DE3926384A1 - Torsional oscillation damper in vehicle drive-line - has input and output part, with two torsional spring arrangements and stops - Google Patents

Abstract

The torsional oscillation damper is fitted in the drive line of a vehicle with an IC engine. It has an input part, output part and a torsional spring arrangement (F). Parallel to this first torsional spring arrangement (F) is a second torsional spring arrangement (f) which has a sprung characteristic line with negative course at least near the partial torsion angle. The second torsional spring arrangement (f) has a range of action restricted by stops (7, 8, 9). USE/ADVANTAGE - A very flat sprung characteristic line is produced which uncouples the IC engine and drive mechanism to prevent the transmission of vibrations.

Description

The invention relates to a torsional vibration damper in the drive train of a motor vehicle with an internal combustion engine with an input part, an output part and a torsion spring device, the spring characteristic of which is designed in such a way that with increasing angle of rotation an increasing torque is transferable.

Torsional vibration dampers of the type mentioned above are in known in diverse forms. They are usually structured that - starting from a load-free neutral position - with increasing torque and thus with increasing springs are switched on in succession at the angle of rotation, so that the resulting spring characteristic with less Inclination begins and ends with a large inclination. One if possible low inclination of the spring characteristic would be desirable from the Demand for the best possible decoupling between the Brenn engine and the vehicle drive. On the other hand it is not possible to goal with such flat spring characteristics sion vibration damper to build, as the resulting Would twist angle of twist. In addition, there would be additional problems me arise with an abrupt load change.  

From the German patent 34 13 695 is a torsion Vibration damper known that by connecting in series a very flat initial characteristic of springs of various types line and then a steeper characteristic curve. From European patent specification 1 65 874 is a torsion Vibration damper known that the system with the flat Spring characteristic curve when a certain speed is exceeded completely bridged, so that only the steep spring characteristic remains and the possible twisting angular deflection is limited under load. At the same time with this complex construction meets load change problems.

It is an object of the present invention to improve to achieve the vibration decoupling bypassing the Disadvantages of the prior art.

The object is achieved by identifying the Main claim solved. By overlaying a first one conventional torsion spring device with a second, which at least over a partial twist angle of the maximum twist angle is also effective and their spring characteristic one negative course, it is possible to use this subver angle of rotation to achieve a very flat spring characteristic, which the favorable decoupling between internal combustion engine and An drive caused.

It is further suggested that this second torsion spring be used direction in its area of action can be precisely determined by stops limit and via a one-way effective in both directions of rotation to control the clutch. With this control it is possible the area of action of the second torsion spring device to shift the overall characteristic so that it is in each case currently used working point is used. This is ensures that the working point has a very flat spring characteristic line can be achieved while the basic spring characteristic has a much steeper increase, so that - in the Hin look at the maximum torque to be transmitted - the off strikes the torsional vibration damping device relatively small can be held.  

According to the invention, the one-way clutch can be in shape be designed a friction device, the frictional force at least at least slightly larger than the maximum force the second torsion spring device. So that is rich with everyone change in the application of force ensures that the Elements of the second torsion spring device automatically in their new impact position will be brought. It also has Friction device has the advantage that it is large angle gene, the area of action of the second torsion spring device tion temporarily exceeds as damping takes effect.

However, it is also easily possible to use the one-way clutch in the form of a clamping freewheel which is effective in both directions of rotation train who when passing through the neutral middle position is switchable. Such a facility would come without one Friction device. Any other necessary then rubbing device could then be independent in its frictional force gig be tuned by the second torsion spring device.

According to a further feature of the invention, the second Torsion spring device at least one composite spring, the composed of two preferably identical plate springs is set that both with their conically widening Pages joined together and without a gap to one another fixed unit are connected, the composite spring one on the one hand in the area of their outside diameter and on the other hand in Area of the inner diameter or the center of one the parts input part or output part is acted upon and from an unstable middle position on both sides is at least partially relaxed. A compound spring this type has a spring characteristic that over a Part of their sphere of activity is negative. At match the restriction of the mobility of the composite spring this negative part of the spring characteristic can be very simple means made the proposed overlay will. By superimposing a positive spring characteristic with a negative spring characteristic is the desired one very much flat rising spring characteristic can be realized.  

However, the second torsion spring device can also be made of sheet feathers are shown between two at a distance of mutually supported and rotatable parts under longitudinal preload voltage are clamped at both ends and at the site tion approximately perpendicular to the longitudinal preload from an unstable Middle position at least partially on both sides can be relaxed wisely.

Another constructive solution can also be done using screws springs take place, this under tension between tele Skop-like holders are used and the holder over Rolling surfaces between a cylindrical inner contour and a cylindrical outer contour with the appropriate distance are arranged concentrically to the axis of rotation such that when Rotate the inner contour in relation to the outer contour of the holder be pivoted over the rolling surfaces and the screw change from an unstable, radial center position be relaxed at least partially in both directions of rotation can. Such a construction is therefore common Chen coil springs to realize.

For particularly advantageous application in the present case suggested that the pivoting movement of the holder before the full constant relaxation of the coil springs by stops is bordered. This also ensures that at Reversal of the direction of rotation of the torque application an immediate Use of the second torsion spring device over the before existing contact pressure of the coil springs can take place. Next hin is a fixation of those rolling surfaces that with the Stops are advantageous by a toothing. This ensures that a relative movement over the Stop only on the opposite rolling surfaces is possible.  

Another way of displaying a negative spring Characteristic curve can take place in that two concentrically to each other the spring washers and the rotation axis are provided, between which several spreading elements distributed around the circumference be pivotally arranged between stops, their length is greater than the radial distance between the spring washers in the unloaded state, so that the spread when pivoting elements from their radial, unstable middle position the elastically tensioned spring washers at least partially ent be stretched. The pivoting movement of the expansion elements is transferred directly to the torque-transmitting parts, wuh rend the spring washers themselves are freely arranged.

When using a friction device to control the second torsion spring device, this friction device conventional components exist. This is at least necessary Lich an input part and an output part and in between a spring for generating a contact pressure, from which the Friction results. In addition, you can also target specific ones Friction elements are used with which both an exact Determining the frictional force is possible as well as minimizing it of wear at this point.

However, it is also possible to control it using a clamp to realize free running. According to the present inven This consists of several parts distributed around the circumference nig arranged pinch rollers, each spring to each other are loaded on a cylindrical raceway of a hub con center on the axis of rotation and with inner raceways in a carrier cooperate in the direction of action of the spring lining the pinch rollers represent a narrowing gap, a cover plate is arranged on both sides of the carrier is net, the two cover plates with the entrance part of the gate Sions vibration damper are firmly connected and with a Engage the nose between the two pinch rollers for rotation direction-dependent unlocking in one direction of rotation and wherein also between the cover plates and the carrier Spring device is arranged. The starting part is the provided with the cylindrical raceway hub.  

Such a freewheel clutch is more complex than a pure one Friction device, but his moment jump is at Drehrich not reversed by a friction device.

The invention is then based on several embodiments games explained. The individual shows:

Figures 1 and 2, the generation of a negative spring characteristic with the help of disc springs.

Fig. 3 to 5 generation of a flat spring characteristic by the combination of a steep spring characteristic with a superimposed negative characteristic, to control via friction device;

Fig. 6 is the contracted characteristic at dently control via a clamping freewheel;

FIGS. 7 and 8 are schematic diagrams showing the arrangement of the spring means and the control mode;

FIGS. 9 and 10 structural configuration of the example of a clutch disc;

Fig. 11 shows a modification with radially clamped leaf springs;

Fig. 12 to 14 use of coil springs with rolling surfaces in connection with a two-mass flywheel;

Figures 15 and 16 illustration of a clamping freewheel;

Fig. 17 and 18, the generation of a negative spring characteristic by means of spring rings and spread elements.

Fig. 2 shows two disc springs 1 and 2 , which are placed one on top of the other with their conically opening sides and are brought into contact with one another by means of a rivet 4 under pretension. This creates a composite spring 3 which, in the form shown, assumes an unstable central position. You can experience a conical deformation on both sides and this property can be used to generate a negative spring characteristic. In Fig. 1, the development of the spring characteristic of the composite spring 3 is reproduced. The two spring characteristics F ₁ and F ₂ represent the individual characteristics of the diaphragm springs 1 and 2 , respectively. When the spring characteristic F ₁ is set, the diaphragm spring 1 has been loaded in the direction of the arrow and the spring force F recorded over the spring travel S. In the diaphragm spring 2 , the loading was carried out in the opposite direction and the spring characteristic F _{1 was} subtracted from the spring characteristic F ₂ . As a result of the spring characteristic F ₃ , which rises from a negative spring force according to FIG. 1, changes into a positive spring force, after a positive maximum changes into a negative branch, which in turn passes through the unstable zero position and a second maximum in the negative spring force range to then go back to the positive range. The negative part of the spring characteristic F ₃ with its partial spring travel ST can be made usable for the desired use by appropriate limit limitation. Proposed solutions will follow later with reference to FIGS. 9 to 18.

In FIGS. 3 to 5, the formation of the overall spring characteristic is shown line, where it is assumed that the control of the elements for generating the negative spring characteristic curve (with play, the composite spring 3) via a friction device R he follows, which is connected in series with the Spring device f and therefore must be made at least slightly larger than the maximum spring force when the torque is reversed. This constellation is shown in Fig. 4. The partial twist angle is specified in the present case with α T and is determined by fixed stops. It corresponds to the partial spring travel ST of FIG. 1.

If, for example, the unstable but force-free zero position is assumed, the spring travel F _{31 runs} from the zero position on a negative spring characteristic up to the con structively defined stop, which corresponds to the maximum size of the spring force MF. When moving beyond this point, the spring force is first released and then the full friction torque MR is built up. This is slightly above the value of MF. This results in a jump upwards in the characteristic according to F ₃₂ . With further movement in the same direction, the spring characteristic F ₃₃ runs horizontally and only when the movement reverses will the spring preload force MF and additionally the friction force MR be overcome via F ₃₄ until the returning spring characteristic F ₃₅ can be moved. If the entire area of application α T is used and further movement takes place in the same direction, then the overall jump must be made again via the spring characteristic F ₃₆ before it can continue on a horizontal characteristic F ₃₇ . This entire arrangement results from the fact that the spring device and the frictional force are connected in series to one another. If this characteristic curve F _{3 is} superimposed with the general characteristic curve F accordingly in FIG. 3, the overall characteristic curve results in accordance with FIG. 5. This shows outside the partial rotation angle α T a curve corresponding to FIG. 3 and within this angle a curve with a clear characteristic curve inclined less. As long as the use of the torsional vibration damper the occurring torque changes remain within the partial angle of rotation α T, the flat spring characteristic F _G1 or F _G5 according to FIG. 5 is effective. This means a significantly better decoupling of internal combustion engine and motor vehicle drive despite an overall sufficiently steep main spring characteristic according to FIG. 3, so that the overall deflection angle of the torsional vibration damping device remains structurally easy to control.

The development of the overall spring characteristic on the basis of FIGS. 3 to 5 is drawn together in FIG. 6 and shows the result of the combination of a negative spring characteristic, which is controlled via a clamping freewheel.

It is assumed that the clamping freewheel works in an ideal manner without any friction. Compared to FIG. 5, the total spring characteristic lies on characteristic F corresponding to FIG. 3 outside the partial angle of rotation α T.

FIGS. 7 and 8 show the equivalent graphs of nachfol quietly to be described constructions. In FIG. 7, a torsion spring device F is connected between an input part 5 and an output part 6 , to which the torsion spring device f is connected in parallel, which in turn is arranged in series with the friction device R. The effective area of the torsion spring device f is fixed with α T and this is realized by stops 7 to 9 . In contrast to Fig. 7, the torsion spring device f is connected to the output part 6 via a clamping freewheel FR in Fig. 8. Here, too, stops 7 to 9 are provided for determining the negative spring characteristic of the torsion spring device f.

FIGS. 9 and 10 show a running example, in conjunction with a coupling plate 15. This consists of a hub 18 with a hub disk 21 , which is arranged as an output part in a rotationally fixed manner on a gear shaft. On both sides of the hub disc 21 cover plates 19 and 20 are arranged, the torsion springs in the form of coil springs 17 are in rotary connection with the hub disc 21 . When loading the Reibbe layers 16 on the cover plate 19 with a torque, this torion spring device F can supply a spring characteristic with a medium pitch, for example according to FIG. 3. Parallel to this torsion spring device F, a torsion spring device f is connected between the input and output parts of the clutch disc 15 , which provides a negative spring characteristic, for example, according to FIG. 4. The connection of this Torsionsfedereinrich device f takes place via a hub disk 22 which is fixedly arranged on the hub 18 and via two cover plates 23 and 24 which are connected via the friction device R to the cover plate 19 . The friction device R consists of conventional components, a driving plate 25 being fixedly arranged on the cover plate 19 and an axially acting spring generating a frictional force between the driving plate 25 and the two cover plates 23 and 24 .

The torsion spring device f is clearer from Fig. 10 it clearly. Here are several circumferentially distributed composite springs 3 corresponding to FIG. 2 provided that ges in the region of Außenumfan are in windows 26 of the two cover plates 23 and 24 are once held, and which are on the other hand acted upon by projections 28 of the hub disc 22 through its central region, the Projections 28 are part of windows 27 . The composite springs 3 are not round but flattened on two opposite sides to save axial space. The torsion spring f is in its maximum From proposals limited by pins 9, which are arranged in the cover plates 23 and 24 and engage into corresponding recesses of the hub disc 22 can abut there against edges 7 b. A partial rotation angle α T1 or α T2 can be covered in both directions of rotation from an unstable middle position according to FIG. 10. With this con construction, an overall characteristic curve according to FIG. 5 can be aimed.

Fig. 11 shows a section of a structurally different solution torsion spring device f, here are not used Ver bundfedern but leaf springs 10 which extend radially and are clamped on the one hand in the hub disc 22 and on the other hand in the cover plate 23 and 24 while observing a radial preload. These leaf springs 10 are arranged symmetrically with their bulges due to the radial clamping th - starting from the unstable middle position - to achieve a smooth course of the characteristic curve on both sides. The stops are realized in this case by lugs 8 on the hub disc 22 and by 7 a on the cover plate 23 .

In Figs. 12 to 14, the torsion spring is f generated by conventional coil springs and this assembly is installed in a two-mass flywheel, as is already known in many forms.

The two-mass flywheel 29 consists in a known manner of a first flywheel 31 and a second flywheel 32 , both of which are used in the drive train of an internal combustion engine and which are arranged concentrically to one another about the axis of rotation 30 and are mutually supported by a bearing 33 . To take rotation, a torsion spring device F is provided between the two flywheels 31 and 32 , to which a friction device 34 can be arranged par allel. Also parallel to the torsion spring device F, the torsion spring device f is arranged and it is also effective between the two flywheels 31 and 32 . The Torsionsfederein direction F consists in a conventional manner of the two cover plates 35 and 36 on both sides of a hub disc 37 , where the two cover plates are firmly connected to the first flywheel 31 and the hub disc with the second flywheel 32nd In between, torsion springs 17 are arranged in the form of screw springs and they never produce a conventional spring characteristic with medium spring stiffness. Between the cover plate 36 and the second flywheel 32 is disposed, the torsion spring f and consists of a plurality of circumferentially spaced brackets 38 and 39 corresponding to FIGS. 13 and 14. The two holders are each guided telescopically in one another and are determined by the pre-tensioned coil springs 11 from each other, charged away. The holder 38 and 39 each have Abwälzflä surfaces 40 and 41 , which rest on the one hand by the force of the coil springs 11 on a cylindrical outer contour 44 of the cover plate 36 or on a cylindrical inner contour 45 of the guide part 43 . The guide member 43 is attached directly to the second flywheel 32 . Furthermore, on the guide part 43 a plurality of circumferentially distributed and radially inward-facing strikes 7 c are provided which limit the effective range of the torsion spring device f. The two holders 38 and 39 are each secured by a holding rivet 48 and an elongated hole 49 to facilitate assembly. Cover disks 46 and 47 are arranged on both sides of the holders 38 and 39 , of which the cover disks 47 are simultaneously held by the holding rivets 48 and the cover disks 46 via separate rivets. This cover discs represent the axial securing of the holder 38 and 39 with respect to the cylindrical contours 44 and 45 .

In addition, one of the cover plates 47 is provided in the region of its outer circumference with a toothing 42 which engages in a corresponding counter toothing of the guide part 43 . This toothing is used less for torque transmission than for fixing the position of the holders 38 and 39 in each case between two circumferentially spaced stops 7 c.

The function is now as follows: By applying torque to the two-mass flywheel 29 and by torsional vibrations, the holders 38 and 39 are pivoted about their unstable central position shown in FIG. 13 to both sides and the bias of the coil springs 11 , which are in the neutra len but unstable central position according to FIG. 13 does not bring, with increasing pivoting a circumferential component that generates a negative spring characteristic. Before reaching the complete relaxation of the coil springs 11 , the holder 39 strikes the stop 7 c and thus limits the mode of operation of the torsion spring device f. A further movement of the cover plate 36 beyond this stop is readily possible and there is a sliding movement relative to the holders 39 . When the direction of rotation is subsequently reversed, the holders 39 are immediately pivoted again via the rolling surfaces 40 and the effect of the torsion spring device f is ensured.

In Figs. 15 and 16 is the already explained in principle structurally angespro chene clamping freewheel FR in one embodiment. In this case, 53 inner raceways 54 are arranged in a carrier, which, together with pinch rollers 50 and with a cylindrical raceway 52 on a hub 18, form the clamping freewheel FR. Overall, several of these elements are evenly distributed on the circumference. The inner raceways 54 together with the cylindrical raceway 52 form clamping surfaces for the pinch rollers 50 in such a way that the two interconnected inner raceways 54 always form narrower gaps. Furthermore, the pinch rollers 50 are spring-loaded towards one another by corresponding springs in order to bring the pinch rollers into their respective clamping positions.

Laterally of the support 53 cover plates 55 and 56 are net angeord, which are rotatably connected to the cover plate 19, for example, the hitch be disc 15 of FIG. 9. The cylindrical raceway 52 is formed in one piece in the hub 18 and the hub disk 21 of the clutch disk. The two cover plates 55 and 56 are extended outwards radially inwards such that they engage with lugs 57 in each case between two together clamping rollers 50 and functionally bring one of the two clamping rollers 50 into the unlocking position. The Bol zen 9 used to connect the two cover plates 55 and 56 simultaneously connect both cover plates to the cover plate 19 and they act together with stops in the form of elongated holes 7 in the carrier 53 for the circumferential path limitation of the torsion spring device f, which is also between the carrier 53 on the one hand and the two cover plates 55 and 56 on the other hand is effective. The torsion spring device f can be of different types, in the present case it is based on composite springs 3 according to FIG. 2 and windows 26 and 27 as well as projections 28 approximately according to FIG. 10.

The function of the clamping freewheel FR is now as follows: FIG. 16 shows the one end position of the spring device f. In this position, the pinch roller 50 arranged on the right is brought into the release position by the lugs 57 . At the same time, the stops 7 and 9 are in operation. This position corresponds to a rotation of the cover plate 19 or the cover plates 55 and 56 in the direction of the arrow P with an assumed hub 18 . If a force is still maintained in the same direction of rotation, the parts 19 , 53 , 55 , 56 move together with the pinch rollers 50 in the direction of arrow P with respect to the hub 18 . When the movement reverses, the pinch roller 50 arranged on the left will immediately take effect and the carrier 53 will be blocked with respect to the hub 18 . As a result, the bolts 9 move from the strikes 7 away against the direction of arrow P and the full biasing force of the torsion spring device f must be overcome.

In the further course of motion, the superimposition of the negative spring characteristic curve from f over the unstable central position of the composite springs 3 up to the stop of the bolts 9 on the elongated hole 7 in the opposite position from FIG. 16. Here, in the area of the weak, unstable middle position of the composite springs 3, the clamping freewheel FR switched over by the lugs 57 releasing the clamping rollers arranged on the right, so that these are brought into the clamping position by the springs, while the clamping rollers arranged on the left are moved in the release direction. By reversing the clamping freewheel FR, the torsion spring device f which changes the direction of force can remain continuously active.

The force transmission of the torsion spring device f described in connection with FIGS. 15 and 16 during passage through the unstable middle position takes place in the subsequent construction according to FIGS . 17 and 18 by the already known te friction device R. The spring device f is here of two Spring rings 12 and 13 arranged concentrically to one another and to the axis of rotation 30 are shown, which are elastically deformed in the radial direction by expansion elements 14 , with several expansion elements 14 distributed on the circumference being provided, the radial extent of which is greater than the radial distance between the two spring rings 12 and 13 from each other in an unloaded state. The expansion elements 14 are fixed on both sides by cover plates 61 and 62 , the axial guidance of the two spring washers 12 and 13 being taken over at the same time. The force line in the torsion spring device f is carried out via bolts 58 , which are introduced, for example, on the cover plate 19 according to FIG. 15. In elongated holes 60, the bolts penetrate the expansion elements 14 in a radially outer position. In the radially inner position, bolts 59 are also inserted in elongated holes 60 , which are firmly connected to an inner frame 63 . This inner frame 63 is connected via the already known friction device R in a rotationally locking manner to the hub 18 of a clutch disc. On the frame 63 stops 7 d are arranged, which extend to the side of the expansion elements 14 in order to fix the working area of the torsion spring device f.

The function is as follows: starting from the unstable middle position shown, in which the expansion elements are loaded with maximum force by the spring washers 12 and 13 , but a component does not occur in the circumferential direction, there can be a swiveling on both sides, which is a negative spring characteristic in the form already described.

Since the described torsion spring device f only be in one agreed a negative spring characteristic can testify, is controlled by a Reibeinrich device or via a double-acting clamping freewheel ensures that it is automatically updated and therefore always in the respective working area of the torsional vibration damper can take effect.

Claims (10)

1. Torsional vibration damper in the drive train of a motor vehicle with an internal combustion engine having an input part, an output part and a torsion spring device, the spring characteristic of which is designed such that an increasing torque can be transmitted with increasing angle of rotation, characterized in that parallel to this first torsion spring device (F) a second torsion spring device (f) is arranged, which is additionally effective at least over a partial angle of rotation (α T) of the maximum twist angle and whose spring characteristic curve has a negative run at least in the region of the partial angle of rotation. 2. Torsional vibration damper according to claim 1, characterized in that the second torsion spring device (f) has a range of action limited by stops ( 7 , 8 , 9 ) and can be controlled via a way coupling (R, FR) effective in both directions of rotation, that when crossing the partial angle of rotation (α T) in one direction of rotation, the one-way clutch (R, FR) separates the connection and restores the connection when the direction of rotation is subsequently reversed. 3. Torsional vibration damper according to claims 1 and 2, there characterized in that the one-way clutch in the form of a Friction device (R) is formed, the frictional force at least least is set slightly larger than the maximum Force of the second torsion spring device (f). 4. Torsional vibration damper according to claims 1 and 2, there characterized in that the one-way clutch in the form of a Clamping freewheel (FR) effective in both directions of rotation is formed, when passing through the neutral means position of the second torsion spring device (f) switch is cash.   5. Torsional vibration damper according to claims 1 to 4, characterized in that the second Torsionsfedereinrich device (f) has at least one composite spring ( 3 ) which is composed of two preferably identical plate springs ( 1 , 2 ) such that both with their own conical he widening sides joined together and connected without a distance to each other to form a fixed unit, the United spring ( 3 ) on the one hand in the area of its outer diameter and on the other hand in the area of the inner diameter or center of one of the parts input part or output part is acted upon and off an unstable middle position is at least partially relaxed on both sides. 6. Torsional vibration damper according to claims 1 to 4, characterized in that the second Torsionsfedereinrich device (f) consists of leaf springs ( 10 ) between two spaced and rotatable parts ( 22 , 23 ) as the input part or output part below Longitudinal pre-tension are clamped at their two ends and are at least partially relaxed on both sides when the position changes approximately perpendicular to the longitudinal pre-tension from an unstable middle position. 7. Torsional vibration damper according to claims 1 and 2, characterized in that the second Torsionsfedereinrich device (f) consists of preloaded coil springs ( 11 ) which are inserted between telescopically guided holders ( 38 , 39 ) and the holder via rolling surfaces ( 40 , 41 ) between a cylindrical inner contour ( 45 ) and a cylindrical outer contour ( 44 ) as the input part or from the output part with a corresponding distance concentrically to the axis of rotation ( 30 ) are arranged such that when the inner contour is rotated relative to the outer contour, the holder over the rolling surfaces are pivoted and the coil springs are at least partially relaxed in both directions of rotation from an unstable radial central position. 8. Torsional vibration damper according to claim 7, characterized in that the pivoting movement of the holder ( 38 , 39 ) before complete relaxation of the coil springs ( 11 ) by stops ( 7 c) on which the inner contour ( 45 ) having guide parts ( 43 ) is limited and From parallel to the rolling surfaces ( 41 ) and the inner contour ( 45 ) a toothing ( 42 ) is provided. 9. Torsional vibration damper according to claims 1 to 4, characterized in that the second Torsionsfedereinrich device (f) consists of two concentric to each other and to the axis of rotation arranged spring washers ( 12 , 13 ), between which a plurality of circumferentially spreading elements ( 14 ) pivotally between Stops ( 7 d) are arranged and act on an input or output parts (R, 58 ) whose length is greater than the radial distance of the spring washers from one another in the unloaded state, so that when the spreading elements are pivoted out of their radial unstable central position out the elastically tensioned spring washers are at least partially relaxed. 10. Torsional vibration damper according to claim 4, characterized in that the clamping freewheel (FR) consists of several circumferentially arranged oppositely arranged pinch rollers ( 50 ), which are spring-loaded towards each other, on a cylindrical raceway ( 52 ) of a hub ( 18 ) concentrically The axis of rotation ( 30 ) rest and cooperate with inner raceways ( 54 ) in a carrier ( 53 ), which produce a narrower gap in the direction of action of the spring loading of the pinch rollers ( 50 ), with a cover plate ( 55 ) on both sides of the carrier ( 53 ) , 56 ) is arranged, which cover plates are firmly connected to the input part (cover plate 19) of the torsional vibration damper and which engage with a nose ( 57 ) between each of the two clamping rollers ( 50 ) for unlocking the direction of rotation in each case in one direction of rotation and also further the Torsionsfedereinrich device (f) is arranged between the cover plates ( 55 , 56 ) and the carrier ( 53 ).