially oriented cams distributed along the circumference. These cams can be formed integrally axially in the direction of the crankshaft or in the opposite direction, where an orientation of the cams in the direction of the crankshaft can be particularly advantageous for reasons of space. In order to save axial space, it may also be advantageous to provide the first part of the disc with recesses in the shape of windows, corresponding to the cams, through which the cams pass, so that the cams, for housing the starting ring gear, can be moved in the direction axial towards the heat engine. Furthermore, the first part of the disc along its outer contour can have a surrounding molding in the axial direction, which preferably does not face the starting ring gear and in which ignition marks are made. This results in a particularly space-saving arrangement, in which the first part of the disc is axially arranged between the starter ring and a massive part of the annular component, where on the massive part of the annular component the cams are arranged axially in the direction crankshaft and ignition markings are arranged around the outer circumference of the annular shaped component.

For further optimization of the first disc part, profiling in the peripheral direction or in the radial direction can be provided on this, which positively influence the axial stiffness of the disc part. For example, a surrounding rib can be provided radially between the annular component and the crankshaft, where advantageously the rib is axially deepened in the direction of the annular component.

For easier assembly, the first disc part can be centered on the annular component by means of the ignition marking mold, whereby the annular component can be equipped with corresponding radially oriented centering cams. . The annular component is subsequently advantageously connected to the first disk part, preferably riveted or compressed. In this case the rivets can be provided all around radial height in the region of the bearing surface for friction linings of a friction clutch.

Similarly, the arrangement of a torque transmitting device may be advantageous, in which a first axially flexible disc part can be a component of a split flywheel with a primary flywheel mass and a secondary flywheel mass rotatable relative to and opposite to it. an energy accumulator acting in the circumferential direction, where the axially flexible disc part can be axially clamped by means of a second disc part of lower axial stiffness.

In this case, it can be advantageous to axially flexibly configure the primary flywheel and / or the secondary flywheel mass, wherein the correspondingly axially flexible component can be designed as a one-piece disc part or, composite, consist of components rigid and elastic, so that the primary flywheel and / or the secondary flywheel mass is at least partially vibration-isolated from the crankshaft stressed by axial or flexural vibrations, by at least one axially flexible component in the force flow between the shaft at elbows and clutch. Thus, for example, vibration isolation of the flywheel part of the secondary side, for example of the thrust plate of a friction clutch, can be achieved by means of an axially flexible disc part supported on the relatively rotatable primary part against the action of the damping device, for example in the form of energy accumulators acting on the periphery, where the axially flexible disk part can also consist of disk segments distributed along the periphery.

According to the invention, a second disc part is associated with the component which is each time axially flexible, respectively with the disc part, which can also consist of disc segments distributed along the periphery, and has a lower rigidity than the first. axially elastic disc part. The second disc part in this case is axially clamped indirectly or directly with the corresponding and axially flexible disc part and can form in this case for example annular bearing surfaces, which in the case of a relative axial movement of the two parts of one disc with respect to the other establish a frictional moment, which at least partially compensates for the bending or axial vibrations introduced by the crankshaft. It is understood that vibration isolation for damping axial or bending vibrations of the crankshaft can also be advantageous for vibrations introduced by the drive chain.

Advantageous embodiments for clamping the axially flexible disc part with the axially less rigid second disc part can provide that the disc part with the first disc part is housed on the crankshaft and can form a support radially outwardly. annular shape respectively a friction surface, or, in a further embodiment example, is fixedly connected in a radially outer zone with the axially flexible disc part, for example riveted, and on its radially inner zone can form a surface of annular bearing or annular friction surface with the axially flexible disc part.

Furthermore, it may be advantageous, in the case of a split flywheel, to axially clamp the flexible disc part axially with a less rigid disc part, where the disc part to be tightened is axially clamped between the secondary side and the primary side, and can therefore simultaneously represent a friction device for relative rotations in the circumferential direction and a friction device in the case of a relative axial movement of primary and secondary mass. Here the friction surface can be provided on the axially flexible disc part or on the opposite side of the rigid and non-frictional component with the attachment of the second disc part. It may also be advantageous not to fix the ring integrally in rotation in either of the two bearing surfaces, so that a friction surface on the secondary side and a friction surface on the primary side respectively are formed.

The invention is illustrated with the help of Figures 1 to 20. In this case:

Figure 1 shows a section of an exemplary embodiment of a torque transmission device according to the invention,

Figure 2 shows a diagram with the representation of the axial amplitude of the first part of the disc as a function of the number of revolutions of the heat engine compared to the state of the art,

Figures 3-13a show further examples of embodiments of torque transmission devices according to the invention in partial section, possibly with illustrative detailed representations and Figures 14-20 show examples of embodiments of a torque transmission device in section partial, as a split flywheel.

Figure 1 shows an embodiment example of a torque transmission device 1 with the first disc part 2, the second disc part 3 and the component 4 having an annular shape.

The torque transmission device 1 is connected to the crankshaft 8 with axial interposition of a reinforcement ring 5 on the crankshaft side and with the second disc part 3 on the other side of the first disc part 2 by means of screws 9, which pass through the openings 6 correspondingly provided in the parts 2, 3, 5. To facilitate assembly, the reinforcement ring 5, the first and second disc parts 2, 3 are riveted together, so that a one-piece coraponent is formed, where the rivets 7 are formed from the reinforcement ring 5 by means of axial compression in the circumferential direction alternately towards the openings 6 and are riveted with the second disc part 2.

In a further radial progression of the first part of the disc 2 towards the outside, this, directly radially outside the reinforcement ring 5, for the optimization of the axial dimension, is bent at an oblique angle axially in the direction of the shaft elbows 8 at least of the axial extension of the reinforcement ring 5, and after reaching the desired axial offset it is oriented again parallel to the plane of the screws 9. In the area of the outer diameter the first disc part 2 has a surrounding molding 10, not facing axially towards the crankshaft 8, so that the first part of the disc 2 is roughly cup-shaped, in which surrounding ignition marks 11 are made, which are detected by a transducer - not shown - and are transmitted to an evaluation unit.

The annular component 4 is arranged radially inside the axial molding 10 and is centered on the first part of the disc 2 by means of centering cams 12 distributed along the circumference. The axial connection integral in rotation with the first part of the disc 2 takes place by means of rivets 13 distributed along the periphery. The annular component 13 in the embodiment shown is configured as a clutch thrust plate with housings 14 and threaded holes 15 for accommodating the remaining clutch components as well as the friction surface 16, which is brought into frictional engagement with the clutch disc and in its radially external zone has, distributed along the periphery, the recessed rivets 13 for fixing the annular component 4 with the first part of the disc.

Radially outside the circle of rivets 13, at least two, preferably four or six cams 17 distributed along the circumference, extending axially in the direction of the crankshaft, are molded on the annular component 4, each of which has radially outwardly a bearing surface 18, on which a starting crown 19 is applied. The starting crown 19 can be fixed by welding, pre-sealing and / or withdrawal. In the area of contact of the cams 12 with the first part of the disc 2, in the part of the disc 2 window-shaped openings 20 are provided, corresponding to the cross-sectional profile of the cams 17, through which the openings 17 are made to pass, so that the starter ring 19 is arranged at approximately the same axial height as the collar 21 belonging to the crankshaft 8, respectively at least at the same axial height as the end of the crankshaft, so that the overall dimensions of the crankshaft are axially reduced. torque transmission 1 and / or a better behavior of the annular component 4 acting as flywheel mass is obtained.

The second disc part 3 is riveted with the first disc part 2 as well as with the reinforcement ring 5 to form a constructive unit 1, and is housed and screwed onto the crankshaft 8. The second radially outwards disc part 3 substantially follows the first disc part 2 and in the area of its outer periphery on the front side not facing the crankshaft, it is clamped with the front side, facing the first disc part, of the component 4 of annular shape, i.e. the second disc part is performed in an axially elastic way, preferably with a lower stiffness than the first disc part 2.

Radially on the outside of the screws 9, respectively of the rivets 7, the second part of the disc 3 has elastic tabs or tabs 22 in the shape of rays, radially outwardly oriented, which are distributed along the periphery and are tightened with the component 4 of annular shape, where on the annular-shaped component 4 there are provided, on the supporting surfaces, ribs 23 extending radially outwards, integrally formed corresponding to the number and shape of the tabs 22, which ribs can simultaneously represent a guide of the tabs 22 in the circumferential direction and thus improve the frictional engagement of the tabs 22 on the annular component 4.

The function of the torque transmission device consists in the fact that bending vibrations, caused by the ignition processes of the individual cylinders of the internal combustion engine, of the crankshaft 8 cause an axial vibration of the first part of the disc 2, which, compared with rigid flywheels, partially absorbs these vibrations and does not transmit them to the extent of the rigid flywheels to the clutch or to the converter. Decreasing axial stiffness actually improves the transmission behavior of these vibrations, but if the fit is too soft it affects the clutch release process.

In the exemplary embodiment shown of a torque transmission device 1, the second disc part 3 is therefore associated parallel, as a less rigid component axially, to the first disc part 2, where the second disc part is fixedly clamped only on one side - here at the first disc part 2 - and, axially clamped on the other side, constitutes a frictional engagement.

In the event of axial displacement of the first disc part 2 due to a bending vibration of the crankshaft 8, for example with an amplitude of up to two millimeters, preferably one millimeter, this is deflected in the predetermined radial range by the screws 9 as a fixed point and by the rivets 13, which counteract a moment that occurs due to the stiffness of the clutch structure, so that the second part of the disc 3 is axially tightened in a decreasing way in the opposite direction to its stiffness, i.e. with increasing axial deviation, with lower contact force, with the annular component 4 and corresponding to the axial displacement of the first disc part 2 and therefore of the annular component 4, friction of the second disc part 3 with the annular component in the radial direction is generated .

The action of the damping device thus formed is illustrated in more detail with the help of the diagram shown in Figure 2. In the drive chain, depending on the number of revolutions U of the heat engine, vibrations are generated with the amplitude A. L Example of execution of a torque transmission device 1 is adapted to the elimination of these vibrations and shows the behavior 50, represented in Figure 2, with respect to a behavior 51 of a Flexible Flywheel, or of an axially flexible flywheel according to the state of the art, without the second disk part 2.

In a motor speed range U from Uj * <»> 2000 / min to U2 = * 6000 / min, an excitation of the drive chain occurs compared to the prior art only at high speeds U, for example at about 4000 revolutions per minute. The amplitude of the maximum excitation is also reduced by half in execution 1 compared to the state of the art. The vibration behavior has up to high rpm - rarely used - in the entire rpm range, lower vibration amplitudes compared to a version without the second part of the disc 3.

Figures 3 to 8 represent a further example of execution of torque transmission devices according to the invention, in which only the upper half of the device rotating around the axis of rotation is shown in section, and which coincide with the exemplary embodiment 1 of figure 1 except for the differences described for the corresponding figures, so that the explanations provided in relation to figure 1 - if transferable - are also to be applied to the exemplary embodiments described below.

Figure 3 shows an embodiment example of a torque transmission device 101, in which the first disc part 102 has a surrounding rib 123 to optimize the axial stiffness of the torque transmission device 101, where the rib 123 has preferably the recess axially in the direction of the second disc part 103.

The second disc part 103 is axially housed between the reinforcement ring 105 and the first disc part 102 on the crankshaft 108.

The annular component 104 is provided as a clutch thrust plate for housing the clutch and has on the front side, not facing the crankshaft 108, a shoulder 124, on which the second disc part 103. In this case, the clamping takes place axially against the first disc part 102 with a progressive contact force, i.e. the contact force and the resulting frictional engagement increase with increasing deviation of the first disc part 102 For the attachment of a defined friction surface, which does not fit into the shoulder 124, the second disc portion 103 is conducted axially in an arc shape around the shoulder 124 and on the outer contour moves axially away from the shoulder 124, so that the frictional engagement takes place via a surrounding contact surface 125, with the annular shaped component 104.

Figure 4 shows a further possibility of providing a radially effective friction device in a torque transmission device 201. The second disc part 203 is axially clamped between the annular component 204 and the first disc part 202, without the disc part 203 being fixed on the crankshaft. For the radial fixing of the second disc part 2, which can be performed as a membrane or cup spring with corresponding axial elasticity, a shoulder 224 is needed which joins radially internally to the part 203, provided in the annular component 204. The spring acts, in the event of axial deviation of the first disc part, in a decreasing manner and can cause a frictional engagement on its outer and inner periphery, where the second disc 203 is deviated in the event of a deviation of the first disc part 202 , due to its compression, radially inwards and thus causes frictional engagement.

It is understood that the second disc part 202 on the outer and / or inner periphery may have tabs distributed along the periphery, extending radially outward - not shown here - which engage in corresponding openings or moldings of the disc part 202 and / or of the annular component 204, and therefore fix in the peripheral direction and / or in the radial direction at least one of the parts 202, 204, where for the fixing of the second disk part 203 on the first disk part 202 and / or on the component of annular shape, other means can also be used, for example profiles complementary to each other.

Figure 5 shows a similar example of a torque transmission device 301, in which the second disc part 303 is engaged without loss, by means of extensions 325 provided along the outer periphery, axially oriented, with the component of annular shape 304 by means of embossing 324 correspondingly distributed along the periphery. The frictional engagement in the radial direction can always still take place on both sides 302, 304.

Figure 6 shows an embodiment example of a torque transmission device 401, in which at least a radially elastic disc part 403 at least on the outer periphery is clamped on the outer periphery with the inner circumference, which for this purpose has a surface of corresponding bearing 423, of the annular component 404. For the optimization of the friction surface, the disc part for this purpose on the external periphery is reentering all around radiating towards the inside.

A damping takes place by turning the first disc part 402 over the screws 409 as a pivot point. In this case the first disc part 412 supports radially on the second disc part 403 and causes an axial frictional engagement between the annular shaped component 404 and the second disc part 403.

The torque transmission device 501 shown in Figure 7 follows the principle underlying the torque transmission device 401, with a modified construction solution. For this purpose the reinforcement ring 505 as the second disc part is executed radially outwards and axially in such a way that a surrounding gap is formed between it and the annular component 504. In this slot is introduced a corrugated ring 526 with a rectangular cross section with axial tension, which with its external corrugations 526a causes friction on the inner circumference of the annular component 504 and with its internal corrugations 526b friction on the external circumference of the ring reinforcement 505. Thus a damping device is formed which in the event of axial deviations of the first disc part 502 opposes the deviation, thanks to the spring constant of the corrugated ring 526, a radial spring force via the annular component, and defines an axial frictional engagement by rubbing the reinforcement ring 505 against the annular shaped component 504.

Against a deviation of the corrugated ring in the axial direction, a shoulder 524, provided in the annular component, or the ribs 523 of the first disc part, is needed in another direction.

In figure 8 the corrugated ring 526 of figure 7 with rectangular cross section is replaced by a corrugated ring 626 with circular cross section. The axial fastening takes place by means of a surrounding groove 604, provided in the annular shaped component 604.

Figure 9 shows a longitudinal section of an embodiment example of a torque transmission device 701, which is identical to the torque transmission device 1 of Figure 1 except for the differences described below.

The connection of the disc part 702 in this embodiment example does not take place directly with the annular component 704, which can be a thrust plate for a friction clutch, but rather by means of a snap ring or by means of leaf springs distributed along the periphery, to the first end of which the annular-shaped component 702 is fixedly applied, for example riveted, and to the other end of which the annular-shaped component 704 is fixedly applied, for example riveted. The axial stiffness of the snap ring or leaf spring 750 can be adapted in this case to the axial stiffness of the disc part 702, whereby additional damping of the axial and / or bending vibrations of the crankshaft can be achieved, not shown in this figure, in the direction of the drive chain. In particular applications the disc part 702 can be made relatively rigid, for example more rigid than for the compensation of axial vibrations with respect to a resonant frequency in the range from 200 to 250 Hz, i.e. stiffer than a field, depending on the mass of the clutch, from 600 kg / mm to 2200 kg / mm, to damp axial vibrations to a large extent by means of the axially elastic means 750 in the force flow between the disc part 702 and the annular shaped component 704.

Furthermore, for the execution of a damping system, the second part of the disc 703 can be tightened with the annular component 704 with the formation of a friction device by means of a frictional engagement. An additional alternative friction device 751 may be provided between a component of the disc portion 702, such as the ignition marking ring 711, and an annularly shaped component of the component 704, such as a shoulder 752 radially expanding its external circumference, which can consist of annular segments distributed along the circumference by a passing nose, which in the case of a relative movement of the two parts 702, 704, forms a frictional moment.

In the torque transmission devices according to the invention, as here in the embodiment example 701, an axial stop can be provided between the two parts 702, 704, which can be arranged in the area of the outer periphery and is formed here by the crown starting ring 719 and the ignition marking ring 711, which are axially spaced from each other with the distance x in the state of equilibrium. The distance x can assume a value less than 1 mm, preferably a value less than 0.3 mm.

The connection means 750, thanks to their reduced heat flow, thermally insulate the disc part 702 sufficiently from the annular component 704, which for example as a clutch thrust plate is subjected to large temperature fluctuations as a result of the friction engagement with the friction linings. Advantageously, the connection means are made of a material with reduced thermal conductivity, for example alloy steel. The combination of an axially flexible material with a material with poor thermal conductivity is particularly advantageous.

Figure 9a shows a snap ring 750, which forms the connection of the two parts 702, 704 (figure 9), which ring is formed by several segments of snap ring 750a, preferably four. The elastic ring segments are connected in a fixed manner, for example riveted or screwed, by means of openings 753, 754 alternating along the circumference, with the disc part 702 and the component 704 of annular shape. Contrary to the use of leaf springs which also act advantageously, the segments of the elastic ring 750 are axially oversized, so that the axial stiffness can be in a higher range. A further exemplary embodiment provides for superimposing the snap ring segments 750 and by means of a fastening means acting in the openings 753 of two snap ring segments, for fixing the disc part 702 or the annular component 704 and by means of of aperture 754 the respective other component.

Figure 9b shows a closed elastic ring 750b for the axially flexible connection in particular of the parts 702, 704 of Figure 9, where the openings 753a, 754a house fixing means 713, 13a, alternating along the periphery, of Figure 9, for secure the disc part 702 with the annular shaped component 704.

Generally, the connecting piece 750 of Figure 9 can have an elastic constant - seen in the axial direction - single-stage or multistage, for which for example the snap ring segments 750a and the snap ring 750b can present in the circumferential direction between the openings 753, 754 respectively 753a, 754a an axial profile 755 respectively 755a, which divides the elastic range between two openings 753, 754 respectively 753a, 754a in at least two different flexible beams.

The torque transmission device 701 of Figure 9 can be completed with the spring means 702, 750 previously described and the friction devices to form a damping system for damping axial vibrations, which can be specially adapted to each type of engine. thermal, drive chain and vehicle. For this purpose, in particular, the damping devices can be combined individually or together, single or multistage, and several friction devices, for example two, which form different frictional moments. In particular, it may be advantageous to combine friction devices, which provide axial and radial friction parts, together. It may also be advantageous to provide for bending vibrations and axial vibrations preferred damping devices, wherein the bending vibrations can be damped by means of damping devices preferably arranged in the radially outer zone. Thus for example it may be advantageous to damp one type of vibration - bending vibration or axial vibration - preferably with the connection means 750 of Figure 9, while the other type of vibration can be damped predominantly by means of the elastic disc part 702 ( figure 9). From the point of view of the vibration technique, thanks to the introduction of one or more damping elements (for example the elastic ring 750) with different elastic constant, possibly in interaction with at least one friction device, where in the case of radially friction devices As a result of the increased axial friction path, a higher friction work is provided, therefore such friction devices can be particularly advantageous, the number of possible resonance maxima can be increased, so that a torque transmission device adapted thereby to a drive chain can approximately specifically dampen e.g. a typical resonance maximum of an axial vibration between 200 and 300 Hz and a resonance maximum for a field bending vibration of 600 to 800 Hz, and thus a better adaptation to the corresponding drive chain. With this it is possible both to provide damping devices according to the principle of the low-pass filter, per se known, with bending axial vibrations, and to individually dampen the single resonance frequencies.

Figure 10 shows a partial section of an embodiment example of a torque transmission device 801, in which the disc part 802 is directly connected to the annular component 804 by means of the fastening means 813, for example rivets. In the immediate vicinity of the fastening means 813, the disc part is provided with a division 856, which is provided, in the example shown, in the form of a circular segment radially outward in connection with a further division 856 radially inward fixing means. The view A of Figure 10, shown in Figure 10a, illustrates the cutting guide of the divisions 856, 856a for a fixing means 813, which are uniformly distributed along the entire periphery.

Figures 10b-10e show further advantageous execution possibilities, where in Figure 10b only a radially internal division 856 is provided, in Figure 10c only a radially external division 856 and in Figures 10d and 10e respectively, divisions 856b, 856c, radially surrounding the means 813, i.e. radially from the outside 856c, figure 10e and radially from the inside 856b, figure 10d.

The advantages of the torque transmission device 801 with the divisions 856, 856a, 856b, 856c which can be executed in a variable way consist in a thermal insulation of the two parts 802, 804 with respect to each other and an axial flexibility, where the divisions they can be advantageously performed axially, for example by means of cold deformation techniques. The torque transmission device 801 can be economically manufactured thanks to the saving of a connection means such as 750 of Figure 9.

In an example of embodiment of a torque transmission device 901 - shown in Figure 11 -, similar to the torque transmission device 801, the divisions 956 are conducted with the formation of tabs 986 cut in the peripheral direction, where the tabs 986 they can be oriented in the traction and / or thrust direction of the torque transmission device 901 and / or they can be axially extracted. Fixing means 913 are housed in the tabs for connecting the disc part 902 with the annular component.

A partial view B of Figure 11 is shown in Figure 11a. Here by means of two fold edges 987, 987a, tongues 986 exposed axially approximately parallel are shown, which are arranged alternately in the pulling and pushing direction of the torque transmitting device 901. It is understood that all tongues 986 can be oriented in the direction of pulling or pushing. The advantages of the torque transmission device 901 largely correspond to those of the torque transmission device 801.

A further advantageous embodiment example of a torque transmission device 1001 is shown in Figure 12, the second disc part of which, which forms a frictional engagement with the annular-shaped component 1004 (compare with the disc part 3 in Figure 1) is connected in one piece with the connection means 1050. For this purpose the connection means, in this case the snap ring 1050, has extensions 1003 which are radially widened inwards and axially adapted to the offset towards the component 1004 of annular shape, which are axially clamped with the annular component 1004 and form a frictional engagement therewith.

Figure 12a shows a partial view of the elastic ring 1050 with openings 1054 for housing the fastening means 1013 for fastening the disc part 1002 and openings 1053 for housing the fastening means for fastening the component 1004 of annular shape. It is understood that the arrangement of the extensions 1003 can also take place on the fixing means for fixing the annular-shaped component. The radially inwardly oriented extensions are widened in the circumferential direction, for example to increase the contact surface with the annular component 1004.

Figure 12a shows a further possibility of executing extensions 1003 'on the elastic ring 1050'. Here the extensions 1003 'distributed along the circumference are separated from the body of the elastic ring 1050' and are fixed together with the fastening means for the disc part 1002 or the annular component 1004 (Figure 12). This version has advantages in particular when the material characteristics of the extensions 1003 must be different from those of the snap ring 1050 ', for example since the snap ring 1050' should also have thermally insulating characteristics.

Figures 13, 13a show further advantageous variants of a torque transmission device 1101, 1201, which do not require a second disc part (compare with 3, figure 1). The frictional engagement with the annular-shaped component 1104 in this embodiment example is formed by tongues 1103 respectively 1203, distributed along the circumference, positioned on the disc part 1102 respectively 1202. In this case the tongues 1103 of the transmission device torque 1101 (FIG. 13) are radially outwardly oriented and the tongues 1203 of the torque transmitting device 1201 (FIG. 13a) are radially inwardly oriented. The tabs 1203, 1103 can be arranged axially in such a way as to rest on the annular-shaped component 1104 with axial tension, which can be variably adjusted in its size. Figures 14 to 20 show advantageous embodiment examples of axially flexible disc parts in a split flywheel, where respectively the axially flexible disc part is axially clamped with a second disc part of lower stiffness. Therefore, in the contact zone of the two disc parts, a frictional contact is formed in the case of a relative axial movement of the parts relative to each other, which can result in a damping of the axial vibration. In the same way, a relative rotability of the two parts with respect to each other can also be provided, so that a friction device in the circumferential direction is also provided, where here the axially flexible disc part is associated with the primary side or with the secondary side and the second part of the disc, less rigid, is axially clamped between components of the primary side on one side and of the secondary side on the other side.

Figures 14 to 16 show exemplary embodiments, which have an axially flexible disc part in the primary region and Figures 17 to 20 axially flexible disc parts, arranged on the secondary side.

Figure 14 shows a torque transmission device such as flywheel 1301 divided into partial section. The axially flexible primary disk portion 1302 is housed and riveted to a hub 1302a, where the hub is fixed for example by means of screws to the crankshaft not shown. The primary disk portion radially outwardly forms with a flange portion 1302c a chamber 1350b with retracted feed devices 1302d for the peripherally effective energy accumulators 1350. Radially within the energy accumulators 1350, a disk portion 1303 is applied to the primary disk portion 1302, for example, as shown here, riveted, and is axially clamped along its inner periphery with the disk portion 1302. Therefore, in the zone 133a between the disc part 1302 and the disc part 1303 with lower rigidity, a frictional contact is formed in the case of a relative movement of the two parts relative to each other, so that in the event of axial vibrations of the part of the disc 1302 can be damped.

The secondary disc part 1360 is supported by means of a bearing 1361 on the hub 1302a, and is rotatable in a relative manner overcoming the action of the energy accumulator 1350 respectively of the energy accumulators 1350a, belonging to a second shock absorber stage, with respect to the part of the disc 1302. For the stressing of the secondary side of the energy accumulators 1350 respectively 1350a, a part of flange 1370 having corresponding recesses, for example riveted, is integrally connected in the rotation with the secondary disc part 1360. The secondary disc portion 1360 houses a friction clutch - not shown -.

Figure 15 shows a structure, similar to Figure 14, of a split flywheel 1401 with an axially flexible primary disc part 1402, a secondary disc part 1460 rotatable relative to the disc part 1402, overcoming the action of energy accumulators 1450 , as well as a disk portion 1403 of reduced rigidity relative to the rigidity of disk portion 1402, which disk portion 1403 with the primary disk portion 1402 and a support dome 1460a for the secondary disk portion 1460 is housed in common on the 'crankshaft - not shown - and is axially clamped in the region 1403a with the disc part 1402 and therefore performs a frictional contact, which in the event of axial vibrations of the primary side, in particular of the disc part 1402, can exert a damping action.

Figure 16 shows an embodiment example of a split flywheel 1501, which largely corresponds to the embodiment example 1401 of Figure 15, where for this purpose the second disc part 1503 is differently housed with the primary disc part 1502 radially inside on the crankshaft - not shown - and is axially tightened radially at the height of the energy accumulators 1550 with the disc part 1502, where the less rigid disc part 1503 is centered on the disc part 1502 by means of the centering nose 1503a. Furthermore, the disc part 1503 in the region of its outer periphery has markings 1503b for managing the engine, which are evaluated by a correspondingly arranged and designed sensor, not shown in more detail. The disc portion 1502 is axially deformed along its outer periphery and is provided with an additional primary mass 1502a. The split flywheels 1403 and 1303 of Figures 14 and 15 have these primary masses in a more or less reduced range, where on the disc part 1302 of Figure 14 the flywheel mass is substantially formed by the shape of the disc part and the additional disc part 1302c as well as from the starter crown.

In the exemplary embodiment of a split flywheel 1601 of Figure 17, the secondary side is axially flexible and the secondary flywheel mass is axially clamped against the secondary disc part by means of a less rigid disc part.

The structure of the split flywheel 1601 is divided in this case into a primary disc part 1602, which is housed on the crankshaft, a secondary disc part 1660, which is rotatably housed on a support flange 1660a, applied on the primary side, and a secondary flywheel part 1661, fixedly connected to the secondary disc part 1660, for example riveted.

Part of the secondary disk 1660 and part of the primary disk 1602 are supported in a relatively rotatable way overcoming the action of the energy accumulators 1650, where these on the primary side are stressed by pockets or niches 1602a set and on the secondary side by a flange 1660b, oriented radially, with corresponding 1665 recesses. Radially between the bearing, for example here a plain bearing 1660d, and the rivets 1662 distributed along the periphery, which connect the flange 1660d to each other, and the flywheel 1661 and the secondary disc part 1660, the disc part 1660 is made flexible axially, so that axial vibrations introduced by the crankshaft through the disc part 1602, for example bending vibrations in the secondary zone, can be isolated and thus can be kept largely away from the clutch - not shown in more detail - for example a friction clutch.

For this purpose, axially between the flywheel mass 1661 and the secondary disc part 1660 the disc part 1603 reduced in its axial stiffness with respect to the disc part 1660 is clamped, where in the exemplary embodiment shown the disc part 1603 is supported on a stop shoulder 166a, protruding radially, along the inner periphery of the flywheel mass 1661 against the secondary disc part 1660, and possibly in the case of a relative movement of the two parts 1661, 1660, establishes a frictional moment, preferably in the cross-zone. In this case the disc part 1660 and / or the flywheel part 1661 can serve as a friction partner.

Figure 18 shows, except for differences to be illustrated in more detail below, a split flywheel 1701, as described based on the embodiment example 1601 of Figure 17.

Different from flywheel 1601 of Figure 17 is the configuration of the connection between the flange piece 1760 and the flywheel part 1761. Here these two parts 1760, 1761 are connected by means of an axially flexible disc part 1765, which is formed also from a plurality of disc segments distributed along the periphery, for example radially inward by means of rivets 1766 distributed along the periphery on the secondary disc part 1760 and radially outward by means of rivets 1766, distributed along the periphery, with the flywheel mass part 1761. The secondary disc part 1760 can form in this case the radial flange 1760b in one piece with the stress devices 1760c and has an increased stiffness compared to the more axially flexible disc part 1765, so that by the disc part 1702 from the clutch is isolated vibrations introduced axially by the crankshaft and / or bending vibrations substantially on the disc part 1765.

Radially outside of the 1767 rivet circle the 1761 flywheel is axially tightened with the 1760b flange, then with the 1760 secondary disc part, where the axial tightening means is again a 1703 disc part, which is weaker designed as far as relates to its stiffness with respect to the disc portion 1765. As shown, the disc portion rests on the flange 1760b and abuts radially inwardly on the disc portion 1765 respectively on the associated rivets 1767. A frictional moment can be established both between the flange portion 1760b and / or the disc portion 1765 on one side and the disc portion 1703 on the other side. It is understood that the disc portion 1765 can also be radially connected within the fastener on the secondary disc portion 1760 with the flywheel portion 1761.

Figure 19 shows an embodiment example of a split flywheel 1801, in which the disc portion 1802 is axially flexible and supported axially against the secondary side. For this purpose the disc part 1803, for example a cup spring, is axially clamped between the secondary side and a flange part 1802, where the flange part 1802a is fixedly connected with the primary disc part 1802, for welded example, and forms the chamber 1850a for housing the energy accumulators 1850. In the exemplary embodiment shown the disc part 1803 is axially supported, rotatably relative to the disc part 1802, between the primary mass part 1861, which is supported directly on the primary side on a support flange 1802b, which is connected again with the crankshaft and primary disc part 1802, and flange part 1861b, which represents the secondary side biasing device for energy accumulators 1850, for example by means of rivets 1862 distributed along the periphery. In this case, a frictional contact is formed in the zone 1803a between the disc part 1803 and the flange part 1802a - here on the outer contour of the disc part 1803. This frictional contact is subjected to a frictional moment both in the case of relative axial movement of the primary disc part 1802 due to axial vibrations respectively of bending and in the case of a relative rotation of the disc part 1802 with respect to the flywheel mass part 1861, thus acts as a friction device for axial vibrations respectively bending and for torsional vibrations, as known per se from friction devices of split flywheels. In the case of increased stiffness in the axial direction it can be advantageous for the reduction of the basic friction in the case of a relative rotation of the two components 1802, 1861, to rotatably support the disc part 1803 relative to the secondary side, for example by means of a plain bearing. In this case, it can also be advantageous to provide a rotability with play, so that a friction device with a rotational play can be obtained from the friction device originally designed as a base friction.

Figure 20 shows in principle the structure of a split flywheel 1901 similar to the embodiment example 1801 in figure 19, where a spring is opposed to the spring force of the disc part 1903 between the flange part 1902a and the flywheel 1961 1903a, which is supported axially on the disc part 1903 and on a shoulder 1961a of the flywheel mass part 1961. The spring constants of the two cup springs 1903, 1903a are advantageously adapted in such a way that they act on the bearing surface 1902b a small axial force and a large axial force acts on the bearing surface 1903b of the two cup springs 1903, 1903a. From this it results for a relative movement between the primary side and the secondary side, therefore between the disc part 1902 with the flange part 1902b on one side and the flywheel mass part 1961 with the flange part 1961b on the other side, winning the 'effect of the energy accumulators 1950, a small frictional moment in the friction zone 1902b and in case of axial vibrations of the disc part 1902 with the flange part 1902a against the flywheel mass part 1961 a large frictional moment on the surface of support 1903b.

The patent claims filed with the application are proposed for formulation without prejudice to obtaining further patent protection. The Applicant reserves the right to claim still further characteristics disclosed so far only in the description and / or in the drawings.

References used in sub-claims refer to the further execution of the object of the main claim through the characteristics of the respective sub-claim; they are not to be understood as a waiver of obtaining autonomous objective protection for the characteristics of the sub-claims containing the references.

However, the objects of these sub-claims also form autonomous inventions, which have a configuration independent of the objects of the preceding sub-claims.

Furthermore, the invention is not limited to the exemplary embodiments of the description. On the other hand, numerous variations and modifications are possible within the scope of the invention, in particular variations, elements and combinations and / or materials, which are inventive for example by combining or modifying individual characteristics or elements or process steps, described in connection with the general description and the embodiments as well as the claims and contained in the drawings, and by means of combinable characteristics lead to a new object or to new process steps or sequences of process steps, also as regards manufacturing, test and work processes.

Claims (65)

CLAIMS 1. Torque transmission device for connecting a crankshaft of an internal combustion engine with a power take-off part of a drive chain, in particular a friction clutch or a liquid clutch such as a Fottinger clutch or a converter hydrodynamic, consisting of at least a first part of an axially flexible disc, connectable to the crankshaft, to which an annular component is connected in a radially external area, which forms the connection with the drive part, characterized by the the fact that the first disc part with the annular shaped component is clamped by means of a second axially resilient disc part. 2. Torque transmission device for connecting a crankshaft of an internal combustion engine with a drive part of a drive chain, in particular a friction clutch or a liquid clutch, such as Fottinger clutch or converter hydrodynamic, consisting of at least a first disk part connectable to the crankshaft, to which an annular component is connected in a radially external area, which forms the connection with the drive part, characterized in that the annular component is flexibly connected axially with the first disc part. 3. Torque transmission device for connecting a crankshaft of an internal combustion engine with a drive part of a drive chain, in particular a friction clutch, consisting of at least a disc part and a component annular in shape, which forms a connection with a drive part, characterized in that the disc part and the annular shaped component are thermally insulated from each other. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part with the annular component forms a damping device for the suppression of axial vibrations of the first disc part. 5. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is housed with the first disc part on the crankshaft. 6. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is clamped by means of an axial front surface with a front side, facing the first disc part, of the component annular in shape. 7. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is clamped by means of an axial front surface with a front side, not facing the first disc part, of the annular component. 8. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is fixed on the first disc part or on the annular component. 9. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is connected radially outside the crankshaft with the first disc part and / or with the annular shape. 10. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part forms a frictional engagement with the annular component or with the first disc part. 11. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part has a lower axial stiffness than the first disc part. Twisting moment transmission device, in particular according to one of the preceding claims, characterized in that the second disc part has tongues oriented radially outwards, distributed along the periphery, which are axially clamped with the annular component . 13. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second component is housed in a connection of the first disc part with the annular component. 14. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second component is axially housed between the first disc part and the annular component. 15. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part has tabs distributed along the periphery, facing radially inwards, which make a frictional contact with the component annular shape or with the first part of the disc. Torque-transmitting device, in particular according to one of the preceding claims, characterized in that the tabs are extended radially inward on one side or on both sides in the circumferential direction. 17. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is formed by an energy accumulator which develops an axial spring effect. 18. Torque transmission device, in particular according to one of the preceding claims, characterized in that the energy accumulator is an elastic ring. 19. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is at least in two pieces. 20. Device for transmitting torque, in particular according to one of the preceding claims, characterized in that the second disc part consists of the elastic ring and tongues formed as separate parts. 21. Torque transmission device, in particular according to one of the preceding claims, characterized in that the snap ring is formed by at least two snap ring segments. 22. Torque transmission device, in particular according to one of the preceding claims, characterized in that the elastic ring is connected along the circumference alternately with the disc part and with the annular component. 23. Torque transmission device, in particular according to one of the preceding claims, characterized in that a relative axial movement between the disc part and the annular component is limited. 24. Torque transmission device, in particular according to one of the preceding claims, characterized in that an axial effect of the energy accumulator which is axially effective with respect to a relative axial movement of the disc part and the annular component is single-stage or multistage. 25. Torque transmission device, in particular according to one of the preceding claims, characterized in that an axial effect of the axially effective energy accumulator is asymmetrical with respect to a relative axial movement of the disc part and the annular component in direction of the crankshaft or towards the drive part. 26. Torque transmission device for connecting a crankshaft of an internal combustion engine with a drive part of a drive chain, in particular of a friction clutch or a liquid clutch, such as Ftìttinger clutch or hydrodynamic converter, consisting at least of an axially flexible disc part, connectable to the crankshaft, to which an annular component is connected in a radially external area, which forms the connection with the drive part , characterized in that at least one radially extending tab is pushed out of the disc part, which is supported on the component. 27. Torque transmission device, in particular according to one of the preceding claims, characterized in that the at least one tongue is axially supported. 28. Torque transmission device, in particular according to one of the preceding claims, characterized in that the tongue forms a frictional engagement with the annular-shaped component. 29. Torque transmission device, in particular according to one of the preceding claims, characterized in that the connection of the first disc part with the annular component takes place by means of fastening means distributed along the circumference, in the immediate proximity of which at least one division is provided, provided with a part oriented in the circumferential direction, of the first part of the disc. 30. Torque transmission device, in particular according to one of the preceding claims, characterized in that the division is arranged radially inside and / or radially outside the fixing means. 31. Torque transmission device, in particular according to one of the preceding claims, characterized in that the division is carried out in the form of a tab, where the fastening means is provided on the tab. 32. Torque transmission device, in particular according to one of the preceding claims, characterized in that the tongue is oriented radially or in a circumferential direction. 33. Torque transmission device, in particular according to one of the preceding claims, characterized in that the circumferentially oriented tabs, distributed along the circumference, are oriented unitarily in the thrust or traction direction or mixed in the direction of traction and thrust. 34. Torque transmission device for connecting the crankshaft of an internal combustion engine with a drive part of a drive chain, in particular of a friction clutch or a liquid clutch such as a Fòttinger clutch or hydrodynamic converter, consisting of at least a first part of an axially flexible disc, connectable to the crankshaft, to which an annular-shaped component is connected in a radially external area, which forms the connection with the drive part, characterized in that the second disc part is integrally housed in rotation on the crankshaft and is frictionally engaged with the annular component. 35. Torque transmission device, in particular according to one of the preceding claims, characterized in that the frictional engagement between the second disc part and the annular component takes place by means of a corrugated ring with corrugations oriented radially towards the outer, as a friction disc, where the corrugations are in frictional engagement along the outer circumference with the inner circumference of the annular shaped component and the undulations of the inner circumference are in frictional engagement with the outer periphery of the second disc part . 36. Torque transmission device, in particular according to one of the preceding claims, characterized in that the cross section of the corrugated ring is rectangular or circular. 37. Device for transmitting torque, in particular according to one of the preceding claims, characterized in that the second part of the disc, executed radially springing, is housed on the crankshaft and with its external periphery is directly in frictional engagement with the inner circumference of the annular component. 38. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is axially housed between the first disc part and a reinforcement ring on the crankshaft. 39. Torque transmission device, in particular according to one of the preceding claims, characterized in that the annular component is a thrust plate for a clutch. 40. Torque transmission device, in particular according to one of the preceding claims, characterized in that a starting crown is housed on the outer circumference of the annular-shaped component. 41. Torque transmission device, in particular according to one of the preceding claims, characterized in that the starting crown forms an axial stop for the first disc part. 42. Torque transmission device, in particular according to one of the preceding claims, characterized in that the toothed crown is housed on at least three axially oriented cams distributed along the circumference. 43. Torque transmission device, in particular according to one of the previous claims, characterized in that the cams are axially oriented in the direction of the crankshaft. 44. Torque-transmitting device, in particular according to one of the preceding claims, characterized in that the cams pass through recesses made correspondingly as a window in the first disc part. 45. Torque transmission device, in particular according to one of the preceding claims, characterized in that the first disc part has on the outer periphery a surrounding molding in the axial direction, in which the ignition marks are made. 46. Torque transmission device, in particular according to one of the preceding claims, characterized in that the first disc part extends radially outward axially between the starter crown and a mass part of the annular component. 47. Torque transmission device, in particular according to one of the preceding claims, characterized in that the first disc part has a surrounding rib between the annular component and a housing on the crankshaft radially 48. Torque transmission device, in particular according to one of the preceding claims, characterized in that the rib is axially retracted in the direction of the annular component. 49. Torque transmission device, in particular according to one of the preceding claims, characterized in that the first disc part is centered by means of the molding on the annular component. 50. Torque transmission device, in particular according to one of the preceding claims, characterized in that the annular component is riveted with the first disc part. 51. Torque transmission device, in particular according to one of the preceding claims, characterized in that the riveting takes place all around at radial height in the region of a bearing surface for friction linings of a friction clutch. 52. Torque transmission device, in particular according to one of the preceding claims, characterized in that a first axially flexible disc part is a component of a split flywheel with a primary flywheel mass and a secondary flywheel mass, rotatable in relative direction the first, in the opposite direction to an energy accumulator acting in the circumferential direction, and is axially clamped by means of a second disk part of lesser axial stiffness. 53. Torque transmission device, in particular according to one of the preceding claims, characterized in that the axially flexible disc part is associated with the primary flywheel mass or with the secondary flywheel mass. 54. Torque transmission device, in particular according to one of the preceding claims, characterized in that the part of the flexible disc is flexibly housed axially on the crankshaft. 55. Torque transmission device, in particular according to one of the preceding claims, characterized in that the axially flexible disc part forms a secondary disc part for housing a friction clutch, where a primary disc part, housed on the crankshaft, and the secondary disc part are supported on each other and are rotatable relative to each other in a circumferential direction overcoming the effect of at least one energy accumulator. 56. Torque transmission device, in particular according to one of the preceding claims, characterized in that the flexible disc part axially connects a thrust plate of the friction clutch and the secondary disc part to each other. 57. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is housed on the crankshaft and is axially clamped preferably radially outward with the primary disc part. 58. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is riveted radially inward or radially outward with the primary disc part along the periphery, and is clamped axially in the opposite direction radially with the primary disc part. 59. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is fixed to the secondary disc and is axially clamped against the primary disc part or against the thrust plate. 60. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is fixed to the thrust plate or to the primary disc part and is axially clamped against the secondary disc part or a component connected with this. 61. Torque transmission device, in particular according to one of the preceding claims, characterized in that the component connected with the secondary disc part is an axially effective energy accumulator. 62. Torque transmission device, in particular according to one of the preceding claims, characterized in that the second disc part is rotatable relatively towards the axially flexible first disc part. 63. Torque transmission device, in particular according to one of the preceding claims, characterized in that the first disc part is axially flexible with the second disc part in their bearing area by means of a relative rotation and / or a relative axial movement relative to each other form a friction device. 64. Torque transmission device, in particular according to one of the preceding claims, characterized in that the friction device is affected by play. 65. Invention, consisting of at least one feature disclosed in the application documents.