DE3721710A1 - Vibration damper - Google Patents

Abstract

The invention relates to a vibration damper having two mutually vibrating elements between which damping means are provided, it being possible for one of the elements to be connected to a driving engine and for the other element to be connected to a transmission and at least two dampers being provided between these elements, at least one of which dampers is fully compressed to limit the relative movement between the mutually vibrating elements.

Description

The invention relates to a device for damping vibrations, especially in the drivetrain of a vehicle between the engine and transmission be with at least two flywheel elements rotatably mounted to each other th, between which damping means are provided and wherein the one Flywheel element is connectable to the engine and the other flywheel element via a clutch, like a friction clutch with the transmission is connectable.

Such devices usually have between as damping means the flywheel elements effective energy storage both in the circumferential direction, like coil springs that store elastic energy, as well as in axles effective energy storage, which in cooperation with friction or Sliding pads cause friction, i.e. hysteresis, in parallel is switched to the energy stores effective in the circumferential direction.  

The moments of inertia of the flywheel elements and those between them Effective damping elements are dimensioned such that the critical fundamental frequency or the critical speed of one with a sol Chen damping device equipped drive system below the Frequency of engine vibrations when the engine is operating above one Limit speed is.

To ensure proper operation of such a drive system To enable equipped vehicle, this limit speed is lower than the engine idle speed.

When turning the engine on and off, the kri table speed or the critical speed range is not sufficient be driven through quickly to build up large vibration ampli tuden between the two flywheel elements due to the occurring To avoid arousal. These large vibration amplitudes or these generating alternating torques cause that between the two Flywheel elements acting in the circumferential direction so far be pushed through until between the two flywheel elements also provided rigid stops to limit the rotation in Activity. In these states, the one between the two Damping device provided flywheel elements their function, näm prevent or dampen impacts no longer meet. When opening hitting the hard stops thus result in impermissibly high and un Audible shock loads that are both the comfort of one  reduce such a drive system equipped motor vehicle, including Components of the damping device and the shafts and bearings of the engine and endanger the coupled gear.

Furthermore, vehicles that are equipped with a facility of the beginning type are equipped, in many cases also in higher gears operated with engine speeds below idle speeds be so that it can happen because the drive system in the resonance reached rich and remains in this sufficiently long so that Reso vibrations of impermissibly high amplitude. In this The resonance range is that which occurs between the flywheel elements Alternating torques so large that they are between the flywheel elements effective stops or those interacting with these stops Components can damage or even shear, which reduces the damping direction is destroyed.

The object of the present invention was to provide such facilities conditions to improve, especially their damping effect, so that an opti Male filtering of the vibrations occurring between engine and transmission both at low and high speeds, at resonance speed, when starting or when parking or the like is achieved. Farther the device according to the invention should be particularly simple and cost-effective be inexpensive to manufacture.  

According to the invention, this is achieved in that between the swing wheel elements at least two torsionally elastic dampers acting in parallel are available, starting from a rest position or a means position range of the flywheel elements with a relative rotation of the same one of the dampers over a first angular range alone and the other the damper over an adjoining second angular range together with the first damper of a relative rotation of the flywheel counteracts elements and thereby to limit the relative rotation the springs of the second damper on the block between the flywheel elements go, that means that when using coil springs their Windun against each other.

Such a structure of the device makes it possible in the second win kelbereich effective force storage in such a way that this can absorb or intercept very high alternating torques, and also Avoid a hard stop when torque peaks occur can, because springs going on block in the last section, in the the turns are practically already together, but due to radial displacements can make a slight axial movement, a very high increase or a high progressiveness of the spring rate or Show spring identification. The one that takes effect in the second angular range Damper thus forms an impact damper with a very high impact torque, which be the relative rotation between the two flywheel elements borders.  

For the structure and function of the device, it can be advantageous when the second damper is provided radially within the first damper is. It can be useful if the torsional rigidity of the two th damper is larger than that of the first.

For the mode of operation and the construction of the device, it can further be advantageous if the second radially inner damper has an input part which can be rotated to a limited extent with respect to the input part of the first damper. The input part of the first damper can be formed by a flywheel element. Through such a configuration of the device, the receptacles provided in the input part and in the output part of the second damper, such as windows, for the energy accumulators of the second damper — viewed in the circumferential direction — can have the same extent.

A particularly simple structure of the device can be achieved by who the fact that both dampers have a common output part, which with the other flywheel element is connected.

To reduce wear and to better adjust the damping characteristics of the device to certain applications, it can be special be advantageous if the components of a flywheel element min at least form an annular space that is closed radially towards the outside at least partially with a viscous medium, e.g. Lubricant filled is, at least the radially further located damper in this  Annulus is added. The viscous medium between the Energy storage of the outer damper and the radially supporting it Areas of friction are reduced.

Although it may be beneficial for some applications if only the outer damper is accommodated in the annulus, it can be used by other users Application cases may be useful if both dampers pre-featured in this annulus are seen. For the sealing of the annular space, it can be advantageous if the output part common to the two dampers is from the inside extends radially into the annulus, so that between the two swing dynamic dynamic seals to be provided radially within the Levels of the viscous medium provided in the ring channel can be arranged can.

In a particularly simple manner, the output part of the two dampers are formed by two interconnected disc parts that Recesses for the energy storage of the first and second damper sen and the at least in the radial receiving area for the energy storage of the inner damper are axially spaced. In particular one This axial distance can be generated in a number of ways in that the two disc parts in the radial receiving area for the energy storage of the radially outer damper are potted or plate towards each other and lie against each other. With an output part configured in this way can advantageously between the axially spaced areas of the  Disc parts the input part of the radially inner damper featured be seen, which allows a compact design of the facility becomes.

Furthermore, it can be advantageous if one of the disc parts immediately bar is connected to the other flywheel element and the other this one part of the pane attached a larger inside has diameter than the one disc part and on the other Flywheel element side of the one disk part is provided is. The input part of the radially inner damper can be extend radially further inwards than the other disk part. Especially It can be advantageous if the radially inner regions of the one gear part of the radially inner damper stop to limit the Angle of rotation relative to the input part of the radially outer Damper. The counterstops interacting with these attacks can be provided on a flywheel element in a simple manner be. The counter-stops can by on a flywheel element fixed rivet elements are formed and the stops of the input part of the radially inner damper by on the inner circumference of this input part projections provided.

For the function of the device, it can be particularly advantageous if at least some of the energy absorbers of the inner damper in the circumferential direction tion without play in the window of the entrance part and exit part of this Damper are included. It can be useful for some applications be moderate if the energy damper of the inner damper between the input  part and output part of this damper are provided such that they Form stages, that means that at least two energy accumulators different twist angles come into effect. For other users application cases, however, it can be advantageous if the energy storage of the Use inner damper at least approximately at the same time or kompri be lubricated, resulting in a very steep increase in the torsional resistance that results. Such a sudden increase in the resistance to rotation between the two flywheel elements is especially in the endbe range of the possible relative torsion angle between the two swing wheel elements of advantage, as this causes the alternating torque peaks or Vibrations of very large amplitude can be intercepted resiliently.

This enables a particularly simple construction of the device be that the annulus encloses the radially outer damper ßender outer wall and radially from the latter inside and axially between them the output part of the damper receiving side walls is formed. It can in particular simple way one of the side walls of the annular space at least in essentially by a radial flange of a flywheel element be educated. The other of the side walls is advantageous axially between one side wall and the other Flywheel element arranged. The outer wall of the annulus can in simply by an annular, axially extending from one wall extending approach be formed, which is also in one piece with this  can be a wall. The other of the side walls can pass through be a disk-like component formed on the axial approach of one Flywheel element is attached.

The at least one damper can be accommodated in a particularly simple manner Annulus are formed by two shell-like housing halves. Here it can be advantageous for some applications if the housing half are formed by castings, for other applications it can however, also be useful if at least one of the housing halves through a sheet metal part is formed.

It can be particularly advantageous if the annular space is separated by two half-shells len-like sheet metal parts is formed, these components of the can be connected to the engine flywheel element. Such an advantage sheet metal parts compared to parts produced by machining consists in the substantially reduced manufacturing effort.

For the function of the device, it can also be advantageous if the lateral walls have axial indentations for receiving at least the Have energy storage of the outer damper and the indentations at least least in the radially outer area to the circumference of the cross section of the force memory are aligned. Such a configuration of the device enables a perfect guidance of the in the indentations Menen springs, so that these springs are made relatively long can and therefore a large angle of twist between the two flywheels elements. It can be particularly advantageous if the  Indentations limit a torus or ring-like space in which force memory like coil springs, which are at least under Centrifugal force on the surfaces delimiting the indentations radially support.

A particularly simple sealing of the annular space to the outside can can be achieved in that axially between the other wall and the a disc directly connected to the other flywheel element part of a plate spring-like component is arranged between this Wall and the disc part is axially resiliently clamped. Can be advantageous be there when the plate spring-like component with the other swing wheel element is non-rotatable and with radially outer areas on the other Seals against the wall.

To reduce or prevent abrasion wear on the one Areas delimiting bays can at least in the areas on which the Kraftpseicher are supported under centrifugal force, one have greater hardness. This can increase hardness at least in places by induction hardening, case hardening, laser beam hardening or flame hardening be generated.

To reduce wear, however , the parts that delimit the indentations can also have a coating that reduces wear and tear - at least in the contact areas between the energy stores and the surfaces of the indentations. Metallic coatings such as hard nickel coating, chrome coating or molybdenum coating are advantageously suitable as a wear protection layer. For some applications, however, it can be advantageous if a ceramic or plastic coating, for example glass fiber coating, is applied.

Another possibility of abrasion wear on the indentations To reduce limiting parts is that at least between the parts on which the individual turns of the springs are under fleeing support force, and the springs by an intermediate layer formed wear protection is provided. Such wear protection can be formed in a simple manner that between the springs and the components delimiting the indentations, at least radially outer area, an insert in the form of at least one hardened Steel strip is inserted. It can be particularly advantageous if the Insert through between the indentations and the energy stores Hene shells is formed, which is arched in cross-section and at least are approximated to the spring outer diameter. This allows the springs are supported over a larger circumferential area, so that the specific surface pressure and thus also minimizes frictional wear becomes.

It can be particularly advantageous if the indentations are annular are, that means are continuous over the scope of the facility and the support areas in the circumferential direction for the energy storage through in Indentations attached circumferential stops are formed. This scope blows can be formed by individual elements such as rivets,  which are connected to the parts forming the indentations. These Individual elements can be welded, riveted or pressed into corresponding recordings associated with the components assigned to them be.

To ensure that the lift mechanism is properly loaded, it can be particularly advantageous if the application areas of the Circumferential stops or individual elements for the energy accumulator or are flattened. To increase the life of the device, the order catch stops at least in the application areas for the force storage have a high hardness, or with a wear-resistant Be layering.

For the function of the device, it can be advantageous if the one gear part of the radially inner damper on the common output part of the Damper is centered. The central mounting of the output part can take place via the energy accumulator of the inner damper.

They limit the annular space, which is at least partially filled with viscous medium Zenden housing halves can advantageously by a them in Fastening strap encompassing the circumferential direction is connected axially to one another will. Such a fastening tape can be designed as a sheet metal cage be, this cage axially over areas of the two housing halves engages and flanks radially inwards from these areas can be. For exact positioning of the two housing halves during  pins, e.g. Heavy duty pins are used e.g. in corresponding holes in the two housing halves are.

In the previous facilities of the type mentioned is still a relatively low torsional load between the flywheel elements relative rotation possible, which is why at least over a large range this relative rotation is the damping rate between the flywheel effective damping elements is relatively high. For many Use cases, however, would be advantageous to better damping the Achieve vibrations when large relative rotations between the Flywheel elements would be present, because then the damping rate between the flywheel elements over a large or even almost that total twist angle can be relatively low. The damping rate can get smaller the larger the possible twist angle is.

According to a development of the invention, therefore, the individual force store the outer damper at least over 45 degrees of the circumference extend. It can be particularly advantageous if the energy store of the outer damper extends over 80 to 115 degrees of the scope of the device extend.

To a large relative rotation between the two flywheel elements too enable, it may be appropriate if the outer damper is maximal has four, preferably three energy stores. As mentioned earlier, are  in the device according to the invention due to the perfect management use relatively long one-piece springs due to the indentations bar. The inventive design of the device can therefore Springs with low stiffness, but with large travel are set so that between the two flywheel elements of the Einrich low damping rate possible over a large angle of rotation is. Because of the possible large angle of rotation at the same time low damping rate, vibrations of large amplitude or large alternating torque peaks as well as vibrations with smaller ampli tude or smaller alternating torques are damped or filtered. Thus, practically in all operating conditions of the engine is a perfect Free damping of the vibrations that occur.

The radially inner damper with the high spring force save comes only after a relatively large angle of rotation between the two flywheel elements, preferably only in the end range of the possible angle of rotation between the flywheel elements Effect so that when vibrations of very high amplitude occur can be practically completely intercepted by the springs. Around to be able to absorb the peaks of the vibrations of very high amplitude, it can be particularly advantageous if in the effective range of the inner damper He also a high connected in parallel to the energy stores of this damper Friction hysteresis is present. This high friction hysteresis can are advantageously generated in that the input part of the inner damper axially between the two disc parts of the output part of the two dampers is clamped, so that with a relative rotation  friction damping between this input part and this output part is produced. It can be particularly advantageous for this if the one gear part of the inner damper resilient axially similar to a plate spring is. Furthermore, it can be advantageous if axially between this one gear part and the disc parts of the output part friction or sliding linings are interposed.

It is useful if the energy accumulator with a high spring rate of the inner Damper between the input part and the output part of this damper apply at least a sufficiently high moment to do that too friction torque generated between this input part and this output part overcome so that the input part in relation to the output part a defined starting position is pushed back.

The formation of the device according to the invention can result a resonance can be avoided as soon as the amplitude of the vibrations a certain amount exceeds the vibration peaks due to the high spring rate of the inner damper and the effective friction along with this damping are eradicated or consumed.

The invention will be explained in more detail with reference to FIGS. 1 to 6.

It shows:

Fig. 1 shows a section through an inventive device,

Fig. 2 shows a section along line II / II of FIG. 1,

Fig. 3 shows a further possible embodiment of a device according to the invention,

Fig. 4 shows a detail that may be 2 or 3 used in a device according to FIGS. 1 and,

Fig. 5 shows another possible embodiment of a device according to the invention,

Fig. 6 shows a section according to line VI-VI of Fig. 5.

The Drehmomentübertragungseinrich shown in Figs. 1 and 2, device 1 for compensating for rotational shocks has a flywheel 2, which is divided into two flywheel elements 3 and 4. The flywheel element 3 is attached to a crankshaft 5 of an internal combustion engine, not shown, via fastening screws 6 . A switchable friction clutch 7 is attached to the flywheel element 4 . Between the pressure plate 8 of the friction clutch 7 and the flywheel element 4 , a clutch disc 9 is provided, which is received on the input shaft 10 of a transmission, not shown. The pressure plate 8 of the friction clutch 7 is struck in the direction of the flywheel element 4 by a plate spring 12 which is pivotally supported on the clutch cover 11 . By actuating the friction clutch 7 , the flywheel element 4 and thus also the flywheel 2 or the internal combustion engine of the transmission input shaft 10 can be engaged and disengaged. Between the flywheel element 3 and the flywheel element 4 , a first, radially outer damper 13 and a second, radially inner damper 14 connected in parallel therewith are provided, which enable a relative rotation between the two flywheel elements 3 and 4 .

The two flywheel elements 3 and 4 are mounted relative to one another via a bearing 15 . The bearing 15 comprises a roller bearing in the form of a single-row ball bearing 16 . The outer bearing ring 17 of the Wälzla gers 16 is in a recess 18 of the flywheel element 4 and the inner bearing ring 19 of the roller bearing 16 is on a central, axially extending from the crankshaft 5 away and into the recess 18 inra ing cylindrical pin 20 the flywheel element 3 arranged. The pin 20 is integrally formed on the engine-side component 3 a of the flywheel element 3 .

The inner bearing ring 19 is taken up by means of a press fit on the pin 20 and clamped between a shoulder 21 of the pin 20 or the component 3 a and a locking washer 22 which is fixed on the end face of the pin 20 .

The bearing 16 is axially secured against the flywheel element 4 by being axially clamped with the interposition of two rings 23 , 24 of L-shaped cross section between a shoulder 25 of the flywheel element 4 and a disk 27 which is firmly connected to the second flywheel element via rivets 26 .

The two rings 23 , 24 form a thermal insulation that interrupts the heat flow from the interacting with the clutch disc 9 friction surface 4 a of the flywheel element 4 to the bearing 16 or at least vermin changed.

The component 3 a of the flywheel element 3 carries an axially annular extension 28 radially on the outside, which delimits an annular space 29 .

The annular space 29 is delimited radially on the outside by the axial extension 28 and since by the radially inwardly extending from this and between them the damper 13 , 14 receiving walls 31 and 32 . The side wall 31 is formed by the radial flange 33 of the component 3 a , which extends from the pin 20 . The side wall 32 is formed by an essentially inelastic or rigid, disk-shaped cover 32 which extends radially inwards between the radial flange 33 and the flywheel element 4 and radially on the outside of the component 3 a or on the end face of the extension 28 is attached by means of rivets 34 .

The two dampers 13 , 14 have a common output part 35 which is non-rotatable with the flywheel element 4 . The output part 35 is formed by the disk 27 , which is attached to the end face of an axial extension 36 of the flywheel element 4 pointing in the direction of the crankshaft 5 , and a disk 37 attached to this disk 27 . As can be seen from Fig. 1, the disc 27 is axially at its radially outer region axially in the direction of the flange 33 of the component 3 a and the disc 37 is riveted 38 to the outer, axially offset Be rich 37 a of the disc 27 attached .

The plate 27 forms an axial space 39 between it and the disk 37 connected to it, in which a disk-shaped component 40 is accommodated, which forms the input part for the radially inner damper 14 . The disks 27 and 37 and the disk-shaped component 40 have in the axial direction aligned Ausneh measures 41 , 42 , 43 , which may be window-shaped and in which the energy accumulator in the form of coil springs 44 of the inner damper 14 are received. In the illustrated embodiment, the windows 41 , 42 , 43 - viewed in the circumferential direction or in the tangential direction - are of equal length and the coil springs 44 are installed with prestress in these windows, so that a certain moment between the input part 40 and the output part 35 of the inner damper 14 can be transmitted before the coil springs 40 begin to be compressed.

The disk 37 of the common output part 35 facing the flange 33 of the flywheel element 3 has a larger inner diameter 45 than the disk 27 , which serves to fix the bearing 16 relative to the flywheel element 4 . As can be seen in connection with FIG. 2, the input part 40 for the damper 14 has on its inner circumference radially inwardly extending arm 46 , between which - viewed in the circumferential direction - stops 47 are provided which are attached to the flange 33 of the component 3 a are. The stops 47 are formed by rivet bolts which have an axially projecting into the annular chamber 29 pin region 47 a . By placing the arms 46 against the stops 47 , the relative rotation between the input part 40 of the damper 14 and the flywheel element 3 is limited.

As can also be seen from FIG. 2, an angle of rotation 49 is possible between the input part 40 for the damper 14 and the flywheel element 3 or the pin regions 47 a in the pulling direction 48 and an angle of rotation 51 in the pushing direction 50 . In the illustrated embodiment, the twist angles 49 and 51 are the same. The stops 47 could, however, be arranged asymmetrically with respect to two cantilevers 46 adjacent in the circumferential direction, so that the possible angles of rotation in the pulling direction and pushing direction would be of different sizes. For example, in the pulling direction 48, the possible angle of rotation between the flywheel element 3 and the input part 40 could be greater than the possible angle of rotation between these parts in the direction of thrust 50 .

As can also be seen from the figures, the radially outer, axially offset portions 37 are formed of a disk 27 by means of radial arm 37a that are bent in the axial direction at the inner region. The disc 37 also has molded on the outer circumference of radial arms 52 which rest axially on the arms 37 a and are connected to them via the rivets 38 . The radial arms 37 a and 52 have the same extent in the circumferential direction, so that they form with their side surfaces acting areas 53 , 54 for the springs 55 of the outer damper 13 .

At the radial height of the springs 44 of the inner damper 14 , the two disks 27 and 37 are connected to one another via spacer bolts 56 . The spacer bolts 56 are riveted to the two disks 27 , 37 and they extend axially through elongated recesses 57 of the disk-shaped component 40 in the circumferential direction. The elongated recesses 47 are dimensioned such that the springs 44 of the inner damper 13 go into block, that is to say that the individual turns of this spring 44 come into contact with one another without the spacer bolts 56 being able to strike the end regions of the elongated recesses 57 . As a result, a too hard stop is avoided when high torque shocks occur, since springs in the last section, where the windings are practically adjacent to one another but can still make a small axial movement due to radial displacements, cause the spring to be very progressive have rate.

As can be seen from Fig. 2, the spacer bolts 56 are arranged radially inner half of the boom 37 a and 52 . Radially inside the arms 37 a and 52 or radially inside the elongated recesses 57 , cutouts 58 are made in the disk-shaped component 40 and are laterally delimited by arms 46 . The cutouts 58 make it possible to rivet the rivets 26 which , viewed in the axial direction (see FIG. 2), are arranged in their area.

The input part 40 of the inner damper 14 is clamped axially between the two disks 27 and 37 , which form the common output part 35 for both dampers 13 , 14 . For this purpose, the disc-shaped component 40 is formed like a plate spring, so that it is resilient in the axial direction. When removed, the disc-shaped member 40 has - similar to a diaphragm spring - a certain conicity. When installing the schei ben-shaped component 40 between the two disks 27 , 37 this is clamped in the axial direction such that the friction linings 59 axially between the radially outer regions of the component 40 and the disc 37 and the friction linings 60 axially between the radially inner regions of the component 40 and the disc 27 are clamped. To simplify assembly, the friction linings 59 , which are radially outside of the springs 44 and the Reibbe 60 , which are arranged radially inside the springs 44 , are glued to the disc-shaped component 40 . When the disc-shaped component 40 rotates relative to the output part 35 , the friction linings 59 , 60 generate on the discs 37 , 27 a friction damping which is connected in parallel with the spring action of the springs 44 .

For accommodating the springs 55 of the outer damper 13 have the component 3 a and the wall 31 and the disk-shaped cover 32 axial recesses 61, 62 into which the both sides of the output part 35 projecting regions of the energy accumulator 55 at least partially chen immerse.

1 as can be seen from Fig. , The axial indentations 61 , 62 are formed in cross section such that their arcuate course is at least in the radially outer region to the circumference of the cross section of the Kraftspei 55 aligned. The outer regions of the indentations 61 , 62 can thus form the bearing region or guide regions for the force accumulator 55 , on which the force accumulator 55 can be supported radially, at least under the influence of centrifugal force. By aligning the contact areas formed by the indentations 61 , 62 to the outer circumference of the force accumulator 55 , the wear that occurs due to the friction of the windings of the force accumulator 55 on the radially outer regions of the indentations 61 , 62 can be significantly reduced, since the support surface between springs 55 and indentations 61 , 62 is enlarged. Viewed in the circumferential direction, the indentations 61 , 62 are ring-shaped, which means that they extend over the entire circumference. This is advantageous since, for example, the pre-cast indentations 61 , 62 can then be machined by a turning operation. To act upon the energy accumulator 55 , circumferential stops 63 , 64 are introduced into the indentations 61 , 62 , which form support regions for the energy accumulator 55 in the circumferential direction. The circumferential strokes 63 , 64 have - viewed in the circumferential direction - the same angular extent as the boom 38 , 52 of the output part 35th The peripheral stops 63 , 64 are formed by the bulges 61 , 62 adapted components which are riveted to the flywheel component 3 a or the disk-shaped cover 32 . The end regions of the circumferential stops 63 , 64 viewed in the circumferential direction are flattened for better loading of the force accumulator 55 .

As can be seen from FIG. 2, three springs 55 are provided over the circumference of the device 1 , each of which extends at least approximately over 110 degrees. In the unmounted state, the springs 55 - viewed in the axial direction - can be straight, which means that during assembly the springs 55 must be bent according to the shape of the bulge 61 , 62 , or the springs 55 can also be accordingly The shape of the bulges 61 , 62 already have a corresponding curvature.

The springs 55 of the outer damper and the springs 44 of the inner damper are matched to one another in such a way that at full angular deflection between the two flywheel elements 3 and 4 the final torque or maximum torque which is applied by the outer springs 55 is less than the corresponding one Moment generated by the inner damper springs 44 . Furthermore, the springs 44 have a higher spring rate than the springs 55 .

To seal the annular chamber 29 from the outside, a sealing ring 65 is provided, which is arranged radially inside the rivet 34 between the axial extension of the component 3 a and the side wall 32 . In the illustrated embodiment, the sealing ring 65 is formed by an O-ring. A further seal 66 is provided between the radially inner region of the side wall 32 and the disk 27 or the axial extension 36 of the flywheel element 4 . The seal 66 is formed by an annular part which has a radially inner, flat, disc-shaped region which is clamped between the end face of the axial extension 36 of the flywheel element 4 and the disc 27 , and an outer, frustoconical region which acts in the manner of a plate spring has, which is supported with prestress on radially inner regions of the side wall 32 . To support the resilient area of the seal 66 , an axial recess or an axial shoulder 67 is formed in the inner area of the side wall 32 , the radially outer lateral surface of which axially engages over the outer areas of the seal 66 .

In the annular chamber 29 , a viscous medium or a lubricant is easily seen. The level of the lubricant can - at least up to the middle region or the axis of the outer springs 55 of the damper 13 - range with rotating device 1 .

By assigning the annular chamber 29 , which contains a viscous medium or a lubricant, to the flywheel element 3 connected to the engine and also by the spatial separation from which the friction clutch 7 carrying flywheel element 4 becomes an influence of the context of Friction clutch heat generated on the hydraulic damping device largely turned off.

Furthermore, between the annular chamber 29 or the side wall 32 on the one hand and the flywheel element 4 on the other hand, an outwardly open annular gap 68 is provided, which further improves the cooling effect in connection with ventilation channels 69 . The ventilation channels 69 are provided radially within the friction surface 4 a of the flywheel element 4 for the clutch disc 9 .

A pasty agent such as fat or a liquid agent such as oil or the like can be used as the viscous medium for the annular chamber 29 . By using such a viscous medium, the wear in the contact area between the windings of the energy accumulator 55 and the bulges 61 , 62 is further reduced.

To reduce this wear of the recesses can continue, at least in the contact areas between the energy accumulators 55 and the surfaces of the indentations 61, 62 bounding parts 3 a, 32 have a greater hardness. This can be done, for example, by induction hardening, case hardening, laser beam hardening or flame hardening at least these contact areas. In the case of very high loads, however, it can also be expedient if the parts 3 a , 32 delimiting the indentations have a coating which reduces wear and tear, at least in the abovementioned contact areas. Such a coating can be formed, for example, by chemical nickel plating, by chrome plating or by coating with plastic or molybdenum. The applied coating can further be smoothed afterwards in order to obtain a better surface quality of the indentations against which the turns of the springs 55 rub. Such smoothing can be done, for example, by a grinding process or turning.

The mode of operation of the device 1 is now described below:

When the two flywheel elements 3 and 4 are rotated from the rest position shown in FIG. 2, for example in the direction of thrust 50 , the springs 55 are first compressed. After driving through the relative Ver rotation angle 49 between the two flywheel elements 3 and 4 , the radial arm 46 of the input part 40 of the inner damper 14 comes to rest against the stops 47 , so that in the event of a further relative rotation between the two flywheel elements 3 , 4 in addition to the springs 55 the springs 44 of the inner damper 14 are compressed. The compression of the springs 55 and the springs 44 takes place until the springs 44 go into block, as a result of which the relative rotation between the two flywheel elements 3 and 4 is limited. In the illustrated embodiment, the angle of rotation 49 is of the order of 32 degrees and the block angle of the springs 44 can be of the order of 4 degrees, so that a total angle of rotation of 36 degrees between the two flywheel elements 3 and 4 is possible. In the torsion angle range in which the springs 44 are effective, additional friction damping is generated by the friction linings 59 , 60 . In the angle of rotation region 49 , frictional damping is generated by friction of the springs 55 on the indentations 61 , 62 and by friction of the axially resiliently preloaded outer region of the component 66 on the side wall 32 . Furthermore, damping is generated by swirling the viscous medium contained in the annular chamber 29 .

In the embodiment according to FIG. 3 of a device according to the invention, 32 shells 169 , 170 are provided in the indentations 161 , 162 of the flywheel component 3 a and the side wall 32 , which encompass the energy accumulator 55 .

The shells 169 , 170 can be formed by sheet metal parts, which can be hardened to increase wear resistance. However, the sheet metal parts 169 , 170 can also have a coating, such as a hard nickel coating. Furthermore, the shells 169 , 170 , which support the force accumulator 55 in the radial direction, can be made from a wear-resistant plastic. In the illustrated embodiment, the bulges 161 , 162 are adapted to the contour of the shells 169 , 170 . The indentations 161 , 162 could, however, also be designed in such a way that they only support the shells 169 , 170 in places, which therefore means that there may be free spaces in places between the bulges 161 , 162 and the shells 169 , 170 . Instead of two shells 169 , 170 , only a single shell can be used, which extends at least over a partial area of the outer half of the circumference of a spring 55 .

The use of shells 169 , 170 for supporting or guiding the springs 55 has the further advantage that the shells 169 , 170 can be renewed if the device 1 is repaired, if necessary. There are so massive castings 3a and 32 are not damaged by the springs 55th

The detail according to FIG. 4 of a further embodiment shows a further possibility for connecting the flywheel component 3 a to the side wall 32 . To connect these two parts 3 a and 32 , a sheet metal cage 271 is used, which extends over the circumference of the device. The sheet-metal cage 271 engages axially radial regions 272 of the flywheel component 3 a and 273 of the lateral wall 32 and is at the free Endbe range of the abutting radial portions 272, 273 radially flanged to the inside, whereby the flywheel component 3 a and the lateral Wan dung 32 are axially connected. To prevent rotation of the union since wall 32 relative to the flywheel member 3 a 273 axial alignment pins 274 can be introduced into the radia len areas 272. To axially secure the dowel pins, the flanged edges 271 a , 271 b of the sheet metal cage at least partially overlap the dowel pins 274 radially.

The embodiment of a device 301 according to the invention partially shown in FIGS. 5 and 6 also has two flywheel elements 303 , 304 . The flywheel element 303 consists of two sheet metal parts 331 , 332 which delimit an annular space 329 . The two sheet metal parts 331 , 332 are centered over axially overlapping, annular surfaces 334, 335 . The sheet metal parts 331 , 332 are connected to one another by a weld 338 at the outer end regions of the centering surfaces 334 , 335 .

The sheet metal parts 331 , 332 have impressions 361 , 362 , which in the circumferential direction form areas similar to a circle, in which the springs 355 of the outer damper 313 are received. The impressions 361 , 362 are at least in the radially outer region to the circumference of the springs 355 is compared. In the illustrated embodiment, the impressions 361 , 362 encompass the springs 355 almost over the entire circumference, so that the springs 355 are properly guided by the sheet metal parts 331 , 332 .

When using sheet metal parts 331 , 332 , the circumferential stops provided on the sheet metal parts for the radially outer and / or the radially inner springs can advantageously be formed by impressions formed in the sheet metal parts 331 , 332 , such as pockets 363 , 364 according to FIG. 6 will. There are therefore no circumferences made of individual elements 63 , 64 according to FIG. 1 necessary.

The invention is not based on the illustrated and described Ausfüh tion examples limited, but also includes variants by combination nation of individuals in connection with the various embodiments described features or elements can be formed.

Claims (43)

1. Device for damping vibrations, especially in the drive train of a vehicle between the engine and transmission, with at least two rotatably mounted flywheel elements, between which damping means are provided and wherein a flywheel element can be connected to the engine and the other flywheel element via a Coupling, as a friction clutch can be connected to the transmission, characterized in that between the flywheel elements there are at least two rotationally elastic dampers acting in parallel, starting from a rest position or a central position region of the flywheel elements with a relative rotation of one of the dampers via a first Angle range alone and the other of the damper counteracts a relative rotation of the flywheel elements together with the first damper via a second angular range that adjoins it, and thereby to limit the relative movement between the sc hwungrad elements the springs of the second damper go on block. 2. Device according to claim 1, characterized in that the second Damper is provided radially within the first damper. 3. Device according to claim 1 or 2, characterized in that the Torsional stiffness of the second damper is greater than that of first damper. 4. Device according to one of claims 1 to 3, characterized in net that the second damper has an input part, the opposite the input part of the first damper can be rotated to a limited extent. 5. Device according to one of claims 1 to 4, characterized in net that the input part of the first damper by one Flywheel element is formed. 6. Device according to one of claims 1 to 5, characterized in net that both dampers have a common output part, wel ches is connected to the other flywheel element. 7. Device according to one of claims 1 to 6, characterized in net that the components of a flywheel element at least one form an annular space which is closed radially towards the outside, at least is partially filled with a viscous medium or lubricant and in which at least the damper located radially further out is opened is taken.   8. Device according to claim 7, characterized in that both Dampers are included in the annulus. 9. Device according to one of claims 1 to 8, characterized in net that the output part of the two dampers from the inside out extends radially into the annulus. 10. Device according to one of claims 1 to 9, characterized in net that the output part of the two dampers by two together connected disc parts is formed, the recesses for the Have energy storage of the first and second damper and the at least in the radial receiving area for the energy storage of the inner damper are axially spaced. 11. The device according to claim 10, characterized in that the two Disk parts in the radial receiving area for the energy storage of the radially outer damper potted towards each other are and lie against each other. 12. Device according to one of claims 10 or 11, characterized records that between the axially spaced areas of the Schei benteile pre-the input part of the radially inner damper see is.   13. Device according to one of claims 10 to 12, characterized in net that one of the disc parts directly with the other Flywheel element is connected and the other on this one Disk part attached disk part, a larger inner diameter it has one part of the disc and the other Flywheel element facing away from a disc part see is. 14. Device according to one of claims 10 to 13, characterized in net that the input part of the radially inner damper itself extends radially further inwards than the other disk part. 15. Device according to one of claims 1 to 14, characterized in net that the radially inner areas of the input part of the radial inner damper stop to limit the angle of rotation opposite the input part of the radially outer damper. 16. The device according to claim 15, characterized in that the counter stops on the one flywheel element are provided. 17. The device according to claim 16, characterized in that the counter stops by rivets attached to one flywheel element elements are formed and the stops of the input part of the radial inner damper by on the inner circumference of this input part seen projections.   18. Device according to one of claims 1 to 17, characterized in net that at least some of the energy storage of the inner damper in Circumferential direction without play in windows of the entrance part and from gear part of this damper are included. 19. Device according to one of claims 1 to 18, characterized in net that the annulus by a the radially outer damper closing outer wall as well as from the latter radially inward and axially between them the exit part of the damper-receiving side walls is formed. 20. Device according to claim 19, characterized in that one of the lateral walls of the annulus at least essentially by a radial flange of a flywheel element is formed. 21. The device according to claim 19 or 20, characterized in that the other of the side walls axially between one side Lichen wall and the other flywheel element is arranged. 22. Device according to one of claims 19 to 21, characterized in net that the outer wall of the annulus by an annular, is axially formed by the extension extending a wall.   23. Device according to one of claims 19 to 22, characterized in net that the other of the side walls of the annulus through a disk-like component is formed, the axial approach of the a flywheel element is attached. 24. Device according to one of the preceding claims, characterized records that the annulus essentially by two housing halves ten, how bowl-like sheet metal body is formed. 25. Device according to one of claims 19 to 24, characterized in net that the lateral walls for receiving axial indentations have at least the energy accumulator of the outer damper and the Indentations at least in the radially outer area to the circumference of the Cross section of the energy accumulator are aligned. 26. The device according to claim 25, characterized in that the one Bays delimit a toroidal or ring-like space in which Energy storage are included, which are at least under centrifugal force Radial action on the surfaces delimiting the indentations support. 27. Device according to at least one of the preceding claims, characterized in that axially between the other wall and one directly connected to the other flywheel element Disk part is a plate spring-like component is provided, which Seals the annulus to the outside.   28. Device in particular according to one of claims 25 to 27, characterized characterized in that at least in the contact areas between the energy stores and the surfaces of the indentations that the Parts that delimit indentations have a greater hardness (e.g. through induction hardening, case hardening, laser beam hardening, flame hardening ten). 29. Device in particular according to one of claims 25 to 27, characterized characterized in that at least in the contact areas between the energy stores and the surfaces of the indentations that the Parts delimiting indentations reduce abrasion wear have an aging coating (such as chemical nickel plating, glass fa coating, chrome plating, molybdenum coating). 30. Device according to at least one of the preceding claims, characterized in that between the indentations and the Lift mechanism shells are provided. 31. Device according to one of claims 25 to 30, characterized in net that the indentations are ring-shaped, that means over the The circumference is continuous and the support areas in the circumferential direction for the energy storage by Um in the indentations catch stops are formed. 32. Device according to claim 30, characterized in that the order catch stops are formed by rivets.   33. Device according to claim 31, characterized in that the Beauf areas of impact of the rivets for the energy accumulator or are flattened. 34. Device according to at least one of the preceding claims, characterized in that the input part of the radially inner Damper on the output part common to both dampers is trated. 35. Device according to one of claims 19 to 33, characterized in net that the two side walls or housing halves of the a flywheel element are connected via a sheet metal cage, which areas of the one flywheel element axially overlap and is flanged radially inwards laterally from these areas. 36. Device according to one of claims 1 to 35, characterized in net that the individual energy storage of the outer damper itself extend at least over 45 degrees of the circumference. 37. Device according to one of claims 1 to 36, characterized in net that the energy storage of the outer damper is at least extend approximately 110 degrees around the perimeter of the facility. 38. Device according to one of claims 1 to 37, characterized records that the outer damper a maximum of four, preferably three Has energy storage.   39. Device according to one of claims 1 to 38, characterized in net that the input part of the inner damper axially between the braced two disc parts of the output part of the two dampers is. 40. Device according to claim 39, characterized in that the one gear part of the inner damper is axially resilient. 41. Device according to claim 39 or 40, characterized in that the input part of the inner damper is a cup spring-like component is. 42. Device according to one of claims 39 to 41, characterized in net that axially between the input part of the inner damper and the disc parts of the output part of the damper Reib- or Gleitbe would be provided. 43. Device according to at least one of the preceding claims, characterized in that the final torque of the inner damper is larger than that of the outside.