DE3745156C5 - Device for damping vibrations - Google Patents

Abstract

Means for damping vibrations, in particular between a motor and a clutch in a drive train, with zwiszen two flywheel elements vorzusehender damping arrangement, wherein the input part, the first, connectable to the engine, and the output part, the second, a counter-friction surface for engaging a friction disc of the clutch Flywheel element is characterized by the following features:
a) the damping arrangement has a radially outwardly closed, annular chamber (30) radially outwardly forms an annular channel (51), in the energy storage, such as springs, are added.
b) on the lateral boundary wall of the annular channel (51) are provided first support areas for acting on ends of the energy accumulators,
c) in the annular channel (51, 151, 251, 551) projecting with the second flywheel element (4, 204, 504) in rotary closure flange body (41, 141, 241, 541), the second support portions for acting on power storage ends forms, in,
d) the force accumulators (45; 145; 245) provided between the first and second support regions allow the flywheel elements between the flywheel elements to be ...

Description

The The invention relates to a device for damping vibrations, in particular between an engine and a clutch in a drive train, with damping arrangement to be provided between two flywheel elements, wherein the input part of the one, connectable to the motor and the Output part the other, a Gegenreibfläche to attack a friction disc the clutch having flywheel element is.

Such devices, such as those by the DE 35 20 853 C2 have proposed, as a damping means usually between the flywheel elements both circumferentially effective energy storage, such as coil springs that store energy, as well as axially effective energy storage, which cause friction in conjunction with friction or sliding linings, ie a hysteresis, the connected in parallel with the force accumulators acting in the circumferential direction.

Such Facilities although in certain applications relatively good improvements in vibration or noise behavior however, in many cases these are a compromise solution. How to do it these purely mechanical solutions not, the wide range of pending demands on the various Operating conditions, the completely different vibration and noise behavior have to cover. They would be so the more expensive and therefore more expensive, if tried, many operating conditions to capture, since for additional Amplitude ranges additional and more complicated measures required are. In particular, such facilities not, the damping characteristic to several changing ones Operational conditions, among other things not because the individual damper stages or the circumferentially effective energy storage associated Hysteresis is not dependent change the conditions occurring can. They are as well wear- and prone to failure.

at the previous facilities of the type mentioned is still between the flywheel elements a relatively small torsionally elastic Relative rotation possible, why at least about a big Range of this relative rotation, the damping rate of the flywheel elements effective damping means relatively high is. For many applications would it be However, it is advantageous to better damp the vibrations achieve when big Relative rotations between the flywheel elements would be present because namely thereby vibrations with great Amplitude better damped could become.

By DE-AS 28 48 748 is a flexible coupling in disc design has been proposed, which has a liquid-fillable housing in which springs as well as special displacement chambers are arranged. The housing forming Components are connected to the output shaft of an engine and into the casing protruding center disc over an inner hub directly connected to a shaft to be driven. This document thus does not relate to devices with two flywheel elements according to the beginning type described. Such a flexible coupling in disc design has the further disadvantage that due the arrangement of the displacement chambers for the radially outside in the housing provided springs relatively little Space remains in the circumferential direction, so that only a small relative torsion angle between the case and the center disc possible is.

Of the Present invention had the object, facilities of to improve the type described above, in particular their damping effect, so that one Optimal filtration of the engine and transmission Vibrations at both low and high speeds, at resonance speeds, during starting or when parking or the like is achieved. Furthermore, the possibility should be created the damping characteristic, i.e. the measure of energy destruction to the different vibration and noise behavior of a vehicle unterverschiedenen To be able to adapt to operating conditions and other influences. In addition, the should Inventive device be produced in a particularly simple and cost-effective manner. In particular, by constructive measures a low production cost by using one as possible high proportion of non-cutting production are made possible. Also should the Minimized wear and tear prolongs the life become. Furthermore, a crowded and thus space-saving design, especially in the axial direction, be guaranteed.

• a) die Dämpfungsvorkehrung besitzt eine radial nach außen geschlossene, ringförmige Kammer, die radial außen einen Ringkanal bildet, in dem Kraftspeicher, wie Federn, aufgenommen sind,
• b) an den seitlichen Begrenzungswandungen des Ringkanals sind erste Abstützbereiche zur Beaufschlagung von Endender Kraftspeicher vorgesehen,
• c) in den Ringkanal ragt ein mit dem zweiten Schwungradelement in Drehschluß stehender Flanschkörper, der zweite Abstützbereiche zur Beaufschlagung von Kraftspeicherenden bildet, hinein,
• d) die zwischen ersten und zweiten Abstützbereichen vorgesehenen Kraftspeicher lassen zwischen den Schwungradelementen mindestens eine relative Verdrehung von ± 25 Grad, ausgehend von einer Mittelstellung, zu,
• e) das den Ringkanal bildende Schwungradelement besitzt Abschnitte, welche die Kraftspeicher axial übergreifen und fliehkraftmäßig abstützen.

According to the invention, this is achieved in that the device according to the invention has the following features:

• a) the damping arrangement has a radially outwardly closed, annular chamber which forms a ring channel radially outside, in which energy accumulators, such as springs, are accommodated,
• b) on the lateral boundary walls of the annular channel first support areas are provided for loading Endender the energy storage,
• c) in the annular channel projects with the second flywheel element in rotational closure flange body, the second support areas for Admission of forces storing ends into,
• d) the force accumulators provided between the first and second support regions allow at least a relative rotation of ± 25 degrees between the flywheel elements, starting from a middle position,
• e) the flywheel element forming the annular channel has sections which axially overlap the force accumulators and support them with centrifugal force.

By the features of the invention will an embodiment of the device allows for a flawless guide or support ensured recorded in the annular channel springs, so that these Feathers relatively long can be trained and thus a big one Angle of rotation between the two flywheel elements is made possible. This can provide better damping of the achieved between the flywheel elements occurring vibrations be there because of the possible huge Relative rotations between the flywheel elements, between this effective attenuation rate over a huge or even over almost the entire angle of rotation can be relatively low. The damping rate can be the smaller, the larger the possible angle of rotation is.

By the embodiment of the invention Facility can So long, one-piece Feathers with a relatively small Stiffness, but with great Be used 'travel, which the previously mentioned allow low damping rate. Because of the possible huge Twist angle while low attenuation rate can both Big vibrations Amplitude or large Alternating torque peaks as well as small amplitude oscillations or smaller alternating torques are damped or filtered. Thus, in all operating conditions of the engine is a flawless damping the occurring vibrations possible.

For the assembly and the function of a device designed according to the invention It may be particularly advantageous if at "n" springs, or energy stores on the same Diameter, where 2 ≤ n ≤ 4, the individual Springs or energy storage over 70 - 96 % of an angle sector, the angle sector being 360 degrees / n is.

Especially when using long one-piece Feathers can do it for the mounting be particularly advantageous if this at least approximately the radius on which they are placed, are pre-curved. As a result, the insertion into the provided for the springs channel-like Recordings considerably easier, since no additional measures are required, to keep the springs in a curved position during assembly.

For the vibrational decoupling of the two flywheel elements, it is particularly advantageous if the radially outside arranged in the chamber energy storage a resilient torsional stiffness cause that in the order of magnitude from 2 to 15 Nm per degree. It has many applications proved to be particularly useful if the energy storage a torsional rigidity in the order from 2 to 4 Nm per degree between the two flywheel elements produce.

The Chamber or the annular channel can at least in the radially outer region be formed such that the corresponding boundary surfaces the outer cross section the energy store is aligned. By such a design can be an extra Improvement of radial support as well the leadership achieved the energy storage within the chamber or the annular channel become.

For the construction and the function of the device can continue to be particularly advantageous be if one of the chamber limiting components a starter ring gear wearing.

The Spring rate or the stiffness of the springs between the Flywheel elements formed elastic damper can be of the order of magnitude between 2 to 20 Nm / degree, preferably between 4 to 15 Nm / degree lie. Especially useful it may be if this spring rate or rigidity over at least one angle of rotation of 15 degrees between the two flywheel elements in the pulling direction and / or is present in the thrust direction.

When advantageous, it may continue to prove, if the annular channel at least partially with viscous medium, such as a pasty agent, filled is. It may also be appropriate if in a device according to the invention - in the circumferential direction of Institution considered - the Force storage between their respective assigned support areas Centrifugally supported.

Furthermore, by the compressing and relaxing the long springs and as a result of the movement of the portions of the flange, which protrude into the annular channel, occurring turbulence or displacement of the recorded in the annular channel viscous medium, a viscous or hydraulic damping can be generated. which changes as a function of the angular velocities or accelerations occurring as a result of torque fluctuations or torsional vibrations between the two flywheel elements. Another advantage is that the attenuation caused by the viscous medium is variable in Ab dependence of the speed of the motor. It can thus be changed depending on the angular velocity between the two flywheel elements and in dependence of the speed of the device, the damping ratio or the hysteresis and thus the entire damping characteristic of the device. By provided in the annular channel viscous medium thus not only large amplitude oscillations can be damped, which are caused by high torque surges or alternating moments, but also small amplitude oscillations, which must be damped with a correspondingly small hysteresis and which occur especially in load operation. This can be attributed to the fact that the pressure building up in the viscous medium depends on the instantaneous speed with which a certain volume of the viscous medium is displaced. This means, therefore, that the damping capacity of the viscous medium accommodated at least in the annular channel is dependent on whether shock moments or high alternating torques or smaller torque fluctuations occur between the two flywheel masses. So it can be achieved practically a selbstätige regulation of the damping effect.

By the use of curved springs can which reduces the stresses that occur during compression and continue to facilitate assembly.

The support areas for the Springs in the ring channel can in an advantageous manner by integrally formed on the flange radial arms are formed, which open into the radial regions of the annular channel. The Cantilevers while radially outside go over the support areas in a the spring in the circumferential direction cross-bridge. The - in the circumferential direction considered - respectively two webs connecting radial beams can be arranged in an annular recess be received, which connects radially outward to the annular channel.

The Webs can - in radial Direction - in be formed with respect to the annular channel such that at least at rotating device, the springs are essentially at this Support webs radially. This can be advantageous in particular if at least individual the stored energy storage in the annular channel successively to Come into effect, ie form a multi-level torsional elastic damping, and only after a relative twist angle between the two flywheel elements first insert springs over the Flange are positioned in the circumferential direction, since then during the Twist angle in which these springs are not compressed, this is rotate with the component, namely the flange on which they are supported radially, so that an additional friction damping between avoided these springs and the boundary surfaces of the annular channel can be.

One particularly advantageous construction of the device can be given when the annular channel is formed by two shell-like body, wherein at least one of these bodies a sheet metal part can be.

Especially may be appropriate it may be if the annular channel through two half-shell-shaped sheet metal parts is formed, this part of the motor connected Flywheel element can be or even form this flywheel element. An advantage of such Sheet metal parts opposite parts produced by brazing is substantially reduced Production expense. Furthermore are by punching, pulling and Shape produced sheet metal parts a variety of favorable embodiments possible, so can e.g. Also channel cross sections are produced inexpensively, by deviate from the rotationally symmetric shape. Also, the extensive supports for the Springs in the annular channel by embossing or bag-shaped Formations are formed so that no additional elements required are to ensure this function.

The supports or attacks in the ring channel for the end portions of the springs can but also formed in a simple manner by individual elements who are in the otherwise over the circumference continuously formed annular channel are used. These elements can by riveted blocks or platelets, be formed by molding rivets or by welded moldings.

to impeccable loading of the springs received in the annular channel it is appropriate if - in the neutral position of the damper or the institution - on both sides a Flanschauslegers a pocket-shaped molding or another Stop element is provided.

In order to obtain a multi-stage torsionally elastic damping, at least in one direction of rotation, starting from a middle position or a middle region of the two flywheel elements relative to one another, it can be advantageous if at least one arm of the flange body is supported relative to the supports provided on both sides by the annular channel. viewed in the circumferential direction - has a smaller extension. In this case, the boom and the supports can be arranged in the mentioned starting position with respect to each other such that their Beaufschlagungsbereiche are offset in both directions relative to each other, so that there is a multi-stage torsionally elastic damping in both directions of rotation. In the mentioned starting position, the Beaufschla However, supply areas of the boom for the energy storage and the supports should also be flush on one side, so that then results in only one direction of rotation graded torsionally elastic damping.

The Application areas of the booms and the supports can However, in relation to the spring ends also be offset from each other in such a way that around the zero position of the relative rotation between the two flywheel elements over a certain Angle no suspension is present, so that then virtually no or only a hydraulic or viscous and / or a friction damping occur can. This damping can be very small.

A smaller extension of the boom of the flange against the supports the annular channel is particularly advantageous in Enrichtungen, at those first non-compressed spring (s) through the supports the annular channel is fixed in the circumferential direction or are.

at Facilities where only after a relative angle of rotation between the flywheel elements coming to effect energy storage over twist this relative twist angle with the flange body, it may be appropriate if at least one arm of the flange against the same on both sides provided supports in the ring channel - in Viewed in the circumferential direction - one has greater extension. It can the loading areas of the arms and outriggers only be offset in one direction of rotation to each other or even in both directions.

For the function The device may be particularly advantageous if at least between some of the arms of the flange body and their facing Spring-end liners are provided which have at least one cross-sectional area have, at least approximately adapted to the cross section of the spring receiving annular channel. By such a design of the intermediate layers act these in the annular channel with a relative rotation between the two flywheel elements like displacement pistons for the provided in this annular channel viscous medium. For better management of Spring ends can Intermediate layers on their side facing the respective spring end an extension projecting into the interior of the springs have. To a self-threading the extensions to allow in the spring ends, can These have a slightly conical area leading to the end in a larger cone angle or a dome-shaped Forming section passes. Thereby it can be ensured that if an intermediate layer or a spring cup in operation from a Spring end slips out or is pushed out, while relaxing the Spring or when the spring plunger latter is applied thread it back into the spring can, without this or he himself is damaged becomes.

Thereby that the Liners or the spring cups in the annular channel displacement piston for the viscous Can form medium this advantageously for the control of the viscous Medium generated damping be used. So it is possible in a particularly simple way, on the piston-like Liners the flow rate or the repressed Volume of viscous medium over a certain relative twist angle between the two flywheel elements to determine or regulate and thus a defined, characteristic attenuation curve dependent on to achieve certain operating parameters. The change of the torsional resistance generated by the viscous medium can in a simple way by change at least one flow area for the viscous medium done. This can be achieved, for example be that Ring channel at least over Subregions of the longitudinal extension at least one spring, which at both ends with intermediate layers or nibble the pen is provided, has no constant cross-section. In a relative movement between the annular channel and an intermediate layer can thus be the free cross-section between the annular channel and the intermediate layer in dependence change the angle of rotation. Appropriately to be there when at least some of the ones in the end sections the non-compressed springs located areas of the annular channel across from the rest Areas of this channel are extended in cross-section. such Cross-sectional extensions can over a certain Verdrehwinkelbereich progressively or it can also the cross-sectional changes abruptly respectively. To a perfect guidance of the To allow intermediate layers and the energy storage radially outside, it is expedient, such cross-sectional extensions in the area of the inner half to provide the annular channel.

The produced by the intermediate layers in connection with the viscous medium damping can continue by introducing axial Ausschitten or from axial recesses are changed in these liners.

For the function of the device, it may be advantageous if the arms of the flange body have circumferentially pointing lugs which engage in a recess of the intermediate layers. The lugs of the arms are arranged or formed with respect to their respective associated recess of the intermediate layers such that At least the end portions of the springs are held out of contact with the radially outer regions of the annular channel via the intermediate layers. The lugs of the boom can be designed such that upon loading the intermediate layers latter are pulled slightly radially inwardly through the lugs, and thus be lifted from the Ringkanalwandung. This ensures that even at high speed at least some of the end turns of the springs do not come to rest on the shell-like bodies, which form the annular channel, and thus springs can be free. It may be advantageous in this case if the recesses in the intermediate layers are annular in cross-section and the vases of the arms have at least regions adapted to the recesses. The latter can be done, for example, by embossing the previously punched-out noses. The Auslegernehmungen the intermediate layers can - viewed in the axial direction of the springs - be cone-shaped or spherical-like and form blind holes.

According to one Development of the invention may be radially within the annular channel provided at least one other spring group of the damping arrangement be. For some applications It may be advantageous if this further spring group with the provided in the annular channel first spring group between the flywheel elements is arranged in parallel. The arrangement of the individual Springs of the first and further spring group between the two flywheel elements can be made such that at least individual springs Both spring groups stepwise, that is angularly offset to the Wizkung come and / or at least individual springs of at least one spring group gradually, that is use angular offset.

According to one another embodiment of the invention the provided in the annular channel first spring group and the radially further arranged inside another spring group between the flywheel elements be arranged in series. The inside of these spring groups parallel connected springs can also form different stages, the angle offset to Effect come.

The Coupling of the at least two spring groups, which between the Flywheel elements are provided, in a simple manner by means of a flange carried out, which has corresponding receptacles for the individual springs. These shots can be advantageously formed in that the flange radially outward, through radial arms circumferentially separated from each other possesses, in which the springs of the first spring group are added are, as well as radially inner windows, in which the springs the further spring group are provided. The cutouts and the Windows can doing - in Viewed circumferentially - so be arranged relative to each other that radially within a cutout one window each. Cutouts and windows can be included at least approximately one same angular extent in the circumferential direction.

Around one possible huge Allow twist angle between the two flywheel elements, it may be advantageous if the first and / or the further spring group each having a maximum of four energy storage.

For the construction and the operation of the device can be particularly advantageous be if radially inside the annular channel, the housing halves or the shell-like bodies, like sheet metal parts, have facing areas that for the Flanschkärper form a passage. The mutually facing areas can be annular surfaces define a circular Passage or Limit gap, which opens into the annular channel. To achieve a very high damping through the recorded in the annular channel viscous medium, the passage width at least approximately the thickness of the flange correspond. For many use cases However, it may be advantageous if the axial distance between the facing areas is 0.1 mm to 2 mm larger as the thickness of the areas of the flange body received therein The gap defined thereby can be a part of the in the annular channel absorbed viscous medium in a sudden relative rotation escape radially inward between the two flywheel elements. By appropriate dimensioning of the gap, the by the im Ring channel contained viscous medium caused attenuation effect the wished Dimension determined become.

Farther Is it possible, the mutually facing portions of the housing halves and the housed therein Areas of the flange body with respect to each other in such a way that between these a function of the angle of rotation between the flywheel elements changing gap is present, wherein the defined by the gap flow area can decrease with increasing angle of rotation, causing the caused by the viscous medium damping is greater. For this purpose, the flange on at least one side extending in the circumferential direction and in the axial Direction have rising ramps, with trained accordingly Counter ramps of the housing area facing him on this page interact in such a way that if the ramps and counter ramps are moved toward each other, the flow area for the viscous medium becomes smaller.

For the construction The device may be particularly advantageous if radial within the inter-facing areas of the Housing halves existing Passage for the flange the further spring group is provided. For receiving this spring group can they Housing halves or the shell-like body axial Have indentations. For the function of the device can be particularly advantageous if the axial indentations, the passage for the flange body and the annular channel merge into one another. For perfect guidance the energy storage of the other, inner spring group may be appropriate if the recesses at least in the radially outer region of the circumference of the cross section this energy storage are aligned. The between ring channel and the indentations existing gap or passage for the flange can be substantially closed. For this purpose, the flange body a have annular region, at least partially extends radially in this gap. This can be advantageous annular region of the flange substantially by extending circumferentially radially between the outer and inner springs Webs are formed, which the loading areas of the flange body for the springs, like radial arms, connect with each other.

to Facilitate the assembly of the device, the springs of the others Spring group at least approximately the diameter is pre-curved be on which they are placed. This is especially true advantageous when it comes to long springs. Furthermore has the pre-bending of the Feathers of the outer and / or the inner spring group the advantage that they are in the installed state and are virtually free of bending moment in unclaimed device.

It may be advantageous if springs of the further spring group radially Outside through the windows of the hub body limited areas are so that these Feathers against rotating device as well as applying mainly against the radially outer contours the window of the hub body support and thus practically only in the axial direction through the indentations the housing parts guided So, that means, with minimal investment force along the slide the indentations bounding wall. In an advantageous manner Way you can the outer contours the window through between the outer and the the inner springs existing webs of the flange, extending in the circumferential direction extend, be formed. In order to prevent an installation of the spring ends on the housing, can the individual windows or the webs towards the end radially slightly behind pulled inside, who, so that the acted spring ends through the flange of the radially outer regions the recesses or the annular channel are retained radially.

For some use cases However, it may also be advantageous if the inner springs themselves at least under centrifugal force at the indentations limiting surfaces support radially. This can be advantageous for springs that only after a certain relative angle of rotation between the two flywheel elements be used. Furthermore, it may be for the function of the device be advantageous if the windows of the flange body for the inner springs in such a way are trained that they form circumferentially facing noses that directly into the Federenden engage or in a recess of an intermediate layer, the between a spring end and its associated Beaufschlagungsbereich of the flange body is provided. The noses can doing so with respect to the spring ends or on the intermediate layers be educated that they at least keep the end portions of the springs radially inward, so that these when applying except Stay in contact with the radially outer areas the recesses and / or the cross-webs of the flange. Thereby also arise in conjunction with the on the jibs of the flange body molded noses already described advantages.

For the. manufacturing The device may be particularly advantageous if the indentations for the other Spring group annular are, that is, over extend the entire scope of the device and the support areas in the circumferential direction for the energy storage by introduced into the indentations stop elements are formed. Such stop elements can by individual elements be formed as they are provided in the ring channel Stop elements have been described. Particularly advantageous can it may be when the stop elements are formed by form rivets, their areas of activity for the energy storage are flat or flattened.

For the construction and the function of the device may be advantageous if The springs of the inner spring group are recorded in windows of two panes that are with the other, connectable to the drive train flywheel element in rotary connection and axially between them, the radially outer and pick up the radially inner spring group in series coupling flange.

According to one embodiment of the invention, it may be particularly advantageous for the function and assembly of the device when the one flywheel element aufwei the one, a profile sending component of an axial connector and the other flywheel element has the opposite profile of the two flywheel elements rotationally coupled connector. Such a connector may be particularly useful in a device in which the spring groups of the damping arrangement are accommodated in a viscous or pasty medium at least partially fillable chamber, which is formed essentially by the components of a connectable to the engine flywheel element and wherein the output part of the damping arrangement is a flange-like component which has profilings which can be brought into engagement with counter-profiles provided on the other flywheel element, furthermore one of the flywheel elements carries a sealing element which seals against the surface of the other of the flywheel elements when the two flywheel elements are plugged together comes. Such a structure allows a pre-assembly in two modules, namely the connectable to the engine primary side and connectable via a coupling to the drive train secondary side assembly.

Advantageous it may be if the flange-like output part of the damping arrangement, like flange body, over the Profiles of the connector with the other flywheel element a rotational lock Coupling has, but not fixed axially. Through a such structure, the flange can be free in the axial direction align so that he when installing the device, not between the two flywheel elements is clamped, causing components of the device claimed inadmissible could become and one already starting at small angles of rotation, for example idling the engine undesirable, high friction hysteresis would arise. Especially useful be it when the flange-like output part of the damping arrangement, like flange body, axially floating between the two housing halves or the shell-like bodies the connectable with the engine flywheel element is mounted.

A particularly advantageous embodiment of the device can thereby allows be that the by the assembly of the two flywheel elements produced seal the viscous medium at least partially filled chamber seals or closes across from an axially rotatable relative to each other between the two Flywheel elements located annular gap, the outward can be open. It may be advantageous if the counterprofiles on the outer circumference an annular disc-like connected to the other flywheel element Component are provided.

The the chamber sealing sealing element has in an advantageous Way at least one annular disc-like sealing part. It can be useful be when the annular disc-like sealing member axially resilient is, so that after the mating of the flywheel elements of this for the production a perfect seal can be elastically deformed. One Such seal member may be connected to the flywheel element connectable to the engine be worn so that it after the mating of the flywheel elements on a contact surface of the another flywheel element with bias voltage applied.

to Facilitating the installation of the device, it may be appropriate when the inner diameter of the chamber sealing the annular channel towards Sealing element is larger as the outer diameter the counterprofiles of the connector. This allows the sealing element during assembly of the device axially over the counterprofiles guided be, which is particularly advantageous if the flange-like output part the damping arrangement has a central recess whose peripheral contour the profiles limited the connector and that the counterprofiles on outer periphery having, annular disc-like component on a motor side Flywheel element facing end face of the other flywheel element is fixed axially.

A perfect sealing of the chamber and a simple construction of the Device can be achieved in that the sealing element with his radially outer edge region is axially supported on a radial wall of the one flywheel element, formed by the housing half is, which at the existing between the two flywheel elements radial annular gap adjacent. In this case, the radially outer edge region the sealing element axially fixed to the radial wall be. For the function of the sealing element may be appropriate if this at the outer edge area is axially clamped. Such a clamping, the axially resilient can be Seal element, similar like a plate spring to pivot around the clamping area. The provided on the other flywheel element bearing surface for the sealing element can be formed in a simple manner by an annular component, that between the face the other flywheel element and the counterprofiles having axially clamped component and radially outward extends further than the counterprofiles. This annular component can while radially outside in the direction of the provided with the counterprofiles component be moved away or be hitched.

For some applications it can be useful if the effective between the two flywheel damping arrangement comprises at least one friction device. This friction device can be effective over the entire angle of rotation between the two flywheel elements or can only be used in a certain range of this angle of rotation. It can be advantageous in this case if the friction device has at least one friction disk which cooperates with at least one force accumulator which acts in the circumferential direction. The energy accumulator can be designed such that the moment exerted by him on the friction torque sufficient at least over a portion of its compression travel to overcome the friction torque of the friction disc so that it is at least partially reset.

Farther it may be appropriate when provided between the flywheel elements friction device In the circumferential direction is fraught with game, that means that between the attacks the friction disc of the friction device and their associated counter-attacks a Game is available. This will reduce the use of the friction device with regard to the use of energy storage delayed.

Around one over the entire life of the unit as constant friction torque To achieve, it may be appropriate to the friction device in the through the housing halves or the shell-like bodies formed chamber for provide viscous medium.

For others use cases However, it may also be advantageous if outside with viscous medium at least partially filled Room or ring channel in addition an effective between the two flywheel elements Trockenreibungsdämofungseinrichtung is arranged.

Even though it for many use cases may be advantageous if the friction damping device with the Springs of the damping arrangement in parallel switched it can be for other applications be particularly appropriate if between the flywheel elements at least one with the between These friction springs are connected in series with these effective springs is available. The damping effect the friction device or friction damping device can via the Angle of rotation changeable be, with the damping effect become larger with increasing twist angle can.

For the function and the structure of the device may be advantageous if the with the inner spring group parallel effective friction damping and / or viscous damping is much lower than that of the outer spring group in parallel switched viscous damping and / or friction damping. Therefor can be outside springs at the ends with cups be provided, whose outer contour at least approximately the contour of the annular channel corresponds, creating a large attenuation by fat displacement arises. The inner springs, at least the first stage, are without Federnäpfe used to at least in the first stage a low fat displacement and thus also a low attenuation to achieve. The feathers of the inner spring group used with play can for optimizing the damping with or without feathering pens to be built in. Furthermore, the outer and inner spring group associated viscous damping be affected by appropriate determination of the level of viscous medium. It may be advantageous if the outer ring channel completely and the inner indentations are only partially filled with viscous medium. The high damping effect when compressing the outer springs therefore begins immediately with the start of the springs. The the inner damping group associated damping remains low, because the springs only partially submerge in the viscous medium.

For the function and the structure of the device may be particularly advantageous if the motor housing half or the motor side, shell-like bodies radially inwardly carries an axial extension, which in the direction of directed to the drive train flywheel element is directed and a rolling bearing wearing, that rotatably supports the two flywheel elements relative to each other. The connectable to the drive train flywheel element can a have axial recess into which the axial projection projects axially. Advantageous it is when this recess forms a seat for recording the outer ring of the Bearing.

For the assembly the device, it is particularly advantageous if before assembly of the two flywheel elements, the rolling bearing positively fixed is at the connectable to the drive train flywheel element and in assembling this rolling bearing is pushed onto a seat of the axial extension.

Around a multi-stage spring characteristic between the flywheel elements to receive be shorter at least individual springs of a spring group or a damper as the circular arc section between the interacting with these Attacks.

Based on 1 to 10 Let the invention be explained in more detail:

It shows 1 an inventive Facility on average,

2 a view of the device according to arrow II of 1 with outbreaks,

3 a section through another device according to the invention,

3a the detail "X" of 6 on an enlarged scale,

4 a view of the device according to 6 in the direction of the arrow IV with outbreaks,

5 a half section through an embodiment of a device according to the invention,

6 a partially illustrated section along the line VI-VI of 5 .

7 a section along the line VII-VII of 6 , Wherein also components are shown, the only off 5 can be seen

8th Details of a device according to the invention, which, for example, in embodiments according to the 1 to 7 can be used 9 and 10 further sections through devices according to the invention.

The in the 1 and 2 illustrated torque transmitting device 1 To compensate for rotational shocks has a flywheel 2 , which in two flywheel elements 3 and 4 is divided. The flywheel element 3 is on a crankshaft 5 a non-illustrated internal combustion engine via mounting screws 6 attached. On the flywheel element 4 is a switchable friction clutch 7 attached. Between the printing plate 8th the friction clutch 7 and the flywheel element 4 is a clutch disc 9 provided, which on the input shaft 10 a transmission not shown is added. The printing plate 8th the friction clutch 7 will be in the direction of the flywheel element 4 through one on the clutch cover 11 pivots supporting diaphragm spring 12 applied. By actuating the friction clutch 7 can the flywheel element 4 and thus also the flywheel 2 or the internal combustion engine of the transmission input shaft 10 be connected and disconnected. Between the flywheel element 3 and the flywheel element 4 is a first, radially outer damper 13 and a second, radially inner damper connected in parallel therewith 14 provided, which a relative rotation between the two flywheel elements 3 and 4 enable.

The two flywheel elements 3 and 4 are relatively rotatable to each other via a storage 15 stored. Warehousing 15 comprises a rolling bearing in the form of a single-row ball bearing 16 , The outer bearing ring 17 of the rolling bearing 16 is in a recess 18 the flywheel element 4 and the inner bearing ring 19 of the rolling bearing 16 is on a central, axially van der Kurbelwelle 5 extending away and into the recess 18 protruding cylindrical pin 20 the flywheel element 3 arranged.

The inner bearing ring 19 is by means of interference fit on the pin 20 taken and between a shoulder 21 of the pin 20 or the flywheel element 3 and a lock washer 22 on the front of the pin 20 is fixed, clamped.

The warehouse 16 is opposite to the flywheel element 4 secured axially, by interposing two in cross-section L-shaped rings 23 . 24 axially between a shoulder 25 the flywheel element 4 and one about rivets 26 with the second flywheel element 4 firmly connected, annular disc 27 is clamped.

The two rings 23 . 24 Form a thermal insulation that blocks the heat flow from the clutch disc 9 cooperating friction surface 70 the flywheel element 4 to the camp 16 interrupts or at least reduces.

The radially inwardly pointing legs 23a . 24a The Rings 23 . 24 extend partially radially over the inner bearing ring 19 and are supported axially on this, thereby simultaneously acting as a seal for the bearing 16 serve. To ensure perfect sealing of the bearing 16 ensure the radially extending legs 23a . 24a each by a power storage in the form of a plate spring 28 . 29 axially in the direction of the end faces of the inner bearing ring 19 applied.

The flywheel element 3 forms a housing, which is an annular chamber 30 limited in the damper 13 . 14 are included. That the annular chamber 30 having flywheel element 3 consists essentially of two housing parts 31 . 32 radially outward by means of screws 33 connected to each other. The screws 33 are in the radial region of the end surfaces or abutment surfaces 34 . 35 over the two housing halves 31 . 32 abut against each other, provided. The abutment surfaces 34 . 35 are located radially outside the first damper 13 , For sealing the annular chamber 30 towards the outside is a sealing ring 36 provided axially between the two abutment surfaces 34 . 35 and radially inside the screws 33 is arranged. For receiving the sealing ring 36 owns the housing part 31 an axial annular groove 37 , To ge Precise positioning of the two housing parts 31 . 32 in the assembly are also cylindrical pins 38 provided, the radially outside of the sealing ring 36 in axially aligned holes of the two housing parts 31 . 32 are included.

The motor facing housing part 31 has a shoulder on the outer circumference 39 on which a starter ring gear 40 has shrunk. The two housing parts 31 . 32 can be made of cast iron. If a low moment of inertia of the first flywheel element 3 is desired, at least one of the housing parts 31 . 32 made of a light metal alloy, such as cast aluminum. Such Leichtmetallgußteile have the advantage that they can be prepared by a printing or pressing and used without much rework.

The two dampers 13 . 14 have a common output part in farm of a radial flange 41 that is axially between the two housing halves 31 . 32 is arranged. The flange 41 is how this particular look 2 worked; with its radially inner regions via an axial plug connection 42 with the annular disc part 27 rotatably connected; which on the front of the in the direction of the crankshaft 5 pointing axial approach 43 of the flywheel element 4 over the rivet 26 is attached. For accurate radial positioning during assembly is between the annular disc part 27 and the axial approach 43 a centering seat 43a intended.

The flange 41 has radial arms on its outer circumference 44 on which the loading areas for the energy storage in the form of coil springs 45 of the outer damper 13 form. Radial within the - viewed in the circumferential direction - between the arms 44 existing cutouts 46 for the coil springs 45 owns the flange 41 arched windows 47 in which the energy store in the form of coil springs 48 the inner damper 14 are included. Radial between the cutouts 46 and the windows 47 forms the flange 41 in the circumferential direction extending webs 49 which are the radial arms 44 or in the circumferential direction between the windows 47 existing radial areas 50 of the flange 41 connect with each other. The radial areas 50 form the loading areas of the flange 41 for the coil springs 48 ,

The annular chamber 30 forms radially outside a ring-channel-like or torus-like recording 51 in which radially the outriggers 44 of the flange 41 intervention.

The annular channel recording 51 for the energy storage 45 is essentially by extending over the circumference axial indentations 52 . 53 formed, which in the radial regions of the housing parts 31 . 32 are inserted and in which the both sides of the flange 41 protruding areas of the power stores 45 dive axially. Radially inward is the annular channel recording 51 through the bridges 49 of the flange 41 except for a small gap 54 , locked.

How out 1 it can be seen that the axial indentations 52 . 53 formed in cross-section such that the arc-like course at least approximately to the circumference of the cross section of the energy storage 45 is aligned. The outer areas of the indentations 52 . 53 can thus for the energy storage 45 Form investment areas or management areas in which the energy storage 45 can support radially at least under centrifugal force. By aligning with the indentations 52 . 53 formed investment areas on the outer circumference of the energy storage 45 can wear, which due to the friction of the windings of the energy storage 45 at the radially outer regions of the indentations 52 . 53 takes place, being substantially reduced because the support surface between springs 45 and indentations 52 . 53 is enlarged. To act on the energy storage 45 are on both sides of the boom 44 in the indentations 52 . 53 extensive attacks 55 . 55a introduced, which in the circumferential direction supporting areas for the energy storage 45 form. In the illustrated embodiment, the circumferential stops have 55 . 55a - viewed in the circumferential direction - the same angular extent as the boom 44 of the flange 41 , The circumferential stops 55 . 55a are through to the indentations 52 . 53 adapted components 56 . 57 formed by means of rivets 58 with the housing parts 31 . 32 are firmly connected. The circumferentially considered end portions of the circumferential stops 55 . 55a are for better loading of the energy storage 45 flattened.

Between the arms 44 and the ends of the feathers facing them 45 are feather pens 59 provided (see 2 ), whose circumference at the cross section of the annular channel-like receptacle 51 is adapted.

Radial within the annular channel-like recording 51 own the housing halves 31 . 32 facing each other, annular surfaces forming areas 60 . 61 , between which an annular passage 62 for the flange 41 is available.

In the embodiment according to 1 and 2 is the width of this annular passage 62 slightly larger than the areas of the flange included in this 41 , so that at least on one side of the flange 41 A gap 54 is available.

Radial inside the circular passage 62 own the housing parts or housing halves 31 . 32 further axial indentations 63 . 64 into which the two sides of the flange 41 protruding portions of the inner coil springs 48 at least partially submerge.

How out 1 it can be seen that the axial indentations 63 . 64 formed in cross-section such that the arc-like course at least in the radially outer region of the circumference of the cross section of the coil springs 48 is adjusted so that the springs 48 at least in the axial direction through the indentations 63 . 64 be kept or led.

Similar to the outer indentations 52 . 53 also extend the inner recesses 63 . 64 over the entire scope of the facility. This is advantageous because then, for example, the pre-cast indentations 52 . 53 and 63 . 64 can be edited by a rotation operation. To act on the energy storage or coil springs 48 are in the dents 63 . 64 extensive attacks 65 . 66 introduced, which in the circumferential direction support areas for the coil springs 48 form. These circumferential stops 65 . 66 are through to the indentations 63 . 64 adapted components formed with the housing parts 31 . 32 over rivets 67 are firmly connected. How out 2 can be seen, have on both sides of the radial areas 50 of the flange 41 provided for attacks 65 . 66 - Viewed in the circumferential direction - a smaller angular extent, as these radial areas 50 , which are the coil springs 48 apply.

The bridges 49 of the flange 41 are with respect to the inner indentations 63 . 64 dimensioned such that the coil springs 48 at least under centrifugal force radially on the webs 49 support.

This is advantageous because the flange can be made of steel which is at least surface hardened, whereby the. Wear on the radial support areas for the springs 48 can be reduced. Another advantage of the radial support of the springs 48 at the jetties 49 is that until the investment of the springs 48 at the circumferential stops 65 . 66 the feathers 48 yourself with the flange 41 can rotate without a significant friction due to the centrifugal force acting on them on the housing parts 31 . 32 to create. Such friction is undesirable in many cases because it is the characteristic of the outer damper 13 falsified.

How out 2 It is apparent from the scope of the institution 1 considered, each 3 springs 45 and 48 provided, wherein the radially outer springs 45 each extend at least approximately over 110 degrees. The radially inner springs 48 extend at least approximately over the same angle as the outer springs 45 , In the present case, a spring extends 48 at least approximately over 100 degrees. The outer springs 45 So extend over about 91% of the circumference of the device and the inner springs 48 over about 83% of the volume.

In the unassembled state, the springs can 45 and / or the springs 48 - When viewed in the axial direction - be straight, this means that during assembly these springs must be bent according to the shape of the receiving indentations, or it can also be the springs 45 and / or the springs 48 according to the shape of the receiving indentations already have a corresponding curvature. By using pre-curved springs 45 . 48 can reduce the stresses occurring in these compressing and continue to facilitate assembly.

In the annular chamber 30 is a viscous medium or a lubricant, such as silicone oil or fat provided. The level of the viscous medium or the lubricant can - with rotating device 1 - At least to the central region or the axis of the outer springs 45 of the damper 13 pass. In the illustrated embodiment, it is advantageous if this level at least up to the outer portions of the turns of the inner coil springs 48 is sufficient, so that at least between these turns and the radially supporting areas, in the present case, the webs 49 of the flange 1 , a wear-reducing lubrication is present. In the device shown 1 It is advantageous if the filling of viscous medium or lubricant in about to the axis of the inner coil springs 48 enough.

By the assignment of the annular chamber 30 , which contains a viscous medium or a lubricant, to the flywheel element connected to the engine 3 and by the physical separation of the friction clutch 7 carrying flywheel element 4 an influence of the resulting in connection with the friction clutch heat to the viscous medium or lubricant is largely eliminated.

Furthermore, between the annular chamber 30 or the housing part 32 and the flywheel element 4 an outwardly open annular channel 68 provided, in connection with ventilation ducts 69 the cooling effect further improved. The air channels 69 are radially inside the friction surface 70 of the flywheel element 4 for the Kupp lung slice 9 intended.

As in particular from 2 can be seen possesses the flange 41 a middle recess 71 whose contour has radial profiles 72 forms, which are engaged with counter-profiles 73 , which on the outer circumference of the flywheel element 4 connected annular disc part 27 are provided. The axial plug connection 42 forming profilings 72 and counterprofiles 73 allow a perfect alignment of the flange 41 between the two housing halves 31 . 32 , so that between the annular passage 62 and the flange 41 existing gap 54 can be made very small. also allows the plug connection 42 To expand the axial tolerances between the various investment or support surfaces of the components.

For sealing the annular chamber 30 is a seal 74 between the radially inner region of the housing part 32 and the annular disc 27 or the axial approach 43 the flywheel element 4 intended. The seal 74 has an annular disc 75 , which with their radially inner area adjoin one another at the axial approach 43 molded shoulder 76 and with its outer area attached to a surface 77 at the radially inner region of the annular housing part 32 is molded, supported. The circular disc 75 is similar to a plate spring axially deformable. The circular disc 75 becomes axial against the shoulder 76 and the area 77 through a plate spring 78 impinged, which axially between the disc 75 and the flange 41 is tense. Through the plate spring 78 also becomes the flange 41 against the surface 60 pressed, leaving only on one side of the flange 41 A gap 54 between the annular channel-like recording 51 at the radially inner areas of the annular chamber 30 is available. How out 1 can be seen seals the seal 74 the annular chamber 30 to the between the two flywheel elements 3 and 4 existing annular gap 68 down. The inner diameter of the annular chamber 30 to the annular gap 68 sealing washer 75 is greater than the outer diameter of the counterprofiles 73 the connector 42 ,

The plug connection 42 and the seal 74 allow a particularly simple assembly of the torque transmission device 1 by first of all the two flywheel elements 3 and 4 be pre-assembled and then by axial mating and securing the lock washer 22 on the front side of the pin 20 axially connected to each other. For this, first, the seal 74 on the flywheel element 3 pre-assembled and the rolling bearing 16 on the flywheel element 4 positively fixed. When assembling the two flywheel elements 3 and 4 becomes the inner rolling bearing ring 19 on the seat 20a of the axial approach 20 of the housing part 31 deferred and the counterprofiles 73 with the profiles 72 engaged. Furthermore comes during the pushing together of the two flywheels 3 and 4 the radially inner region of the sealing disc 75 to the plant at the by the shoulder 76 formed sealing surface, so that the sealing disc 75 against the force of the diaphragm spring 78 is pivoted in and with bias against the shoulder 76 is applied. The final axial fixing of the two flywheel elements 3 and 4 relative to each other, as already mentioned, by attachment of the disc 22 on the cone 20 ,

To reduce wear in the contact area between the turns of the springs 45 and 48 and their indentations 52 . 53 respectively. 63 . 64 can at least in these contact areas, the surfaces of these indentations limiting parts 31 . 32 have a greater hardness. This can be done, for example, that these contact areas are inductively hardened, case hardened, laser beam hardened or flame hardened. At very high loads, however, it may also be appropriate if the indentations limiting parts 31 . 32 at least in the aforementioned contact areas have a wear-reducing coating. Such a coating can be formed for example by chemical nickel plating, by chromium plating or by coating with plastic or molybdenum. The applied coating can furthermore be subsequently smoothed in order to obtain a better surface quality of the indentations on which the turns of the springs rub. Such smoothing can be done, for example, by a grinding process or a turning operation.

In the following, the operation of the device according to the 1 and 2 described.

At a rotation of the flywheel element 4 opposite the flywheel element 3 from the in 2 shown rest position is the flange 41 over the plug connection 42 driven so that initially the outer springs 45 between the circumferential stops 55 . 55a and the radial arms 44 be compressed. After passing through the relative angle of rotation 79 in a direction of rotation or 80 in the other direction of rotation come the circumferential stops 65 . 66 on the inner springs 48 to the plant, so that in a further relative rotation between the two flywheel elements 3 and 4 in addition to the springs 45 the feathers 48 be compressed. The common compression of the springs 45 and 48 takes place until the inner springs 48 go to block where by the relative rotation between the two flywheel elements 3 and 4 is limited. In the illustrated embodiment, the maximum angle of rotation, starting from the in

2 illustrated rest position, in both directions of rotation in the order of 47 degrees. In a relative rotation between the two flywheel elements 3 and 4 becomes a friction damping by friction of the outer springs 45 on the surfaces of the indentations 52 . 53 as well as by friction of the flange 41 on the surface 60 generated. Also between the radially inner springs 48 and their radial support areas takes place a friction damping. The between the springs 45 . 48 and the radial support areas occurring friction damping is speed-dependent, with increasing speed, this attenuation is greater. Furthermore, a damping by turbulence or displacement of the in the annular chamber 30 contained contained viscous or pasty medium. In particular, in the practically closed annular channel-like recording 51 existing viscous medium produces a hydraulic or viscous damping, as the spring cups 59 in the annular channel-like recording piston-like effect. Upon compression of the outer springs are by the boom 44 acted on spring pens 59 in the direction of the at the peripheral stops 55 . 55a supporting cups moves so that the existing in the springs viscous medium substantially through the gap 54 , which acts like a throttle, is crowded. Another part of the viscous medium is placed between the feather heads 59 and the walls of the annular channel-like receptacle 51 repressed. The initially inwardly displaced viscous medium is distributed again due to the centrifugal force acting on this uniformly over the circumference. While relaxing the outer springs 45 that will be on the feathers 45 turned away side of the feathering pens 59 existing viscous medium in a similar manner past the feather pads and through the gap 54 displaces and fills the springs again as a result of the centrifugal force acting on them 45 out. The damping generated by the viscous medium is dependent on the centrifugal force acting on the medium, which means that the damping increases with increasing speeds.

The immersed in the viscous medium areas of the radially inner springs 48 also produce a viscous or hydraulic damping by turbulence.

By introducing axial recesses or cutouts in at least individual wells and by appropriate dimensioning of the gap 54 or the outer circumference of the cups, the attenuation generated by the viscous medium can be changed or adapted to the particular application. Furthermore, the viscous or hydraulic damping can be adapted by only some of the springs 45 with cups 59 be provided. Also, between the spring ends of at least one inner spring 48 and the radial areas 50 of the flange 41 Feather cups are provided.

In the 3 and 4 The device shown has two flywheel elements 3 and 4 Similar to the device according to the 1 and 2 via a rolling bearing 16 are rotatably mounted to each other. The axially securing the two flywheel elements disc 122 is on the front side of the axial extension 120 by riveting 122a attached. Assembling the two flywheel elements 3 and 4 is done in a similar way as in connection with 1 and 2 described. That means the bearing 16 initially on the flywheel element 4 is pre-assembled and the assembly of the two flywheel elements 3 and 4 on the seat 120a of the axial approach 120 is postponed. Furthermore, before the assembly of the two flywheel elements 3 and 4 on the engine side provided flywheel element 3 a seal 174 pre-assembled, and it is between the flange 141 , which is the output part of the two parallel dampers 13 . 14 forms, and the disc-like component 127 , the flywheel element 4 over rivets 126 is attached, an axial connector 142 intended. The two, the annular chamber 130 limiting housing parts 131 . 132 are formed as castings. The housing part 132 has at its periphery an axial cylindrical extension 132a , over its inner lateral surface 135 the housing part 132 on an outer surface 134 of the housing part 131 is centered. The axial securing of the two cast housing parts 131 . 132 via radial pins 138 in the area of the centering surfaces 134 . 135 are introduced. The housing part 132 carries a starter sprocket 140 who has the pins 138 partially axially overlaps, so that they can not migrate radially.

The axial connector 142 is through on the inner circumference of the flange 141 molded radial arm 172 between the outer circumference of the annular disk-like component 127 molded radial projections 173 grab, educated.

As in particular from 3a it can be seen that has between the radially inner portion of the housing part 132 and the annular disk-like component 127 or the axial approach 143 the flywheel element 4 provided seal 174 an annular, axially resilient disc 175 , which with their radially inner area adjoin one another at the axial approach 143 attached annular component 176 supported and with its radially outer region at the radially inner region of the housing part 132 axial is fixed. The similar to a plate spring axially deformable sealing washer 175 carries at its radially outer and inner regions a coating 175a . 175b , such as plastic coating, which is applied for example by spraying. These coatings 175a . 175b should have a low coefficient of friction and a certain elastic or plastic deformability.

The radially outer edge region of the sealing washer 175 is in an annular carrier 180 sealingly beaded. The flanging of the outer region of the sealing washer 175 takes place in such a way that the sealing disc 175 a conicity change can perform. The areas 180b of the annular carrier 180 , which is the outer circumference of the sealing washer 175 are in an axial recess or in an axial. return 177 taken, the at the radially inner region of the housing part 132 is formed. For axially fixing the outer region of the sealing washer 175 owns the ring-shaped carrier 180 flared areas 180a that the inner edge 132b of the housing part 132 encompass radially. The annular carrier 180 forms for the plate spring similar deformable sealing washer 175 a circular Verschwenklagerung.

The annular component 176 which one with the sealing washer 175 has cooperating sealing surface has a radially inner disc-shaped area 176a that is between the end face of the axial neck 143 and the disc-like member 127 is axially clamped, and an annular outer region 176a on which the sealing disc 175 sealingly abuts with axial prestress.

The radially outer regions l76b of the annular component 176 are opposite the radially inner regions 176a in the axial direction of which the counter-profiles 173 the connector 142 having, annular disc-like component set back. How out 3 can be seen seals the seal 174 the annular chamber 130 to the between the two flywheel elements 3 and 4 existing annular gap 168 down.

To an axial mating of the two flywheel elements 3 and 4 to allow, is the inner diameter of the gasket 175 greater than the outer diameter of the radial projections or the counterprofiles 173 , The areas 17bb of the annular component 176 on which the sealing disc 175 axially supported, extending radially outwardly further than the counter-profiles 173 ,

When sliding the rolling bearing 16 on the seat 120a becomes the plug connection 142 made and the sealing disc 175 is due to contact with the counter-sealing areas 176b axially braced.

To prevent or reduce the wear on the radial support areas of the annular channel-like recording 151 for the springs 145 is a high hardness steel strip 181 provided, which extends over the circumference of the annular channel-like receptacle 151 extends and the springs 145 umsdhließt. The steel band 181 is cylindrical and in a recess 182 received, which is formed by a radial recess or a radial recess. With rotating device 101 The springs are supported 145 as a result of the centrifugal force acting on them via their turns on the steel strip 181 from.

The circumferential stops 155 . 155a for the outer springs 145 as well as the circumferential stops 165 . 166 for the inner springs 148 are formed by molded parts, such as forgings, press-formed parts, the one-piece molded rivet 158 . 167 have for attachment to the respective housing part 131 . 132 ,

How out 4 can be seen, have the two sides of a boom 144 of the flange 141 provided for attacks 155 . 155a a greater extent in the circumferential direction than the boom 144 , wherein in the embodiment shown in the in 4 illustrated rest position of the device the boom 144 towards the attacks 155 . 155a are arranged in the middle, that means that the attacks 155 . 155a the outriggers 144 on both sides of an equal measure.

The circumferential stops 165 . 166 on both sides of the radial areas 150 of the flange 141 are arranged, also have a greater extent in the circumferential direction than the areas 150 , which for applying the springs 148 serve. The arrangement of the stops 165 . 166 with respect to the radial regions 150 However, it is made such that the circumferential stops 165 . 166 in the resting position of the institution 101 one-sided to the areas 150 survive, whereas on the other side the attacks 165 . 166 and the radial areas 150 be flush. Furthermore, the offset of the attacks 165 . 166 with respect to the radial regions 150 made such that two successive circumferentially stops 165 respectively. 166 in the opposite direction of rotation relative to their associated radial areas 150 of the flange 141 are offset. Due to this structure, the inner springs form 148 two spring groups, namely 148a and 148 that come into effect gradually.

That in the annular chamber 130 absorbed viscous medium or lubricant, such as For example, silicone oil or grease should be used while rotating 101 at least the annular channel-like recording 151 fill out. However, it may be advantageous if the level of the viscous medium or lubricant at least up to the outer regions of the turns of the inner coil springs 148 ranges, where it may be particularly useful if the filling of viscous medium or lubricant in about to the axis of the inner coil springs 148 see extends.

Between the arms 144 or the circumferential stops 155 . 155a and the ends of the feathers facing them 145 are feather pens 159 whose circumference at the cross section of the annular channel-like receptacles 151 adapted, provided. This will, as in connection with 1 and 2 described a relatively large Dämofung by displacement of the in the annular chamber 130 produced viscous medium.

The feather pens 159 have a slightly conical pin 159a in the feathers 145 protrudes axially. The end 159b of the pin 159a is formed conically in the illustrated embodiment, but could also be formed dome-shaped. By such a configuration of the spring cups 159 finds, if a cup slips out of the spring end in operation, when re-loading the cup or relaxation of the spring self-threading thereof into the spring instead, so that the spring or the cup are not damaged. A leakage of feather pots 159 can occur when the outer springs 145 are compressed and the device 101 rotated at a relatively high speed. In this operating state, the between the spring coils of the springs 145 and the radial support portions of the housing halves 131 . 132 For such springs existing friction be high so that the springs 145 at least not fully able to relax in a sudden load change shock. By the of the radial arms 144 Displacement on viscous medium, which is distributed externally under the influence of centrifugal force during the load change shock, can be provided by spring cups 159 from the ends of the not relaxing feathers 145 be urged.

In the following, the operation of the device according to the 3 and 4 described.

At a rotation of the flywheel element 4 opposite the flywheel element 3 from the in 4 shown rest position is the flange 141 over the plug connection 142 driven so that initially the inner springs 148b between the circumferential stops 165 . 166 and the radial Be rich 150 be compressed. After passing through the relative angle of rotation 179 in a direction of rotation or 190 in the other direction of rotation come the radial areas 150 of the flange 141 at the ends of the inner springs 148a to the plant, so that in a further relative rotation between the two flywheel elements 3 and 4 the feathers 148a and 148b compressed together. After passing through the relative angle of rotation 179a in a direction of rotation or 190a in the other direction of rotation, are the outer springs 145 from the radial arms 144 acted upon, so that in a further relative rotation, the springs between the peripheral stops 155 . 155a and the radial arms 144 be compressed. In the illustrated Auführungsbeispiel corresponds to the angle 179 the angle 179a and the angle 190 the angle 190a so that the springs 148a and the springs 145 take effect simultaneously. This results in the illustrated embodiment according to 3 and 4 a two-stage spring characteristic. The angles 179 . 190 . 179a . 190a However, they may also only partially have the same amount or have different values, so that an at least three-stage spring characteristic in both directions of rotation or at least two-stage spring characteristic in one direction of rotation and at least three-stage spring characteristic in the other direction is possible.

Furthermore, the circumferential stops 165 . 166 like this in 4 dash-dotted with 165a is indicated, compared to the retained in the flange spring ends of the springs 148b be set back so that then to the zero position of the relative rotation between the two flywheel elements 3 and 4 There is no suspension over a certain angle, and only hydraulic or viscous damping and / or friction damping occurs.

The height or characteristic of the hydraulic or viscous damping can be varied by, for example, only some of the outer springs 145 with feathery heads 159 or at one end of at least one spring 145 no bowl 159 provides. Furthermore, at least one spring 148a and or 148b be provided with feather heads. Other factors influencing the viscous or hydraulic damping are the radial filling level of viscous medium and the width of the gap (s) between the flange 141 and the surfaces 160 . 161 the housing halves 131 . 132 ,

The hydraulic or viscous damping by displacement or turbulence of the viscous medium takes place in a similar manner, as in connection with the 1 and 2 described.

How out 4 it can be seen are over the scope of the facility 101 four springs each 145 and 148 provided, wherein the radially outer springs 145 each extending at least approximately over 78 degrees. The radially inner springs 148b extend at least approximately over 74 degrees and the springs 148a at least approximately over 68 degrees of the circumference. Thus, the outer springs extend 145 at least approximately over 86% of the circumference, whereas the inner springs 148 extend at least approximately over 79% of the circumference.

As it is out 4 can be seen possesses the component 3a the flywheel element 3 on the outer circumference radial boom 186 , in each of which a threaded hole 187 is provided for fixing a friction clutch. Some of the outriggers 186 have holes 188 on for picking up pins, ensuring accurate positioning of the clutch cover on the component 3a ensure during assembly.

The radial arms 186 allow a lighter design of the flywheel element 4 , Furthermore, by the between the radial arms 186 existing radial recesses 186a a better cooling of the component 3a and the clutch mounted thereon, since between the cover and the recesses 186a an air circulation can take place. Radial inside the friction surface 4a of the component 3a are ventilation channels 169 provided, which in between the two flywheel elements 3 and 4 provided radial gap 168 open out.

The radial arms 186 allow, for a given mass, the component 3a in the area of the friction surface 4a thicker, so that overheating in this area can be avoided.

A change in the attenuation generated by the viscous medium can be further achieved by the annular channel recording 151 at least over portions of the longitudinal extent of at least one spring 145 does not have a constant cross-section, so that in the areas of larger cross section, a lower attenuation and in the areas with a smaller cross section, a higher attenuation is generated. Although this cross-sectional change of the annular channel-like recording 151 can be provided at any point or even at several points, it is particularly useful if such cross-sectional changes or cross-sectional enlargements in the end portions of the non-compressed springs 145 are located. The cross-sectional changes can be abrupt or progressive. It is particularly advantageous if the cross-sectional widening in the region of the radially inner half of the annular channel-like receptacle 151 be provided. Such an extension is in 4 shown and with 189 characterized. This extension 189 is at the flange 141 molded, which the annular channel-like recording 151 bounded or closed radially inward. However, the extensions can also by appropriate shaping of the ring-channel-like recordings 151 delimiting dents 152 . 153 be formed.

The in the 5 and 6 shown torque transmission device 201 for compensating for rotational shocks has a flywheel 202 , which in two flywheel elements 203 . 204 is divided. The two flywheel elements 203 and 204 are relative to each other rotatable about a storage 15 stored. The flywheel element 203 forms a housing, which is an annular chamber 230 limited, in which a damping device 213 is included.

That the annular chamber 230 having flywheel element 203 consists essentially of two housing parts 231 . 232 , which are connected to each other radially outward. The two housing parts 231 . 232 are formed by sheet metal parts, which at their outer periphery by a weld 238 connected to each other. This weld 238 simultaneously seals the annular chamber 230 radially outwards. For welding the two sheet metal parts 231 . 232 is advantageously a resistance butt welding or a capacitor Stoßontladungsschweißung, ie a weld in which the in contact and to be welded areas of two components are heated by welding to the components of an alternating current of high current and low voltage to welding temperature and combined under pressure.

To carry out such a weld, the two shell-like sheet-metal shaped parts have 231 . 232 Forehead areas or abutment surfaces 234 . 235 which have a defined area with respect to the amperage used for the welding. In the area of these impact surfaces 234 . 235 lie the housing parts 231 . 232 axially against each other and are or are welded together.

For exact radial positioning of the two housing parts 231 . 232 during welding has the housing part 231 radially outside an annular projection 231 , the one on the outer circumference of the housing part 232 molded centering surface 235a embraces. For accurate positioning in the circumferential direction during welding are in the housing parts 231 . 232 axial countersinks 265 . 256 brought in. In these countersinks 265 . 266 Pins of the welding device can engage the two housing parts 231 . 232 currency hold the weld in a precise angular position with respect to each other.

Because during the welding of the two sheet metal shells 231 . 232 As a result of the weld formation takes place a certain axial movement between these sheet metal shells, it may be advantageous to provide axial stops between these sheet metal shells, which are effective only during the welding. In 5 is dot-dashed one such, on the sheet metal shell 232 molded stop indicated and with 267 characterized. By using such limit stops 267 one is not so dependent on the current used for welding, which means that you can work with a higher current, since the axial position of the two housing parts 231 . 232 through the attacks 267 is determined and not by the amperage and during the welding on the two housing parts 231 . 232 applied axial pressure.

The output part of the damper 213 is by a radial flange 241 formed axially between the two housing parts 231 . 232 is arranged. The flange 241 is with its radially inner regions via an axial connector 242 with the annular disc part 227 , which on the front side in the direction of the motor-side housing part 231 pointing axial approach 243 the flywheel element 204 over rivets 226 is attached.

The flange 241 has radial arms on its outer circumference 244 on which the loading areas for the energy storage in the form of coil springs 245 of the damper 213 form.

The two housing parts 231 . 232 form radially outside a ring-channel-like or torus-like recording 251 into which the radial arms 244 of the flange 241 intervention. The annular channel recording 251 for the energy storage 245 is essentially by extending over the circumference axial indentations or embossments 252 . 253 formed, which in the housing parts made of sheet metal 231 . 232 are inserted and in which the both sides of the flange 241 protruding areas of the energy storage 245 dive axially. Radially inward is the annular channel recording 251 through an annular area 249 of the flange 241 except for a small gap 254 , locked.

How out 5 it can be seen that the axial indentations 252 . 253 formed in cross-section such that the arc-like course at least approximately to the circumference of the cross section of the energy storage 245 is aligned. The outer areas of the indentations 252 . 253 can thus for the energy storage 245 Form investment areas or management areas in which the energy storage 245 can support radially at least under centrifugal force.

To act on the energy storage 245 are on both sides of the boom 244 in the indentations 252 . 253 extensive attacks 255 . 255a brought in. In the illustrated embodiment, the circumferential stops have 255 . 255a - viewed in the circumferential direction - the same extent as the radial boom 244 of the flange 241 , How out 6 is apparent, are between the boom 244 and the ends of the feathers facing them 245 Intermediate parts in the form of feather pots 259 provided, the scope of the cross-section of the annular channel-like recording 251 is adapted.

Radial within the annular channel-like recording 251 own the housing halves 231 . 232 facing each other, annular surfaces forming areas 260 . 261 , between which an annular passage 262 for the flange 241 is available.

In the illustrated embodiment according to 5 and 6 , is the width of this annular passage 262 only slightly larger than the recorded in this areas of the flange 241 so that a very small gap 254 is available.

How out 6 It is apparent from the scope of the institution 201 considered, four springs 245 intended; each extending at least approximately over 82 degrees of the circumference. Thus, the springs extend over at least approximately 90% of the circumference of the device 201 ,

To reduce the in the springs 245 When compressing occurring stresses and ease of assembly are the springs 245 at least approximately to the radius on which they are arranged, pre-curved.

In the annular chamber 230 a viscous medium or a lubricant is provided. The viscous medium is meant to be - with rotating device 201 - At least the annular channel-like recording 251 fill out.

How out 6 can be seen possesses the flange 241 a middle recess 271 whose contour has radial profiles 272 forms, which are engaged with counter-profiles 273 located on the outer circumference of the flywheel element 4 connected annular disc part 227 are provided. The counterprofiles 273 are formed by radial projections, which in correspondingly adapted cutouts 272a of the flange 241 one to grab. In the area of the radial projections 273 are also the rivets 226 provided that the component 227 on the flywheel element 204 establish. The axial plug connection 242 forming profilings 272 and counterprofiles 273 allow a perfect alignment of the flange 241 between the two housing halves 231 . 232 , so that between the annular passage 262 and the flange 241 existing gap 254 can be made very small.

Also allows the connector 242 , the axial tolerances between the various investment or support surfaces of the. Expand components.

For sealing the annular chamber 230 is a seal 274 between the radially inner region of the housing part 232 and the flywheel element 204 intended. The seal 274 differs from that in conjunction with the 3a described seal 174 essentially in that the annular axially resilient disc 275 is completely coated and is radially axially clamped axially between an annular region 232a of the housing part 232 and one on the housing part 232 by riveting 232b attached ring disk 280 ,

The annular area 232a of the housing part 232 extends, starting from the outer diameter of the resilient sealing washer 275 radially inward, being between the annular region 232a and the sealing washer 275 a radial space 232c is formed. In this radially inwardly open radial space 232c can be the small amounts of viscous medium, which may be between the interior of the gasket 275 and the backsight areas 276b can escape, be collected and at higher speeds - due to the centrifugal force - between the annular area 232a and the sealing washer 275 back into the annular chamber 230 be pushed back. The contact zones between the inner regions of the sealing disc 275 and the backsight areas 276b are in the axial extent of the radial space 232c intended.

At the inner area of the housing part 232 is an axial recess or an axial shoulder 291 formed, whose radially outer surface, the outer regions of the sealing disc 275 axially overlaps.

The motor facing half of the housing 231 carries inside an axial approach 220 on which the two flywheel elements 203 and 204 relative to each other superimposed bearings 16 in a similar way as in 1 is included. The sheet metal part 231 is on a seat 220b of the approach 220 centered and supported axially on one at the connection to the seat 220b provided radial surface 220c of the approach 220 from.

The connection between the sheet metal part or housing part 231 and the axial approach 220 can by a screw connection; riveting, welding or caulking.

Assembling the two flywheel elements 203 and 204 is done in a similar way as in connection with 1 and 2 described, that means that the rolling bearing 16 first on the flywheel element 204 and the sealing disc 275 on the flywheel element 203 be pre-assembled. When sliding the rolling bearing 16 on the seat 220a of the approach 220 becomes the plug connection 242 made and the gasket 275 by contact with the flywheel element 204 provided counter-sealing areas 276b axially braced. By attaching the lock washer 222 , which the inner bearing ring of the rolling bearing 16 radially overlapped, on the front side of the approach 220 Both are flywheel elements 203 and 204 secured axially to each other. The attachment of the disc 222 can, similar to in 6 represented by riveting done. However, screws can be used instead of rivets.

The hydraulic or viscous damping by displacement or turbulence in the annular channel-like recording 251 provided viscous medium takes place in a similar manner, as in connection with the 1 and 2 described.

To prevent that when welding the two sheet metal housing parts 231 . 232 the components in contact with them - such as in particular the movable components - in places ver welded to the housing parts or experience a structural change due to a localized overheating is between these components and the sheet metal housing parts 231 . 232 provided an electrical insulation. The components which are endangered during the welding process are, in particular, those in the annular channel-like receptacle 251 existing springs 245 , continue the flange 241 and the feather pens 259 ,

The insulating coating can be attached to the housing parts 231 . 232 be provided and / or on the components in contact with these 245 . 241 . 259 . 255 . 255a , The insulating coating can be applied only partially, that is, only in the contact areas between the housing parts and the other components.

The isolation can be achieved in an advantageous manner by phosphating individual components who the. Furthermore, individual components, such as the spring cups 259 and the circumferential stops 255 . 255a made of non-conductive material.

It is particularly advantageous if at least the sheet metal parts and / or the flange are phosphated for insulation. The feathers 245 are suitably painted, but may also be phosphated.

To the housing parts 231 . 232 In addition to insulating the components in contact with them, ceramic coatings, plastic coatings or even grease coatings can be used. Such coatings can in particular on the housing parts 231 . 232 be applied.

Unless the sheet metal parts 231 . 232 in the insulating treatment, such as phosphating, are completely coated, it is useful if in the area of the welding zones and in the contact area for the power supply, the previously applied in these areas insulating layer is removed, for example, by mechanical processing, so that in these areas a flawless electrical conductivity is present.

When selecting the insulating is always to make sure that this with the in the annular channel recording 251 tolerated viscous medium.

The Use of a phosphate layer as an insulating layer is particularly advantageous because it reduces wear and self-lubricating acts.

The housing part 231 furthermore has a seat on the outer circumference 239 on which a starter ring gear 240 is included. The starter ring gear 240 is considered over the circumference, at least in places with the housing part 231 through a weld 240a connected. This is the sheet metal version of the housing part 231 advantageous because due to the limited wall thickness of the housing part 231 the seat 239 does not extend over the full sprocket width.

How out 5 can still be seen, has the motor-side housing part 231 a greater material thickness than the housing part 232 ,

How out 7 can be seen, the circumferential stops 255 . 255a according to 5 be replaced by in the sheet metal parts 231 . 232 impressed formations, such as pockets 255c . 255d , These bags 255c . 255d can advantageously for positioning the two housing parts 231 . 232 be used together during welding. There are for this purpose to provide corresponding projections on the welding device, which are attached to the pockets 255c . 255d are adapted. These projections can form the electrodes, which provide the required welding current in the housing parts 231 . 232 initiate. Through these projections can continue required for the welding axial pressure on the housing parts 231 . 232 be applied. It is particularly useful if these projections are provided in the welding device such that they always occupy a predetermined distance during welding, whereby it can also be ensured that the two housing parts 231 . 232 after welding have a defined axial position relative to each other. This is important with respect to the in the annular channel-like recording 251 provided springs 245 and in particular in relation to the two areas 260 . 261 and the flange provided therebetween 241 to be maintained, defined distance that affects the hydraulic or viscous damping generated by the device.

This in 8th illustrated detail of a device 301 shows a flange 341 , the outer circumference radial boom 344 has formed. About the outriggers 344 can, as described in connection with the preceding figures, energy storage in the form of coil springs 345 . 345a be supervised. The energy storage 345 . 345a are in a ring-channel-like recording 351 taken up by components of the flywheel element 303 is formed. The feather 345a becomes directly through the radial boom 344 whereas, between the spring 345 and the radial boom 344 a spring cup 359 is arranged.

The boom 344 has in the circumferential direction pointing projections in the form of pins or noses 344a . 344b ,

The spring bowl 359 has a recess 359a into which the nose 344a intervenes. The nose 344a and the recess 359a are formed and arranged such that at least when exposed to the spring 345 the bowl 359 and over this the end of the compression spring 345 through the nose 344a relative to the radially outer regions of the annular channel-like receptacle 351 withheld or lifted off. For this purpose forms the radially inner area of the nose 344a a sloping ramp 344c that with a support area 359b of the spring cup 359 interacts. Through the ramp 344c the nose 344a becomes the spring cap 359 acted upon or pulled radially inward.

The nose 344 has a bevel radially inward 344d which coincides with the end turn of the spring 345a interacts and urges them radially inward or urges.

When using a spring cup 359 It is advantageous if at least the cross section of the ramp 344c to the contour of the recess 359a is adapted, so that even upon rotation of the spring cup 359 a perfect investment of the same on the nose 344a or the boom 344 given is.

Formations or noses 344a or 344b can also be advantageously to the radial arms and / or the radial portions of the flanges according to the 1 to 7 be provided.

Such noses 344a . 344b have the advantage that even at higher speeds, at least the end portions, that is, a few turns of the coil spring radially outward out of contact with other components or areas are held so that these spring coils can spring freely, that is, produce no friction damping.

Furthermore, by such noses 344a . 344b be ensured that even in speed ranges in which the normally existing friction between the turns of the springs and their radial support surfaces is so large that the turns can no longer spring, at least the Endbe rich of the springs still have an elasticity or suspension. This is particularly advantageous in order to damp the high-frequency oscillations occurring in these speed ranges with a small angular amplitude.

At the in 9 schematically illustrated embodiment of a unit 401 is for sealing the at least partially filled with a viscous medium annular chamber 430 the flange 441 directly on the axial extension 443 the flywheel element 404 sealingly riveted, and it is still axially between the flange 441 and the flywheel element 404 facing radial side wall 432 the annular chamber 430 a seal 474 intended.

Radial inside the lateral wall 432 and axially between the flange 441 and one of this axially spaced radial portion 404a the flywheel element 404 is a friction device 490 provided outside the viscous medium at least partially filled annular chamber 430 located. This dry rubbing device 490 has a friction disk 494 and on both sides of the same intended friction rings 494a . 494b , where the friction ring 494b axially between the friction disc 494 and the flange 441 is arranged. On the friction disc 494 facing away from the friction ring 494b is a pressure plate 493 arranged, which is acted upon by a diaphragm spring 492 , which is axially braced between the radial region 404a and the pressure plate 493 ,

The friction disc 494 has radial profiles on its outer circumference 495 which engage with at the radially inner edge of the wall 432 molded counterprofiles 495a , Depending on the application, the profilings can be formed free of play or, in the circumferential direction, a certain amount of rotation between the friction disc 494 and the wall 432 allow, so that then the friction device 490 only after the use of at least one of the springs of the damper 413 can be effective.

At the in 10 schematically represented unit 501 is radially inside the damper 513 and adjacent to the annular channel-like receptacle 551 on both sides of the flange 541 one seal each 574 . 574a provided with corresponding areas of adjacent parts 532 . 531 which the annular channel-like recording 551 limit, cooperate sealingly.

Radial inside the seals 574 . 574a is the flange 541 with the interposition of Reibririgen 594a ; 594b axially between two discs 593 . 594 clamped. The disc 594 is about distance bolts 567 with the flywheel element 504 firmly connected. The axial between the flange 541 and the radial area 504a the flywheel element 504 arranged pressure plate 593 is through a plate spring 592 acted upon, the axially between this pressure plate 593 and the radial area 504a is clamped. Radially inside own the plate spring 592 and the pressure plate 593 Cutouts showing the spacers 567 at least partially surround, so that the plate spring 592 and the pressure plate 593 opposite the flywheel element 504 are rotationally secured.

The preload force of the diaphragm spring 592 determines the moment at which the flange 541 opposite the flywheel element 504 can twist or slip. The components 592 to 594b thus form in conjunction with the radially inner regions of the flange 541 a non-positive coupling or slip clutch 590 ,

To limit the rotation between the flange 541 and the flywheel element 504 can the flange on his. Indoors have projections, which - viewed in the circumferential direction - between the standoffs 567 engage radially. By stop this radial projections of the flange 541 at the distance bolt 567 the relative rotation can be limited. For some applications, however, it may also be appropriate, if no such, the relative rotation between the flange 541 and flywheel element 504 limiting means are available. In such cases, the non-positive coupling 590 designed so that the transmissible torque from this is greater than the nominal torque output by the engine.

According to a development of in 10 can be shown with a limited relative rotation between the flange 541 and the flywheel element 504 additional energy storage in the form of coil springs between the two discs 593 . 594 and the flange 541 be effective. These springs can be in corresponding recesses of the two discs 593 . 594 as well as the flange 541 be taken, these recesses - viewed in the circumferential direction - between the standoffs 567 can be introduced. In such an embodiment of the one direction, it is expedient if in the region of the non-positive coupling or friction device 590 provided springs have a significantly higher spring rate than the springs of the outer damper 513 ,

Also by the friction device 590 generated friction damping should be essential. be greater than that in Verdrehwinkelbereich the damper 513 existing friction damping, which among other things by the seals 574 . 574a , which on the flange 541 concerns, is generated.

In the described embodiments, a multi-stage spring characteristic between the corresponding flywheel elements can also be achieved by virtue of the fact that at least individual springs of a spring group or of a damper are shorter than the angular distance between the stop and application areas cooperating therewith. Also, by using such opposed to the receiving them annular channel sectors or cutouts or windows shorter springs a reset starting from a middle position or rest position between the two flywheel elements Verdrehwinkelbereich be created. The latter can, for example, in one embodiment according to the 5 and 6 be achieved in that the springs 245 have a smaller angular extent in the circumferential direction, as the angle between the arms 244 or the attacks 255 . 255a ,

The Invention is not limited to the illustrated and described embodiments limited. but includes also variants, by combination of individual in connection with the different embodiments described features or elements can be formed.

Claims (64)

Means for damping vibrations, in particular between a motor and a clutch in a drive train, with zwiszen two flywheel elements vorzusehender damping arrangement, wherein the input part, the first, connectable to the engine, and the output part, the second, a counter-friction surface for engaging a friction disc of the clutch Flywheel element is, characterized by the following features: a) the damping arrangement has a radially outwardly closed, annular chamber ( 30 ), which radially outside a ring channel ( 51 ) forms, in the energy storage, such as springs, are added. b) on the lateral boundary wall of the annular channel ( 51 ) are provided first support areas for acting on ends of the energy storage, c) in the annular channel ( 51 . 151 . 251 . 551 ) protrudes with the second flywheel element ( 4 . 204 . 504 ) in rotary closure flange body ( 41 . 141 ; 241 . 541 ), which forms second support regions for acting on energy storage ends, into it, d) the energy accumulator provided between the first and second support regions (FIG. 45 ; 145 ; 245 ) between the flywheel elements ( 3 . 4 ; 203 . 204 ) at least a relative rotation of ± 25 degrees, starting from a middle position; to, e) the flywheel element forming the annular channel has sections which axially overlap the force accumulators and support them with centrifugal force f) in the annular chamber (FIG. 30 ) is a viscous medium or a lubricant, such as silicone oil or fat provided. Device according to claim 1, characterized in that with "n" force accumulators ( 45 . 145 . 245 ) on the same diameter, where 2 ≤ n ≤ 4, the individual energy storage ( 45 . 145 . 245 ) extend over 70 to 96% of an angular sector, the angle sector 360 Degrees / n. Device according to claim 1 or 2, characterized in that in the channel-like receptacles ( 51 . 152 . 251 . 551 ) arranged springs ( 45 . 145 . 245 ) are at least approximately pre-curved to the radius at which they are placed. Device according to one of claims 1 to 3, characterized that the Springs on from the flange body radial arms formed in the radial region of the Open out channel, supportable are. Einrichturg according to one of claims 1 to 3, characterized in that the springs are supported on radial arms formed by the flange body, which are included in the radial region of the annular channel, and that these cantilevers pass into a the springs in the circumferential direction cross-bridge. Device according to claim 5, characterized in that that the Jetty is included in one over the Ring channel outgoing radial recess thereof. Device according to one of claims 1 to 6, characterized that the Ring channel is formed of two shell-like bodies. Device according to one of claims 1 to 7, characterized that at least one of the shell-like bodies a sheet metal part is. Device according to claim 8, characterized in that that the Ring channel is formed by two half-shell-shaped sheet metal parts. Device according to one of claims 1 to 9, characterized that the Supports for the springs through in the otherwise over the circumference continuously formed annular channel elements used are formed. Device according to claim 10, characterized that the supports through - in the neutral position of the damper - on both sides the boom located forming rivets are formed. Device according to one of the preceding claims, characterized characterized in that supports through bag-shaped Moldings are produced. Device according to one of claims 1 to 12, characterized that at least a cantilever of Flanscchkörpers across from the both sides of this provided supports the annular channel - in the circumferential direction considered - one having smaller extension. Device according to one of claims 1 to 12, characterized that at least a boom of the flange across from provided on both sides of the same supports in the annular channel - in the circumferential direction considered - a larger extension having. Device according to one of the preceding claims, characterized characterized in that between at least individual cantilevers and springs liners are provided, the the cantilevers cross-sectional areas of those of the springs adapted receiving ring channel are. Device according to claim 15, characterized in that that the Intermediate layers in the annular channel Displacement piston for the form viscous medium. Device according to claim 15 or 16, characterized that the Liners an axial cutout or an axial recess exhibit. Device according to one of the claims 1 to 17, characterized that the Ring channel at least over Subregions of the length extension of at least some springs does not have a constant cross-section. Device according to one of claims 1 to 18, characterized that at least some of them are in the end sections of the uncompressed springs located areas of the annular channel with respect to the other areas of this channel are extended in cross section. Device according to one of the preceding claims, characterized characterized in that radially within the ring channel mindetens another spring group of dämpfungsvorkehrung is provided. Device according to one of claims 1 to 20, characterized that the Flange body radially outer by radial boom in Umgfangsrichtung mutually separate cutouts possesses, in which the springs of the first spring group are added are, as well as radially inner window has, through separated radial webs and provided in which the springs of the other spring group are. Device according to claim 21, characterized that between provided at least individual radial webs and springs liners are. Device according to claim 21 or 22, characterized that the Boom and / or the radial webs of the flange in Have circumferential direction facing wet, which in a recess the intermediate layers and / or engage in the spring ends. Device according to claim 23, characterized that at least the end portions of the springs are set by the wet so that they have no They have contact with the radially outwardly overlapping areas of the Flange body and / or the receiving flywheel element. Device according to one of Claims 20 to 24, characterized that the provided in the annular channel first spring group and the radially further inside arranged another spring group between the flywheel elements are arranged in parallel. Device according to one of claims 20 to 25, characterized that the Spring groups in stages, i. use angular offset. Device according to one of Claims 20 to 26, characterized that at least individual springs of at least one spring group gradually, that is angularly offset deploy. Device according to one of claims 20 to 24 or 26, 27, characterized in that the provided in the annular channel first spring group and the radially further arranged inside another spring group between the flywheel elements are arranged in series. Device according to one of Claims 21 to 28, characterized that in Viewed circumferential direction, radially innernalb a section respectively a window is provided. Device according to one of claims 21 to 29, characterized that in Viewed circumferentially, the cutouts and the windows at least nearly equal in angle are. Device according to one of Claims 21 to 30, characterized that the first and further spring group each have a maximum of four energy storage. Device according to one of claims 1 to 31, characterized in that radially within the annular channel, the housing halves or the shell-like body have mutually facing areas, the one for the flange Make passage. Device according to claim 32, characterized that the form annular surfaces on each other to areas that form a circular gap limit, which opens into the annular channel. Device according to claim 33, characterized that the Gap width at least approximately the thickness of the flange body equivalent. Device according to claim 33, characterized that the Slit 0.1 mm to 2 mm wider than the areas recorded therein of the flange body. Device according to one of Claims 20 to 35, characterized that the housing halves or the shell-like bodies have axial indentations for receiving the inner spring group. Device according to one of Claims 20 to 36, characterized that the axial indentations, the passage for the flange and the Ring channel merge into each other. Device according to claim 36 or 37, characterized characterized in that Indentations at least in the radially outer region on the circumference of the Cross section of the power storage are aligned. Device according to one of Claims 20 to 38, characterized that the inner springs of the further spring group on at least approximately the Pre-curved diameter are they are placed on. Device according to one of claims 1 to 39, characterized that the inner and / or outer springs at least under the influence of centrifugal force on the overarching in the circumferential direction Webs of the flange body support radially. Device according to one of Claims 20 to 39, characterized that the inner feathers at least under centrifugal effect on the indentations delimiting areas support radially. Device according to one of claims 36 to 40, characterized dadurcrh, that the Indentations annular are, i. above the extent of the device are continuous and the support areas in Circumferential direction for the energy storage by attached in the bookings stop elements are formed. Device according to claim 42, characterized that the Stop elements are formed by form rivet. Device according to Claim 43, characterized that the Beaufschlagungsbereiche the form rivet for the energy storage just or are flattened. Device according to one of the preceding claims, characterized characterized in that Feathers of the inner spring group included in the second window windows are, with the other, with the drive train connectable flywheel element in rotary connection and axially between them one the radially outer and pick up the radially inner spring group in series coupling flange. Device according to one of claims 1 to 45, characterized in that the one flywheel element, the one, having a profile component of an axial extension connection and the other flywheel element, the counter profile of the two flywheel elements rotationally coupled Have draw compound. Device according to claim 46, characterized that the Spring groups of the damping arrangement in one with a viscous or pasty medium at least partially fillable chamber are received, which essentially by the components of one, connectable to the engine flywheel element is formed and the output part of the damping arrangement is formed by a flange-like component, the profiling which are engageable with on the other flywheel element provided Gegenorofilierungen, continue one of the flywheel elements wearing a sealing element, the mating of the two flywheel elements on one area the other of the flywheel elements sealingly comes to rest. Device according to claim 46 or 47, characterized that this Flange-type output part of the damping pre-feed, like flange body, over the Profilinierungen the stretched joint with the other flywheel element a rotational lock Has coupling, but not fixed axially. Device according to at least one of the preceding Claims, characterized in that the Flange-type output part of the damping arrangement, like flange body, axially floating between the two housing halves or the shell-like bodies the connectable with the engine flywheel element is mounted. Device according to one of Claims 46 to 49, characterized that the Counterprofiles on the outer circumference an annular disc-like component connected to the other flywheel element are provided. Device according to at least one of the preceding Claims, characterized in that the Volume of the viscous medium received in the chamber such is measured that the inner second spring group immersed in this at least partially. Device according to one of the preceding claims, characterized characterized in that between the Flywheel elements at least one friction device is effective. Device according to one of the preceding claims, characterized characterized in that between the Flywheel elements at least one in the circumferential direction with play Afflictive friction is effective. Device according to claim 54 or 53, characterized that the Friction device in which formed by the housing halves and the shell-like body Chamber for viscous medium is added. Device according to one of the preceding claims, characterized characterized in that outside the with viscous medium, like pasty Medium, at least partially filled Room or ring channel in addition a dry friction damping device effective between the two flywheel elements is provided. Device according to one of the preceding claims, characterized characterized in that between the Flywheel elements at least one with the effective between them Springs connected in series friction damping device is present. Device according to one of the preceding claims, characterized characterized in that with the inner spring group parallel effective friction damping and / or viscous damping is substantially less than that of the outer spring group connected in parallel, viscous damping and / or friction damping. Device according to one of the preceding claims, characterized characterized in that at least individual of the springs shorter are as the circular arc section between the stops. Device according to one of the preceding claims, characterized characterized in that radially outside arranged in the chamber energy storage between the flywheel elements have a resilient torsional stiffness, of the order of magnitude from 2 to 15 Nm per degree. Device according to at least one of the preceding Claims, characterized in that the radially outside provided in the chamber energy storage between the flywheel elements a resilient torsional stiffness in the order of 2 to 4 Nm per Generate degrees. Device according to at least one of the preceding Claims, characterized in that a the chamber limiting components carries a starter ring gear. Device according to at least one of the preceding Claims, characterized in that the Ring channel at least in the radially outer region is aligned to the cross section of the energy storage, Device according to one of the preceding claims, characterized in that the ring channel is at least partially filled with viscous medium, such as a pasty agent, Device according to one of the preceding claims, characterized characterized in that - in the circumferential direction considered the device - the Force storage between their respective assigned support areas Centrifugally supported.