DE19958811A1 - Rotary oscillation damper, for vehicle, for absorbing vibration caused by rotation, comprises elastic element for early reduction of torsional forces - Google Patents

Abstract

The vibration absorbing device (10) consisting of two units (12,14), radial moving and equipped with several spring units (36,40,42,48,50,52,58,62) is exposed to torsional forces acting in opposite directions or parallel, depending on the operation carried out by the user. An elastic element (56), positioned along the support surface (64) and enveloping a spring element (36,40,42,48,50,52,58,62) at least partly, absorbs the torsional forces at a very early stage and reduces the forces received by the main absorbing elements.

Description

The present invention relates to a torsional vibration damper, in particular dual mass flywheel, comprising a primary side and a with respect to the primary side against the action of a spring arrangement Rotary axis rotatable secondary side, the spring arrangement at least one, preferably a plurality of spring units, each Spring unit assigned on the primary side and the secondary side, respectively Support areas are provided on which the peripheral end areas of the respective spring units for torque transmission via respective Support elements are supported or can be supported, with at least one of the support areas on the primary side or the secondary side between this at least one support area and one for closing interaction with this provided at least one support area Supporting element acting and to act on this support element predamping arrangement in the direction away from the support region is provided.

Such a torsional vibration damper is for example from DE 41 41 723 A1 known. There is one between a respective support element and a pre-damping arrangement acting on a support area, which especially in the initial relative rotation range between the primary side and the secondary side with small angles of rotation or with small Loads provides a damping effect. This pre-damping arrangement thus acts in particular as an idle damper. Another operating state, in which such pre-damping arrangements are effective is a Transition from a train to a push operation, d. H. a transition from a state in which, for example, a braking torque of a drive unit is used in a state in which the drive unit  again outputs a drive torque. When passing through the zero position, i. H. of the basic relative rotation angle between the primary side and the secondary side, there is a change in the interaction of the respective outrigger range from primary and secondary side with the different support elements ment instead. That is, support elements, which previously with respect to the Primary side were now held by the support range of the secondary side and have to consider the Move primary side. Especially when attacking the support areas the secondary side to the support elements initially held on the primary side the centrifugal force-assisted holding torque must be overcome become. This often leads to the secondary side striking Support areas on these support elements, this impact in entire drive system is noticeable and often with ignition monitoring systems for incorrect detection of a misfire or Engine knocking leads.

It is the object of the present invention, a generic To design torsional vibration damper so that it is simple Structure can work very efficiently.

According to a first aspect of the present invention mentioned task solved by a torsional vibration damper special dual mass flywheel, comprising a primary side and a with respect to the primary side against the action of a spring arrangement Rotary axis rotatable secondary side, the spring arrangement at least one, preferably a plurality of spring units, each Spring unit assigned on the primary side and the secondary side, respectively Support areas are provided on which the peripheral end areas of the respective spring units for torque transmission via respective Support elements are supported or can be supported, with at least one of the support areas on the primary side or the secondary side between this at least one support area and one for closing  interaction with this provided at least one support area Supporting element acting and to act on this support element predamping arrangement in the direction away from the support region is provided.

It is further provided according to the invention that the pre-damping arrangement arranged on the at least one support area extending and at least along a support surface thereof in some areas at a distance from the support surface area Includes suspension element, which when moving the at least one support area and the associated support element is elastically deformable in the direction of the support surface area.

In this embodiment variant according to the invention, at very small space requirement at the beginning of the interaction of this at least one support area with a respective support element for pre-damping is provided, d. H. this support area does not strike undamped to the initially fixed support element, but the movement of the two components towards one another is made ready damped position of the suspension element.

It can be provided, for example, that the suspension element in a first end region of the same on the at least one support leg is rich and not at least in one intermediate area in one loaded state over the support surface area to the assigned Nete support element protrudes.

To ensure a stable interaction of the suspension element with the It is proposed to be able to provide at least one support area that the suspension element in the same at a second end region at least one support area is present or can be brought to bear.  

The transmitted torque becomes so great that the little immediately at least one support area with the assigned support element cooperates, so that the suspension element in an im Support surface area or recess formed in the support element is recordable, be ensured that a sufficiently flat System contact between the support area and the support element is generated without being between these components horizontal suspension element creates a point overload.

According to a further aspect of the present invention, the generic torsional vibration dampers are further developed such that the pre-damping arrangement is arranged on the support element netes, extend along a support surface area thereof and at least in some areas at a distance from the support surface includes a richly extending suspension element, which closes when facing each other movement of the support element and that interacting with it at least one support area in the direction of the upper support surface area is too deformable. Again, with little construction space required and with a very simple structure for efficient pre-damping when the at least one support area and the respective support element can be obtained.

For example, it can be provided that the suspension element itself extends along the support surface area and in the radial direction. Alternatively, it is possible that the suspension element extends along the Support surface area and inclined with respect to a radial direction extends. This design variant ensures that too low axial manufacturing tolerances or axial relative movements of The primary and secondary sides do not lead to a state with respect to one another can, in which the suspension element with the at least one Ab support area can interact.  

Here too it is necessary to provide an even load during load operation advantageous if the suspension element in a support surface rich of the support element or depression formed in the support area is recordable.

To fix the suspension element on the respective support element can be provided that the suspension element in its two End areas attacks on the support element and in an intermediate area protruding over the support surface area. For example the suspension element can be substantially U-shaped.

According to a further aspect, the task mentioned at the outset solved in that the pre-damping arrangement on the Abselele ment arranged and by a suspension element in the direction of assigned at least one support area biased pressure element comprises, wherein the suspension element on the support element on the one hand and the pressure element is supported on the other.

The suspension element can, for example, be a compression spring element, preferably comprise a helical compression spring.

In this embodiment variant, the compression spring element is preferably in the support element in the direction of movement on the associated guided at least one support area to be movable.

According to a further aspect, the present invention proposes a solution the task mentioned above that the pre-damping arrangement pivotally arranged on or near the at least one support region netes and preloaded into a basic position by centrifugal force bares pressure element, which includes an application area is in contact with the associated support element or can be brought and which when the at least one support area is moved towards one another  and the support element against the action of centrifugal force on the ground position is deflectable. This design variant has the advantage that it with increasing speed, d. H. also with increasing centrifugal force, a provides greater stiffness of the pre-damping arrangement, what is advantageous, as well as with increasing speed, the adherence of the respective support elements on the assigned slideways of the primary or secondary side becomes stronger.

The torsional vibration damper according to the invention can be designed in this way be that on each support area two support elements of circumferentially direction of successive spring units to each other essentially opposite circumferential sides are supported or supportable, and that between at least one of these support elements and the Support area acts a pre-damping arrangement.

In order to be able to take special operating conditions into account, suggested that only between one of the support members and the Support area acts a pre-damping arrangement. This effect can are used to the maximum extent, especially when preferably all, lying in different circumferential areas Support areas on the same circumferential side a pre-damping arrangement cooperates with an associated support element. Around in particular the critical condition of the Transition from a train to a push operation or the initiation of one To be able to take into account pushing operation, it is proposed that each Predamping arrangement on a peripheral side of a support area is provided, which when a drive system changes into a Overrun is effective.

Furthermore, in the torsional vibration damper according to the invention be provided that the primary side two at an axial distance from each other has arranged disc-like elements, each support area  the primary side a pair of axially opposite and each on one of the disk-like elements arranged support projections has that the secondary side between the two disc-like Elements of the primary side arranged central disc element, each support area of the secondary side one between each Includes pair of support projections positionable support arm, and that the at least one support area essentially by one of the Support arms is formed.

To be in such an embodiment between the support arms the secondary side in terms of interacting with it Provide provided support elements a certain clearance angle to be able to H. an angular range in which the secondary side can twist with respect to the primary side without the support arms on attack the respective support elements, in which angular range then the pre-damping arrangement can be effective, it is suggested that the support arms in their interacting with the support elements Sections have a smaller circumferential extent than that corresponding support projections in the corresponding with the Supporting areas interacting.

The present invention will hereinafter be described with reference to the accompanying Drawings in detail based on preferred embodiments described. It shows:

Figure 1 is a partial radial view of a torsional vibration damper shown in principle.

Fig. 2 is a partial axial view, partially broken away, showing a torsional vibration damper according to a first embodiment of the present invention;

Fig. 3 is a circumferential view of a suspension member used in the rotary shock absorber of Fig. 2;

. Figure 4 is an axial view of a support arm of a modified embodiment of the torsional vibration damper of FIG. 2;

FIG. 5 is a sectional view in FIG. 4 along a line VV;

Fig. 6 is a view corresponding to Figure 2 of an alternative embodiment.

FIG. 7 shows a circumferential view of a support element used in the embodiment of FIG. 6;

FIG. 8 shows a view corresponding to FIG. 7 of a modified embodiment;

FIG. 9 shows another view corresponding to FIG. 2 of a torsional vibration damper according to the invention;

FIG. 10 is a peripheral view of a support element used in the torsional vibration damper of FIG. 9;

FIG. 11 is another view corresponding to FIG. 2 of an alternative embodiment of a rotary vibration damper according to the invention;

Fig. 12 is another view corresponding to Figure 2 of an inventive design of a torsional vibration damper.

Fig. 13 is a longitudinal sectional view of a modified support arm, which can be used in the embodiment according to Fig. 12.

First, the basic structure of a torsional vibration damper, as it is also the subject of the present invention, is described with reference to FIG. 1.

The torsional vibration damper 10 basically comprises a primary side 12 and a secondary side 14 which can be rotated about an axis of rotation A with respect thereto. The primary side 12 is, for example, non-rotatably connected to a schematically illustrated drive shaft, for example crankshaft 16 , while the secondary side 14 is connected or connectable to a common rotation with an output shaft, also only shown schematically, for example transmission input shaft 18 , possibly with the interposition of a friction clutch or the like is.

The primary side 12 comprises two cover disk elements 20 , 22 which are axially spaced apart and are fixedly connected to one another, for example, by a radially outer cylindrical section. A central disk element 24 of the secondary side 14 lies axially between these two cover disk elements 20 , 22 . This central disc element 24 , which can be fixedly connected, for example, to a flywheel of a friction clutch or the like, has a plurality of support arms 26 which are distributed in the circumferential direction and project radially outwards and form respective support regions 28 of the secondary side 14 . Associated with each support area 28 of the secondary side 14 , the primary side 12 also has a support area 30 . This can be formed, for example, in the form of a pair of support projections 32 , 34 arranged opposite one another on the cover disk elements 20 , 22 . These support projections 32 , 34 can be fixed to the cover disk elements 20 , 22, for example by riveting or welding, but can also be formed there by stamping or the like. In the circumferential direction between respective support areas 28 of the secondary side 14 or support areas 30 of the primary side 12, there are respective spring units 36 of a spring arrangement generally designated 38. The spring units 36 are supported in their circumferential ranges 40 and 42, respectively, via support elements 44 and 46 on the support areas 28 , 30 or can come to rest on these support areas. In one embodiment variant, in which each spring unit 36 has a spring which extends almost in the angular range of 180 °, two such support regions 28 , 30 are then respectively provided at an angular distance of 180 °. It goes without saying that more than two such support areas 28 , 30 can be provided if the spring arrangement 38 is divided into correspondingly more spring units 36 . Furthermore, it should be pointed out that, of course, each of the spring units 36 can comprise a plurality of springs which follow one another in the circumferential direction and which are then supported on one another by respective sliding elements, these sliding elements, like the supporting elements 44 , 46 , being supported radially outwardly on a slide of the primary side 12 . In order to facilitate this sliding, the radial area in which the spring units 36 lie can be filled with lubricant. This lubricant also has the effect of a viscous damping, since the individual springs of the spring units 36 have to move while displacing the viscous medium and the lubricant. It should also be pointed out that, as can be seen in FIG. 2, for example, the spring units 36 can be constructed in such a way that they have a plurality of nested springs 48 , 50 , 52 , which ultimately act in parallel with one another in torque transmission operation and by superimposing their respective ones Characteristic curves lead to the desired vibration damping effect.

It can also be seen in FIG. 1 that the support areas 28 of the secondary side 14 have a smaller circumferential extent in their arm sections 26 interacting with the respective support elements 44 , 46 with respect to the support areas 30 of the primary side 12 . The result of this is that, starting from the neutral, essentially unloaded state shown in FIG. 1, the secondary side 14 , ie the central disk element 24 , can rotate freely with respect to the primary side 12 in a limited angle of rotation without damping occurring. Only when the support areas 28 come into contact with the support elements 44 or 46 lying on a peripheral side does the essential damping effect, for example the load damping effect, occur, in which the spring units 36 then move in one of their end areas, for example in the end area 42 . Support via a respective support element 46 on the support area or areas 30 of the primary side 12 and in their end area 40 via the support elements 44 by the support arms 26 , ie the secondary-side support areas 28 .

With such a torsional vibration damper 10, there is basically the problem that, for example, during the transition from a pulling operation into a pushing operation, a support element, for example 46, which is initially fixed relative to the primary side 12 , that is to say does not move on the associated slideway, after passing through the one shown in FIG. 1 neutral position is acted upon by the associated support arm 26 and first the static friction state, which is increased by centrifugal force, has to be converted into a sliding friction state with a correspondingly lower coefficient of friction. In order to avoid the occurrence of blows during this transition, which can lead to the incorrect detection of misfires, the present invention provides various measures which, when a respective support area 28 of the secondary side 14 approaches a support element 44 or 46 by means of pre-damping, are gentle Moving towards one another and thus producing a more or less gradual transition of the respective support element 44 or 46 into the sliding state.

It can be seen in FIG. 2 that a pre-damping arrangement 54 is provided on a respective support arm 26 of the secondary side 14 . In the embodiment variant shown in FIG. 2, this pre-damping arrangement 54 comprises an elongated suspension element 56 . This suspension element 56 is bent in a ring in an end region 58 and there surrounds a fastening pin or projection 60 provided on the support arm 26 . In its second end region 62 , the spring element 56, for example formed from spring steel, is supported on a support surface area 64 of the support arm 26 . In its intermediate region 66 lying between the end regions 58 , 52 , the suspension element 56 extends at a circumferential distance from the support surface region 64 , so that an intermediate space is formed there between the suspension element 56 and the support surface region 64 of the support arm 26 . If the central disk element 24 now moves counterclockwise with the fixed primary side 12 in the illustration in FIG. 2, the support arm 26 now moves toward the support element 46 , which is initially still supported on the support region 30 of the primary side 12 . In the course of this movement, the suspension element 56 , which in the embodiment variant extends essentially radially and along the support surface area 64 , comes with its intermediate region 66 to bear against a circumferential end of the support element 46 and is deformed due to its elastic deformability in the event of a continuing relative rotary movement, until it finally rests on the support surface area 64 or is received in a recess provided therein and not shown. During this movement toward one another, a pre-damping, for example also idle damping, takes place, which ensures that there is no spontaneous striking of the support arm 26 on the respective support element 46 , but that a gradual increase in force or torque takes place in order to gradually convert this support element 46 into a sliding state . The occurrence of impacts and the erroneous detection of a misfire with the corresponding output of a warning signal can thus be avoided.

It can be seen that such a pre-damping arrangement 54 is provided on the or each support region 28 of the secondary side 14 only on a peripheral side region. This is preferably the circumferential side, which then acts on a support element 46 when transitioning to overrun.

The suspension element 56 , which can also be molded into the support arm 26 in its first end region 58 , can also be designed in accordance with a further preferred embodiment variant such that it has the same width as the support arm 26 , in particular in its intermediate region 66 . A full-surface contact of the support element 46 via the suspension element 56 can then be obtained even in the event of a transition to the load state, in order to avoid selective overloading.

A modification of the pre-damping arrangement 54 described above is shown in FIGS . 4 and 5. It can be seen that there the spring element 56 is bent, for example from spring wire, and is fixed in its end region 58, for example by a rivet 70 or the like, on one side surface of the support arm 26 . With its intermediate region 66 , the suspension element 56 protrudes again in the circumferential direction over the corresponding support surface region 64 and onto the support element, which is not shown here. To avoid malfunctions, the other end region 62 is bent such that it lies laterally, ie axially next to the support arm 26 .

Figs. 6-8 show an alternative embodiment of a modern dynamic damper Invention. Components which correspond to the components described above with regard to structure or function are described with the same reference numerals with the addition of an appendix "a". In the following, essentially only structural differences from the embodiment according to FIGS. 2-5 will be discussed.

In the embodiment according to Fig. 6 46, the each between a supporting member a and a support portion 28 a of the secondary side 14 a acting pre-steaming assembly 54 a a suspension element 56 a on which is on the supporting element 46 a now provided with its intermediate portion 66 a in the circumferential direction arcuate over a support surface area 72 a of this support element 46 a on the support arm 26 a or its support surface area 64 a protrudes. As can be seen in particular in FIG. 7, a groove-like recess 74 a is provided in the support element 46 a, which extends essentially from radially inside to radially outside. In this groove-like recess, which has undercut-like depressions 76 a and 78 a on its radially inner and radially outer region, the essentially U-shaped suspension element 56 a is bracketed with its end regions 58 a, 62 a. When the support element 46 a and the support arm 26 a are moved towards one another, the spring element 56 a can deform and essentially completely enter the groove 74 a, so that an essentially full-surface contact again arises between the support element 56 a and the support arm 26 a .

In the modification of this embodiment variant shown in FIG. 8, the groove 74 a does not extend exactly in the radial direction, but rather is transverse with respect to the radial direction. This transverse position can cover a larger axial area with the same width of the spring element 56 a. The advantage is that even with a slight axial relative movement between the primary side 12 a and the secondary side 14 a, the support arm 26 a of the secondary side 14 a can always come into contact with the suspension element 56 a. The inclination angle with respect to the radial extension line can be in the range between 0 and 90 °. A wire ring or a leaf spring can be used here as the suspension element. A further modification of the embodiment variant shown in FIGS. 6-8 is shown in FIG. 9. In the embodiment variant shown in FIG. 9, the suspension element 56 a of the pre-damping arrangement 54 a is also provided on the support element 46 . Here, however, the suspension element 56 a is now fixed with its end region 62 a to the support element 46 a in that it is molded directly into the material of the support element 46 a, for example injected or overmolded by this material. This is easily possible in the manufacture of the support elements 46 a, since these are generally produced from plastic in an injection molding process. In its radially outer end region 58 a, the spring element 56 a engages again in the undercut 76 a - when viewed in the circumferential direction - and is ultimately secured there by being locked against being pulled out of the groove-shaped recess 74 a.

As can be seen in particular in FIG. 10, the width of the suspension element 56 a can also be selected in such a configuration variant, in which the suspension element 56 a is provided on a support element 46 a, such that it essentially corresponds to the axial width of the support arm 26 a or the axial distance between the two support projections of the primary side 12 a. It can thus also be ensured, without inclination, that contact is achieved between the spring element 56 a and the support arm 26 a, regardless of the relative axial position between the primary side 12 a and the secondary side 14 a. Furthermore, the broad embodiment has the result that the provision of the groove 74 a which extends completely in the radial direction can be dispensed with, since an essentially full-surface contact is also generated via the spring element 56 a, in which the support surface area 64 a of the support arm 26 s is essentially contacted over the entire surface. The corresponding depressions 76 a, 78 a are then only present radially outside and radially inside.

Another embodiment of a torsional vibration damper according to the invention is shown in Fig. 11. Components that correspond to the components described above with regard to structure or function are described with the same reference numerals with the addition of appendix "b". In the following, only the structural differences from the design variants described above are essentially dealt with again.

In the embodiment according to FIG. 11, an opening 80 b is provided in the support element 46 b. This opening 80 b has a first opening section 82 b with a larger diameter, which is followed by an opening section 84 b with a smaller diameter. The opening portion 84 b with a smaller diameter is open to the support surface area 72 b. The pre-damping arrangement 54 b here comprises a pressure element 86 b, which passes through the opening section 84 b with a stamp section and protrudes beyond the support surface area 72 b to the support surface area 64 b of the support arm 26 b. With a section 88 b of enlarged diameter, the pressure element 86 b is supported on the transition region between the opening sections 82 b, 84 b. Also supported on this section 88 b is a compression spring element, for example a helical compression spring 90 b, which is supported at the other end on a bottom region of the opening section 82 b with a larger diameter. On the pressure element 86 b, a centering projection 92 b is provided for the compression spring 90 b. Again, therefore, upon movement of the support arm 26 b to the support 46 b when the pressure element b 26 to the Abstützoberflächenbereich 64 b of the support arm 26 b abuts, first a Vordämpfungswirkung with gentle initiation of a sliding movement of the support member 46 b be achieved that the pressure element 86 b is displaced against the spring action of the compression spring 90 b, whereby it is guided with its stamp section into the opening section 84 b.

A very simple assembly can be obtained in that the support element 46 b in the region of the opening section 82 b with a larger diameter is open on at least one axial side, so that the pressure element 86 b, the total length of which is shorter than the length of the opening section 82 b, inserted from this axial side into the opening section 82 b and then can be moved with its stamp section in the opening section 84 b. Then the compression spring element 90 b is then used, which is also suitably held in the opening 80 b by the centering section 92 b even when the opening section 82 b is open laterally or axially.

The embodiment variant shown in FIG. 11 can also be designed such that the pressure element 86 b ultimately forms an integral part of the spring element 90 b. That means, for example, the spring element 90 b could be designed such that it has two sections of different winding diameters. A first section, which could ultimately also be formed by an end winding section that no longer provides an essential suspension function, then lies in the opening section 80 b, and a second section of smaller winding diameter then passes through the opening section 86 b and stands over the support surface area 72 b to the support arm 26 b forth. When the support arm 26 b and the support element 46 b are moved towards one another, this spring element is then deformed, at least in its winding section with a smaller diameter, in order to provide the previously described pre-damping function. In principle, it is also possible to use a compression spring element which is formed in an end region, for example, into the support element 46 b during its production process and which projects from the material body of the support element 46 b onto the support arm 26 b assigned to it. Other types of fixing such a spring element to the support element 46 b, for example sticking, are also possible.

Another type of embodiment of a torsional vibration damper according to the invention is shown in Fig. 12. Components which correspond to components described above with regard to structure or function are identified by the same reference numerals with the addition of the appendix "c".

In the embodiment according to FIG. 12, the pre-damping arrangement 54 c associated with the support element 44 c comprises a pressure element 100 c, which in its radially inner region is secured by a fastening pin or bolt 102 c on the central disk element 24 c of the secondary side 14 c about an axis of rotation A. substantially parallel axis is pivotally supported. The center of gravity S of this pressure element 100 c will be arranged in rotary operation in such a way that it lies on a radial line that is orthogonal to the axis of rotation A, intersecting it and passing through the fastening pin 102 c. In this state, the pressure element 100 c then protrudes in the circumferential direction with an application surface section 104 c over the support surface region 64 c of the support arm 26 c. If this support arm 26 c now moves in the circumferential direction towards the support element 44 c, which is initially supported, for example, on the support region 30 c of the primary side 12 c, then in the course of this movement the loading section 104 c of the pressure element 100 c on the support surface region 72 c of the support element ements 24 c come into contact. When the relative rotation continues, the pressure element 100 c is then pivoted against the action of centrifugal force, force having to be applied during this pivoting movement, since the center of gravity S is moved radially inward against the centrifugal force. The pressure element 100 c thus ultimately acts on the support element 44 c in the manner of a spring with low rigidity. However, this stiffness increases with increasing centrifugal force. This has the advantage that an increasingly stiffer pre-damping arrangement 54 c is opposed to the adhering effect of the support element 44 c on the slideway 45 c of the primary side 12 c, which also increases with increasing centrifugal force.

FIG. 13 shows a special embodiment of a support arm 26 c, which is axially shaped in its radially outer region and essentially accommodates the pressure element 100 c in a recess 110 c. In this way, the pressure element 100 c can also engage axially essentially centrally on the associated support element 44 c.

The preceding are embodiments of a torsional vibration damper in which due to the provision of a between respective support areas and support elements acting Predamping arrangement when the support areas interact or support elements for a gradual increase in the transmitted Torque is taken care of. A sudden striking at first support element still adhering to the slideway is avoided. To the Such a predamp is to make the structure as simple as possible arrangement only on a peripheral side area of a support area of the respective two support elements Provided secondary side, namely that peripheral area that at Transition to overrun becomes effective. Basically, however such also at the peripheral end region effective in train operation Predamping arrangement between a support area and a Support element act. It should also be noted that the provision or interaction of such a pre-damping arrangement with a respective support arm of a central disk element on the secondary side is particularly useful embodiment. Basically would be however, such an interaction of the support areas of the Primary side, d. H. the support projections of the same, with the support elements ment possible.

Furthermore, it should be noted that the one described above torsional vibration constructed in the form of a dual mass flywheel damper only with regard to its essential for the present invention aspects were described and presented. Such a spin  Vibration damper can be various other assemblies or Have functional areas. For example, the torsional vibration Damper have multiple planet gears on the primary side or the Secondary side are rotatably supported and by one on the other Side provided ring gear or sun gear, for example, by Shaping can be formed, driven to rotate at relative rotation become. It also goes without saying that a permanent one Friction device or a dragging acting friction device is provided can be, as well as a second set of spring units, in particular can also perform a damping function in the low-load range.

Claims (20)

1. Torsional vibration damper, in particular dual-mass flywheel, comprising a primary side ( 12 ) and with respect to the primary side ( 12 ) against the action of a spring arrangement ( 38 ) about a rotation axis (A) rotatable secondary side ( 14 ), the spring arrangement ( 38 ) at least one , preferably a plurality of spring units (36), each spring unit (36) assigned to the primary side (12) and the secondary side (14) each Abstützbe rich (30, 28) are provided, to which the peripheral end portions (40, 42 ) of the respective spring units ( 36 ) for torque transmission via respective support elements ( 44 , 46 ) are supported or can be supported, with at least one ( 28 ) of the support areas ( 30 , 28 ) of the primary side ( 12 ) or the secondary side ( 14 ) between this at least one support area ( 28 ) and a support element ( 46 ) provided for interaction with this at least one support area ( 28 ) ) acting and for the application of this support element ( 46 ) in the direction of the support area ( 28 ) away from the pre-damping arrangement ( 54 ), characterized in that the pre-damping arrangement ( 54 ) is arranged on the at least one support region ( 28 ) comprises a spring element ( 56 ) which extends along a support surface ( 64 ) and extends at least in some areas at a distance from the support surface area ( 64 ) and which, when the at least one support area ( 28 ) and the associated support element ( 46 ) are moved towards one another, elastically in the direction of the support surface area ( 64 ) is too deformable. 2. Torsional vibration damper according to claim 1, characterized in that the suspension element ( 56 ) in a first end region ( 58 ) thereof is fixed to the at least one support region and at least in an intermediate region ( 66 ) in an unloaded state via the upper support surface region ( 64 ) protrudes towards the associated support element ( 46 ). 3. Torsional vibration damper according to claim 2, characterized in that the suspension element ( 56 ) rests in a second end region ( 62 ) thereof on the at least one support region ( 28 ) or can be brought to bear. 4. Torsional vibration damper according to one of claims 1 to 3, characterized in that the suspension element ( 56 ) can be received in a recess formed in the support surface area ( 64 ) or in the support element ( 46 ). 5. torsional vibration damper, in particular dual-mass flywheel, comprising a primary side ( 12 a) and a secondary side ( 14 a) rotatable about an axis of rotation (A) with respect to the primary side ( 12 a) against the action of a spring arrangement ( 38 a), the spring arrangement ( 38) at least one, preferably a plurality of spring units (36 a), wherein each spring unit (36 a assigned) on the primary side (12 a) and the secondary side (14 a) each supporting areas (30 a, 28 a are provided) , on which the peripheral end regions ( 40 a, 42 a) of the respective spring units ( 36 a) are supported or can be supported for torque transmission via respective support elements ( 44 a, 46 a), with at least one of the support regions ( 30 a, 28 a) of the Primary side ( 12 a) or the secondary side ( 14 a) one between this at least one support area ( 28 a) and a support provided for interaction with this at least one support area ( 28 a) ement ( 46 a) acting and designed to act on this support element ( 46 a) in the direction away from the support area ( 28 a) away pre-damping arrangement ( 54 a), characterized in that the pre-damping arrangement ( 54 a) on the support element ( 46 a ) arranged, extending along a support surface area ( 72 a) of the same and at least in some areas at a distance from the support surface area ( 72 a), comprises a spring element ( 56 a) which, when the support element ( 46 a) and the at least one support area interacting with it, move towards one another 28 a) is deformable in the direction of the support surface area ( 72 a). 6. torsional vibration damper according to claim 5, characterized in that the suspension element ( 56 a) extends along the support surface region ( 72 a) and in the radial direction. 7. torsional vibration damper according to claim 5, characterized in that the suspension element ( 56 a) extends along the support surface region ( 72 a) and inclined with respect to a radial direction. 8. torsional vibration damper according to one of claims 5 to 7, characterized in that the suspension element ( 56 a) in a in the support surface area ( 72 a) of the support element ( 46 a) or in the support area ( 28 a) formed recess ( 74 a) can be received . 9. Torsional vibration damper according to one of claims 5 to 8, characterized in that the suspension element ( 56 a) engages in its two end regions ( 58 a, 62 a) on the support element ( 46 a) and in an intermediate region ( 66 a) above the support surfaces rich ( 72 a) protruding. 10. torsional vibration damper according to one of claims 5 to 9, characterized in that the suspension element ( 56 a) is substantially U-shaped. 11. Torsional vibration damper, in particular dual-mass flywheel, comprising a primary side ( 12 b) and a secondary side ( 14 b) rotatable with respect to the primary side ( 12 b) against the action of a spring arrangement ( 38 b) about an axis of rotation (A), the spring arrangement ( 38) b is at least one, preferably a plurality of spring units comprises (36 b), each spring unit is assigned (36 b) on the primary side (12 b) and the secondary side (14, respectively b) supporting areas (30 b, 28 is provided b) at which the circumferential end regions ( 40 b, 42 b) of the respective spring units for torque transmission are supported or can be supported via respective support elements ( 44 b, 46 b), with at least one ( 28 b) of the support regions ( 30 b, 28 b ) the primary side ( 12 b) or the secondary side ( 14 b) has a support between this at least one support region ( 28 b) and a support provided for interaction with this at least one support region ( 28 b) z-element ( 46 b) acting and for acting on this support element ( 46 b) in the direction away from the support region ( 28 b) is designed pre-damping arrangement ( 54 b), characterized in that the pre-damping arrangement ( 54 b) is attached to the support element ( 46 b ) arranged and by a spring element ( 90 b) in the direction of the associated at least one support region ( 28 b) biased pressure element ( 86 b), the spring element ( 90 b) on the support element ( 46 b) on the one hand and the pressure element ( 86 b) is supported on the other hand. 12. Torsional vibration damper according to claim 11, characterized in that the suspension element ( 90 b) comprises a compression spring element, preferably a helical compression spring ( 90 b). 13. Torsional vibration damper according to claim 11 or 12, characterized in that the pressure element ( 86 b) in the support element ( 46 b) in the direction of movement to the associated at least one support region ( 28 b) is guided to be movable. 14. Torsional vibration damper, in particular dual-mass flywheel, comprising a primary side ( 12 c) and a secondary side ( 14 c) rotatable about an axis of rotation (A) with respect to the primary side ( 12 c) against the action of a spring arrangement ( 38 c), the spring arrangement ( 38 c) at least one, preferably a plurality of spring units (36 c), wherein each spring unit (36 c) is associated with on the primary side (12 c) and the secondary side (14 c) in each case from the support portions (30 c, 28) At which the peripheral end regions ( 40 c, 42 c) of the respective spring units ( 36 c) for torque transmission are supported or can be supported via respective support elements ( 44 c, 46 c), with at least one ( 28 c) of the support regions ( 30 c, 28 c) of the primary side (12 c) or the secondary side (14 c) one (28 c) and a for cooperation with this at least one support portion (28 c between this at least one supporting portion) provided n support element ( 44 c) acting and for acting on this support element ( 44 c) in the direction away from the support area ( 28 c) is configured pre-damping arrangement ( 54 c), characterized in that the pre-damping arrangement ( 54 c) is at or near the at least a support area ( 28 c) arranged in a pivotable manner and prestressable by centrifugal force in a basic position comprises a pressure element ( 100 c), which is or can be brought into contact with an applied area ( 104 c) on the associated support element ( 44 c) and which can be moved towards one another of the at least one support region ( 28 c) and the support element ( 44 c) can be deflected from the basic position against the action of centrifugal force. 15. Torsional vibration damper according to one of claims 1 to 14, characterized in that on each support area ( 28 ; 28 a; 28 b; 28 c) two support elements ( 44 , 46 ; 44 a, 46 a; 44 b, 46 b; 44 c, 46 c) of spring units 36 which follow one another in the circumferential direction; 36 a; 36 b; 36 c) are supported or can be supported on essentially opposite circumferential sides, and that between at least one of these support elements ( 44 , 46 ; 44 a, 46 a; 44 b, 46 b; 44 c, 46 c) and the support region ( 28 ; 28 a; 28 b; 28 c) a pre-damping arrangement ( 54 ; 54 a; 54 b; 54 c) acts. 16. Torsional vibration damper according to claim 15, characterized in that only between one of the support elements ( 44 , 46 ; 44 a, 46 a; 44 b, 46 b; 44 c, 46 c) and the support area ( 28 ; 28 a; 28 b; 28 c) a pre-damping arrangement ( 54 ; 54 a; 54 b; 54 c) acts. 17. Torsional vibration damper according to claim 16, characterized in that in one, preferably all, lying in different circumferential support regions ( 28 ; 28 a; 28 b; 28 c) each on the same circumferential side a pre-damping arrangement ( 54 ; 54 a; 54 b ; 54 c) cooperates with an associated support element ( 44 , 46 ; 44 a, 46 a; 44 b, 46 b; 44 c, 46 c). 18. Torsional vibration damper according to claim 16 or 17, characterized in that each pre-damping arrangement ( 54 ; 54 a; 54 b; 54 c) is provided on a circumferential side of a support region ( 828 ; 28 A; 28 B; 28 C), which during transition of a drive system in an overrun mode is effective. 19. Torsional vibration damper according to one of claims 1 to 18, characterized in that the primary side ( 12 ) has two axially spaced disc-like elements ( 20 , 22 ), each support region ( 30 ) of the primary side ( 12 ) a pair of themselves Axially opposite and each on one of the disc-like elements ( 20 , 22 ) arranged support projections ( 32 , 34 ) has that the secondary side ( 14 ) between the two disc-like elements ( 20 , 22 ) of the primary side ( 12 ) arranged central disc element ( 24 ), each support region ( 28 ) of the secondary side ( 14 ) comprising a support arm ( 26 ) that can be positioned between a pair of support projections ( 32 , 34 ), and that the at least one support region ( 28 ) essentially extends through one of the support arms ( 26 ) is formed. 20. A torsional vibration damper according to claim 19, characterized in that the support arms (26) in its with the supporting elements (44, 46) co-operating portions of a lower peripheral extent have, as the corresponding supporting projections (32, 34) elements in the corresponding with the jacking (44 , 46 ) interacting areas.