DE19817906A1 - Torsion oscillation dampener for vehicular clutch - Google Patents

Abstract

A torsion oscillation dampener has a primary mass (1) and a secondary mass (2). It further has a drag unit incorporating a pressure-exerting friction ring (3''), a pickup (4') and an elastic element. The elastic element has a rubber-like element (5) located within a hollow chamber (8). The friction ring can be applied to either the primary or secondary mass, while the pickup is linked to the other mass.

Description

The invention relates to a torsional vibration damper, in particular for Couplings, which consist of a primary mass and a secondary mass.

Such a torsional vibration damper is for example in EP 0718 518 A1 described, which consists of a primary mass and a secondary mass, between which an arrangement of tangentially effective spiral springs and Clamping body is attached such that primary mass and secondary mass with a torsional characteristic that can be determined by the spring arrangement up to one Maximum angle can be rotated. The clamping bodies consist of Cylinders and pistons that enclose a cavity that is connected to a cylindrical body made of elastoplastic material is filled, the Diameter smaller than the inner diameter of the cavity and such is dimensioned so that after the initial, small path of the piston Fills the cavity completely. Here, the springs and the clamping body serve as Internal damper to prevent torsional vibrations caused by a drive Reduce powertrain.

DE 41 28 868 A1 describes a torsional vibration damper for Couplings of a similar type, but in which the primary mass and Secondary mass are only connected by tangentially active coil springs. A friction ring is provided as the actual damping torque a certain angle of twist between primary mass and secondary mass Effect should come.  

However, these known systems have the disadvantage that they only part of the Work spectrum of a drive include, but in the rest of the load range are ineffective. The problem is that for the load range one transmitted torque and speed corresponding to high spring force and Damping are required while idling and low spring forces there must be virtually no damping in order to provide idle decoupling to reach. In the critical speed range, i.e. H. at speeds in the range of Natural frequency, but very high damping is required, otherwise significant increases in the rotational acceleration compared to the primary side occur. This speed range is especially important when starting the engine, but also go through in load change situations. In the event of a resonance dynamic moments occur that are multiples of the nominal torque.

It is an object of the present invention to provide a torsional vibration damper, especially for couplings, in which the Damping characteristics can be optionally adjusted.

As a solution, the invention proposes one of a primary mass and one Secondary mass existing torsional vibration damper with a Towing element in front, the at least one friction element with at least one Printing device, at least one driver and at least one elastic Element includes.

Here, the friction element either with the primary mass or with the Secondary mass frictionally connected and the driver with the other the aforementioned masses are connected to the drive.  

Advantageously, the printing device is arranged so that one on the Force acting force the friction between the friction element and either the primary mass or the secondary mass increased. As below is explained in more detail, the printing device by a friction ring or but by a correspondingly arranged with respect to a friction ring Spreader ring be formed, which is in operative connection with the elastic element stand that one of the elastic element on the printing device, that is the friction ring rim or the expansion ring, the force exerted is the friction of the Friction elements with the primary mass or the secondary mass increased. To this The friction caused by the friction element changes from that to the elastic one Element applied force and thus from the angle of rotation between Primary and secondary mass dependent.

Due to the arrangement according to the invention, the Damping characteristics, especially suitable for large forces Customize way.

The elastic element advantageously has a cavity arranged rubber-like element. This allows the Damping characteristic of the torsional vibration damper according to the invention advantageous for both large and small forces or twist angles influence. This is the case with low forces or angles of rotation rubber-like element similar to an elastic spring. Will that be rubbery Element continues to compress until it fills the cavity, this is how it works elastic element consisting of cavity and rubber-like element, as if it included a hydraulic fluid. In this condition  meet the elastic element much higher forces than when known torsional vibration dampers.

Especially if the elastic element during a relative movement between Primary and secondary mass is compressed in the tangential direction, it is from Advantage if the rubber-like element in the tangential direction without play in the Cavity is arranged. This sets the resilient effect of rubbery element immediately.

A particularly simple and thus reliable construction follows in this case, if the cavity is delimited in the radial direction by the pressure device becomes. The tangential compression of the rubber-like element causes this radial or axial expansion. Thus, the rubber-like element can be radial the pressure device act and in this way the friction between Increase the friction element and either the primary or the secondary mass. It is too an axially acting pressure device is provided, so this is also applied accordingly with a force.

By constructing the volume ratio between the cavity and rubbery element and their geometries, the behavior of the Drag element depending on the angle of rotation between primary and Set secondary mass. In particular, it is also possible to use the rubbery one Element to be chosen so that the cavity is already in the relaxed state in some places also in the radial direction. With an axial compression of the rubber-like element are then immediate, even if only very much small, forces exerted on the radially arranged pressure device. In  Similarly, the rubber-like element can be configured axially to a to apply axially arranged pressure device with a selected force.

It goes without saying that the cavity does not have to be completely closed. It Rather, it is sufficient for the safe accommodation of the elastic element or the rubber-like element is provided or the rubber-like element sufficient to keep the cavity surrounding the cavity is so that the elastic member is not excessively pressed out of the cavity can be.

The force acting on the rubber-like element can by a Volume reduction of the cavity due to a relative rotary movement between primary and secondary mass. In particular, it is advantageous if this volume reduction takes place in the tangential direction, since a such movement of the relative movement between primary and secondary mass corresponds to and force-diverting measures can be dispensed with. In particular, axial forces between primary and secondary mass avoided.

Regardless of that, it can consist of a primary mass and a secondary mass existing torsional vibration damper comprise a towing element, the at least one friction element with at least one essentially tangential effective stop, at least one essentially tangentially effective Driver and at least one elastic element, which between the Stop and the driver is arranged tangentially effectively, wherein the friction element either with the primary mass or with the secondary mass  frictionally connected and the driver with the other of the aforementioned Mass is connected to the drive.

The tangentially effective arrangement of the elastic element between the Stopping the friction element and the driver enables it, even with the smallest Angle of rotation between the primary and secondary mass through the friction element mediated damping characteristics, i.e. the twisting characteristics, optimal adapt. In particular, those that occur during load changes in the idling range Noises from couplings caused by very small forces can be eliminated this way even more effective than the known couplings avoid.

The printing device can be designed such that it is radially effective. This has the advantage that those acting radially on the printing device Forces can be absorbed by the torsional vibration damper itself and so through this no axial forces on the other modules, such as Example of the clutch. This advantage can also be achieved through the Using a friction element with a friction surface that is radially outward has pointing surface component can be achieved.

To even with little or no load through the elastic element pressurized pressure device a minimum coefficient of friction between the friction element and to achieve primary or secondary mass, the friction element Include preload spring. Especially in the low load range thereby further increasing a customization option.  

It is understood that it is irrelevant in the aforementioned arrangements whether the carrier with the primary mass or with the secondary mass connected to the drive or whether the friction element by rubbing against the secondary mass or removes energy from the system by rubbing against the primary mass.

There is preferably one in each case in the tangential direction on both sides of the driver arranged elastic element, on which in turn a stop in each is arranged tangential direction, or vice versa. This allows the Advantages of the present invention regardless of the direction of rotation between Primary and secondary mass can be used.

In the case of a structurally simple configuration, the towing element is ring-shaped, designed as a drag ring. A driving ring can accordingly be provided be one that has one or more drivers. The driver or the Driving ring can have recesses in which on the primary mass or engage the cams provided on the secondary mass. This will in a drive connection between the driver or Driver ring and the corresponding mass guaranteed. It goes without saying that other connections between the carrier and the corresponding Mass, primary mass or secondary mass, can be provided to a Realize drive connection. In particular, the driver can or the driver ring can be provided with cams in the recesses intervene corresponding mass.

Especially if a towing ring is used as a towing element the use of a friction ring as a friction element advantageous. As before  Executed above, can be followed by a friction surface with a radial outside-facing surface component on the other assemblies, such as For example, reduce the axial forces acting on the clutch. Such For example, surfaces can essentially be created using a friction ring L-shaped cross section with a radially outer leg or through a friction ring with a substantially U-shaped, open in an axial direction Realize cross section. These friction rings should be in appropriate recesses, for example, a U-shaped groove, the corresponding mass rotatable be arranged.

When using a friction ring with an essentially L-shaped Cross section can be the surface to be machined in the appropriate mass be minimized and it is only necessary to be in contact with the friction surface edit the upcoming area of the mass accordingly, while the rest as Cast part can remain raw.

For a radial displacement of the radially arranged friction surfaces due to the to facilitate forces exerted on the pressure device can in the corresponding surface axial slots, or at least one axial slot, be provided.

In itself, the friction ring itself, for example if it is a U-shaped Has cross section to form the rubber-elastic element receiving cavity are used if this on its open side for example, is completed in a suitable manner by the driver ring. However, this places relatively high demands on the  Machining of the friction ring and is when using an L-shaped Friction rings are difficult to implement. The friction element can advantageously In addition to the friction ring, there is also an expansion ring that has at least one stop has and designed to be essentially U-shaped open in an axial direction is comprise, wherein this expansion ring from the driving ring to form the essentially closed cavity is covered. This spreading ring is arranged on the friction ring in such a way that during expansion or displacement of the expansion ring, the friction of the friction ring on the primary or secondary mass is increased. Such an expansion ring makes it particularly simple Way allows the use of an L-shaped friction ring.

When using an expansion ring, a Preload of the torsional vibration damper according to the invention reached be interrupted by the spreader ring at one point and into it Interruption, a tangential bias spring is used. Now this expansion ring placed in the corresponding friction ring, causes the tangential effective bias spring a radial expansion of the expansion ring, i.e. a radial Enlargement of the expansion ring diameter. This creates a preload achieved, which is particularly evenly distributed over the circumference of the friction ring.

The torsional vibration damper can have a further driver, the interacts with a stop from a certain angle of rotation. To this The characteristic of the towing element can be displayed with greater variability certain requirements are adapted. In particular, it is possible to Driver and the stop so that they essentially interact rigidly. With such an arrangement is from  certain angle of rotation then the drag element from the other driver entrained so that the elastic element is no longer compressed. At Such an arrangement is then the characteristic of the towing element from certain angle of rotation constant.

Depending on the requirements, the additional driver and the stop in the interact with each other essentially elastically. With such a Arrangement, it is advantageous if between the other driver and the Stop an elastic element is provided. In this way the Characteristic of the towing element from the certain angle of rotation by two elastic elements determined.

It is understood that the presence of an elastic element between a driver one of the masses and a stop one Towing element regardless of the other features of the Torsional vibration damper can be used advantageously. The same applies for the presence of another driver who only strikes with a stop interacts from a certain angle of rotation. By the latter arrangement can in particular also be ensured that the towing element suddenly from the certain angle of rotation with the driver and thus with one of the both masses is taken.

The present invention can be used in particular with torsional vibration dampers find advantageous application in which primary and secondary mass due the geometric design of the torsional vibration damper only around certain angles of rotation can be rotated against each other. Such  Geometric design can e.g. B. by meshing primary and secondary mass with certain play or by the presence of Wedges that prevent further turning after certain rotation angles have been realized be.

Further features, advantages and refinements of an inventive Torsional vibration dampers can be found in the description below and attached drawing. It shows,

Fig. 1 shows a first embodiment of a torsional vibration damper according to the invention in section along the line II of Fig. 2,

Fig. 2 shows the torsional vibration damper of FIG. 1 along the line II-II in section,

Fig. 3 is a sectional view of the torsional vibration damper of FIG. 1 along the line III-III in Fig. 1,

Fig. 4 is a sectional view of the torsional vibration damper of FIG. 1 along the line IV-IV in Fig. 1,

Fig. 5 shows a second embodiment of a torsional vibration damper according to the invention in a similar but fragmentary view similar to FIG. 1,

Fig. 6 shows a section through the torsional vibration damper of FIG. 5 taken along line VI-VI in Fig. 5,

Fig. 7 shows a detail of the torsional vibration damper of FIG. 5 taken along line VII-VII in Fig. 5,

Fig. 8 shows a detail of the torsional vibration damper of FIG. 5 taken along line VIII-VIII,

Fig. 9 exemplary damping characteristics of the torsional vibration damper according to Fig. 5 sketchy

Fig. 10 shows a second embodiment of a torsional vibration damper according to the invention in a similar representation as Fig. 1 and

FIG. 11 shows an exemplary damping characteristic of the torsional vibration damper according to FIG. 10.

A first embodiment of a torsional vibration according to the invention the damper comprises a primary mass 1 with a starter ring gear 11, and a secondary mass 2 which is rotatably connected by means of a bearing half-shell 14 and a firmly connected by tubular rivets 12 to the primary mass 1 central flange 13 in the tangential direction of the primary mass. 1 In the present description, "axially" means a direction perpendicular to the plane of the drawing in FIG. 1, "radially" away from the axis of rotation of the torsional vibration damper or a direction pointing to the axis of rotation of the torsional vibration damper and "tangential" means both perpendicular to a radial and to each axial direction.

The torsional vibration damper further comprises a transmitter plate 15 and several compression springs 10 , known per se, arranged between wedges, of which only one is numbered as an example.

In the secondary mass 2 there is an L-shaped friction ring 3 which is provided with axial slots 31 (numbered only by way of example) and comprises a friction ring edge 3 which is essentially axially aligned and abuts the secondary mass 2 in a frictional manner. The essentially radially oriented part of the L-shaped friction ring 3 also abuts the secondary mass 2 .

A spreading ring 30 with a U-shaped cross section is arranged in the friction ring 3 . This has stops 3 '.

Furthermore, the torsional vibration damper comprises a driver ring 4 which is connected to the primary mass 1 by cams 7 without play. This driver ring comprises three drivers 4 'which engage in the expansion ring 30 .

The expansion ring 30 and the driver ring 4 enclose cavities 8 , which are each delimited in the tangential direction by a driver 4 'or stop 3 '. The cavities 8 have an approximately square cross section.

In the cavities 8 ring-like rubber elements 5 are arranged, the diameter of which corresponds approximately to the side length of the aforementioned square. The length of the rubber elements 5 corresponds to the arc length of the cavities 8 .

Upon rotation of the primary mass of the secondary mass 1 2 relevant thus filling in the rubber elements 5 the square space, and then have a greater effect on the wall of the expansion ring 30th As a result, the expansion ring 30 is spread and the friction of the friction ring 3 with the secondary mass 2 is increased.

As long as the rubber element 5 has not completely filled the cavity 8 , it essentially acts like a spring. If the cavity 8 is completely filled by the rubber element 5 , the behavior of the rubber element 5 with a further rotation of the primary mass 1 with respect to the secondary mass 2 corresponds to the behavior of a hydraulic spring. As a result, the spring constant increases extremely in this case and the torsional vibration damper can absorb larger forces. In addition, the friction of the friction ring 3 with the secondary mass is increased in this case, so that the damping of the torsional vibration damper also increases.

It is understood that this characteristic behavior of the torsional vibration damper can be adapted to the desired requirements by a suitable choice of the shape of the cavity 8 and the shape of the rubber elements.

Because the rubber elements 5 correspond in length to the length of the cavities 8 , this torsional vibration damper responds in a suitable manner even at low loads, the rubber elements 5 acting approximately like elastic springs:

Due to the apparent in Fig. 1, symmetrical arrangement of the cavities 8 and the rubber elements 5 with respect to the stops 3 and the driver 4 is the behavior of this torsional vibration damper of the relative rotational direction of the primary mass and the secondary mass 1 2, independently of each other. It is understood that an unsymmetrical damping characteristic can also be achieved by a suitable choice of the rubber elements 5 or cavities 8 .

As can be seen from FIGS . 1 and 2, the expansion ring 30 is interrupted at one point and in this interruption a tangential biasing spring 6 is inserted. This requires a preload of the expansion ring 30 in the friction ring 3 , so that it has a defined frictional resistance to the secondary mass 2 . At low loads, this frictional resistance, together with the resilient behavior of the rubber elements 5, characterizes the characteristic of the torsional vibration damper. On the other hand, the damping characteristic at high loads is characterized by the hydraulic behavior of the compressed rubber elements 5 and the resulting, greatly increasing friction between the friction ring 3 and the secondary mass 2 .

The second exemplary embodiment represents a torsional vibration damper similar to the first exemplary embodiment. In this case, a friction ring 3 with a U-shaped cross section is inserted into a correspondingly shaped groove in the secondary mass 2 and the use of an expansion ring is dispensed with. The cavities 8 receiving the rubber elements 5 are formed directly by the friction ring 3 covered by a driving ring 4 . In this embodiment, both legs of the friction ring 3 are effective as a friction ring edge 3 ″ with a radial surface component and are provided with axial slots 31 .

In contrast to the first embodiment, both the entire groove in the secondary mass 2 as a contact surface for the friction ring 3 and the inside of the friction ring 3 as a contact surface for the rubber elements 5 have to be worked up in a complex manner. The rubber elements 5 are not round cord ring sections, but specially adapted molded rubber bodies are used. These have approximately the cross-section of the friction ring at their tangential ends and are provided in the middle with a radially inner recess.

For prestressing the friction ring 3 in the groove of the secondary mass 2 , three radially effective prestressing springs 6 are used, which press the friction ring rim 3 locally outwards at three locations distributed over the circumference.

The operation of this embodiment corresponds to the operation of first embodiment. This works without play and without free travel and brings First small forces and damping in the idling range, which then constructively designed to grow to the desired maximum friction torque.

The twisting characteristics shown in FIG. 9 show different designs with different clamping (A: high, C: low) and different idling angles, ie different sizes of the radially inner recesses.

The third exemplary embodiment ( FIGS. 10 and 11) also essentially corresponds to the first exemplary embodiment. However, this third exemplary embodiment has a drag ring 30 which comprises four cavities 8 , in which drivers 4 'and 4 ''engage. The drivers 4 'correspond to the drivers of the first exemplary embodiment and there are rubber elements 5 on both sides of these drivers 4 ', which bear both on the drivers 4 'and on the stops 3 ' of the expansion ring 30 .

The drivers 4 ″, on the other hand, are larger than the drivers 4 ′. No rubber elements are provided on both sides of these catches 4 ″, and the catches 4 ′, at a certain angle of rotation, strike the stops 3 ″ of the expansion ring 30 directly. In this respect, the drivers 4 ″ interact essentially rigidly with the stops 3 ″ ″.

The drag ring 30 is designed with respect to the drivers 4 'and 4 ''in such a way that the drivers 4 ''strike the stops 3 ''' at an angle before the rubber elements 5 completely fill the cavities 8 . An exemplary twist characteristic curve that follows from such an arrangement is shown in FIG. 11. As can be seen from this figure, there is an abrupt transition at the selected specific angle of rotation, from which the expansion ring 30 is carried along by the drivers 4 ″.

It goes without saying that the twisting characteristic can be selected in a suitable manner by suitable coordination of the sizes of the drivers 4 'and 4 ''.

In particular, it is also possible to provide rubber elements between the driver 4 ″ and the stop 3 ″ ″ which do not completely fill the intermediate space.

Claims (26)

1. torsional vibration damper, especially for couplings,

• - Consisting of a primary mass ( 1 ) and a secondary mass ( 2 ), characterized by
• - A towing element which comprises at least one friction element with at least one pressure device ( 30 , 3 ''), at least one driver ( 4 ') and at least one elastic element.

2. Torsional vibration damper according to claim 1, characterized in that the elastic element has a rubber-like element ( 5 ) arranged in a cavity ( 8 ). 3. Torsional vibration damper according to claim 2, characterized in that the rubber-like element ( 5 ) is arranged in the tangential direction without play in the cavity ( 8 ). 4. Torsional vibration damper according to claim 2 or 3, characterized in that the cavity ( 8 ) is limited in the radial direction by the pressure device ( 30 , 3 ''). 5. Torsional vibration damper according to one of claims 2 to 4, characterized in that the volume of the cavity ( 8 ) is reduced with a relative rotary movement between the primary mass ( 1 ) and secondary mass ( 2 ). 6. Torsional vibration damper according to claim 5, characterized in that the volume reduction is essentially in the tangential direction he follows. 7. Torsional vibration damper according to one of claims 1 to 6, characterized in that the pressure device ( 30 , 3 '') is radially effective. 8. Torsional vibration damper according to one of claims 1 to 7, characterized in that the friction element comprises at least one biasing spring ( 6 ), which has a minimum friction coefficient between the friction element and the primary mass even when the pressure element ( 30 , 3 '') is not acted upon or is not acted upon by the elastic element ( 1 ) or secondary mass ( 2 ) conditional. 9. Torsional vibration damper according to one of claims 1 to 8, characterized in that in the tangential direction on both sides of the driver ( 4 ') each have an elastic element, on which in turn a stop ( 3 ') is arranged in the tangential direction. 10. Torsional vibration damper according to one of claims 1 to 9, characterized in that in the tangential direction on both sides of a stop ( 3 ') an elastic element is arranged, on which in turn a driver ( 4 ') is arranged in the tangential direction. 11. Torsional vibration damper according to one of claims 1 to 10, characterized in that the driver ( 4 ') has at least one recess into which a cam ( 7 ) of the primary mass ( 1 ) or the secondary mass ( 2 ) engages. 12. Torsional vibration damper according to one of claims 1 to 11, characterized in that the friction element comprises at least one friction ring ( 3 ). 13. Torsional vibration damper according to claim 12, characterized in that the friction ring ( 3 ) has a substantially L-shaped cross section with a radially outer leg, at least the radially outer surface of this leg serving as a friction surface (friction ring edge 3 ''). 14. Torsional vibration damper according to claim 13, characterized in that the friction ring ( 3 ) in a correspondingly shaped recess of the primary mass ( 1 ) or the secondary mass ( 2 ) is arranged rotatably rotatably. 15. Torsional vibration damper according to claim 12, characterized in that the friction ring ( 3 ) has a substantially U-shaped, open in an axial direction cross section and at least the radially outer surface of the friction ring ( 3 ) as a friction surface (friction ring edge 3 '') serves. 16. Torsional vibration damper according to claim 13 or 15, characterized in that the friction ring ( 3 ) in a substantially U-shaped groove of the primary mass ( 1 ) or the secondary mass ( 2 ) is arranged rotatably rotatably. 17. Torsional vibration damper according to one of claims 1 to 16, characterized in that the friction element has at least one friction surface (friction ring edge 3 '') with a radial surface component. 18. Torsional vibration damper according to one of claims 3, 15 and 17, characterized in that axial slots ( 31 ) are provided in the friction surface (friction ring edge 3 '') having a radial surface component. 19. Torsional vibration damper according to one of claims 1 to 18, characterized in that the towing element as a towing ring in is essentially annular. 20. Torsional vibration damper according to claim 19, characterized in that the drag ring comprises a driver ring ( 4 ) which has the driver ( 4 '). 21. Torsional vibration damper according to claim 19 or 20, characterized in that the friction element has a friction ring ( 3 ) and an expansion ring ( 30 ) which has at least one stop ( 3 ') and is essentially U-shaped, open in an axial direction includes

• - That the drag ring comprises a driver ring ( 4 ) with at least one driver ( 4 '),
• - That the driver ring ( 4 ) is arranged on the open side of the expansion ring ( 30 ), the driver ( 4 ') engages in the open side and thereby creates at least one substantially closed cavity ( 8 ) in which the elastic element is arranged , and
• - That the expansion ring ( 30 ) is arranged with respect to the friction ring ( 3 ) that in the case of axial and / or radial expansion or displacement of the expansion ring, the friction of the friction ring ( 3 ) with the primary mass ( 1 ) or with the secondary mass ( 2 ) is increased.

22. Torsional vibration damper according to claim 21, characterized in that the expansion ring ( 30 ) and the friction ring ( 3 ) are designed as an assembly. 23. Torsional vibration damper according to claim 21 or 22, characterized in that the expansion ring ( 30 ) is interrupted at at least one point and in this interruption a tangential biasing spring ( 6 ) is inserted. 24. Torsional vibration damper according to one of claims 1 to 23, characterized in that the towing element ( 30 ) comprises a further driver ( 4 '') which interacts with a stop ( 3 ''') from a certain angle of rotation. 25. Torsional vibration damper according to claim 24, characterized in that the driver ( 4 '') and the stop ( 3 ''') interact with each other essentially rigidly. 26. Torsional vibration damper according to claim 24, characterized in that the driver ( 4 '') and the stop ( 3 ''') interact with each other substantially elastically.