WO2008080484A1 - Torsional vibration damper arrangement - Google Patents

Abstract

A torsional vibration damper arrangement, especially for the drive train of a vehicle, comprises a primary side (12) and a secondary side (18) coupled to the primary side (12) via a damper fluid arrangement (16) to rotate about a rotational axis (A) and to rotate relative to each other. The damper fluid arrangement (16) comprises a first damper fluid of low compressibility, accommodated in a first damper fluid chamber arrangement (26), which transmits a torque between the primary side (12) and the secondary side (18), and a second damper fluid of higher compressibility, accommodated in a second damper fluid chamber arrangement (42), which is loaded when the pressure of the first damper fluid in the first damper fluid chamber arrangement (26) is increased. The second damper fluid chamber arrangement (42) comprises at least one chamber unit (44, 46) that is arranged radially outside and/or radially inside in relation to the first damper fluid chamber arrangement (26; 26a), a separating element (50, 52) being associated with every chamber unit (44, 46) and separating the first damper fluid from the second damper fluid and being displaced substantially towards the rotational axis (A) when the pressure in the chamber unit (44, 46) changes.

Description

 torsional vibration damper

(Description)

Technical area

The present invention relates to a torsional vibration damper arrangement, in particular for the drive train of a vehicle, comprising a primary side and a secondary side coupled via a damper fluid arrangement with the primary side for rotation about an axis of rotation and for relative rotation with respect to each other.

State of the art

From the subsequently published German patent application DE 10 2005 058 531 a torsional vibration damper arrangement is known in which the elasticity required for vibration damping is provided by a damper fluid arrangement comprising a substantially incompressible first damper fluid, ie a liquid, and a compressible second damper fluid, ie a gaseous medium , includes. The first, non-compressible damper fluid is arranged in pressure chambers, which change their volume during relative rotation between the primary side and the secondary side. When the volume is reduced, first damper fluid is displaced out of these pressure chambers into connection chambers arranged radially outside it. Each connecting chamber is separated by a separating piston displaceable in the circumferential direction from a compensation chamber located radially outside a respective pressure chamber and extending substantially in the circumferential direction, in which second damper fluid is arranged. When the first damper fluid is displaced from the pressure chamber, the separating piston is displaced by the volume fraction of the first pressure fluid which is increased in the connecting chamber, namely by compression of the second damper fluid.

Presentation of the invention

It is the object of the present invention to provide a Torsionsschwingungs- damper assembly, which with efficient space utilization a having improved vibration damping behavior.

According to a first aspect of the present invention, this object is achieved by a torsional vibration damper arrangement, in particular for the driveline of a vehicle, comprising a primary side and a secondary side coupled via a damper fluid arrangement with the primary side for rotation about a rotation axis and for relative rotation with respect to each other A damper fluid assembly comprising a first damper fluid having a lower compressibility in a first damper fluid chamber assembly and transmitting a second damper fluid having a higher compressibility in a second damper fluid chamber assembly loaded upon pressure increase of the first damper fluid in the first damper fluid chamber assembly, the second damper fluid chamber assembly comprising at least one damper fluid chamber assembly Chamber unit, with respect to the first damper fluid chamber arrangement ange¬ radially outside and / or radially inside rdnet, wherein in association with each chamber unit, a first damper fluid from the second damper fluid separating and displaceable in the chamber unit in the direction of the axis of rotation displaceable pressure change is provided.

Since the or each separating element according to the pressure ratios in the first damper fluid and the second damper fluid shifts in the axial direction according to the invention constructed torsional vibration damper, this movement or the displaceability of such a separator is not subject to further forces. In particular, circumferentially acting inertial forces, as they occur in torque fluctuations, and also acting in the radial direction centrifugal forces, such as occur in the rotary operation, have no effect on the position of the separating element. Thus, the vibration damping behavior is independent of the respective movement conditions of the rotating assemblies of the

Torsionsschwingungsdämpferanordnung be. In an advantageous embodiment, it is proposed that the at least one chamber unit of the second damper fluid chamber arrangement is arranged radially outside with respect to the first damper fluid chamber arrangement. By positioning the second damper fluid chamber arrangement radially outward there is thus a system area which, due to the provision of the volume for the compressible second damper fluid, which will generally be formed as gas, will have a comparatively low mass and thus a comparatively low mass moment of inertia.

In particular, it may be provided that the second damper fluid chamber arrangement comprises at least one chamber unit surrounding the first damper fluid chamber arrangement, wherein the separating element separating the first damper fluid from the second damper fluid of the at least one chamber unit is designed like a ring. By providing a ring-like chamber unit and a ring-like separating element associated therewith, the total number of components to be sealed with respect to each other is reduced, which simplifies the structure.

In an alternative embodiment, it is proposed that the at least one chamber unit of the second damper fluid chamber arrangement is arranged radially inward with respect to the first damper fluid chamber arrangement.

Even with such a configuration, the number of components fluid-tight with respect to each other can be minimized in that the second damper fluid chamber assembly has at least one concentric to the axis of rotation concentrically arranged chamber unit, said separating the first damper fluid from the second damper fluid separating element of the at least one chamber unit substantially circular disc-like is trained.

The torsional vibration damper arrangement according to the invention can be constructed, for example, such that the first damper fluid chamber arrangement at least one during relative rotation of the primary side with respect to the secondary side in a first relative rotational direction in volume reducible first pressure chamber, which communicates via a connecting chamber in operative connection with at least one of these associated chamber unit of the second damper fluid chamber arrangement. It is advantageous for providing a damping functionality both in the pulling direction and in the thrust direction if the first damper fluid chamber arrangement has at least one second pressure chamber which can be reduced in volume in a volume which can be reduced in volume relative to the secondary side relative to the secondary side in a second relative direction of rotation opposite the first relative direction of rotation, which second chamber is reducible via a connecting chamber An operative connection with at least one of these associated chamber unit of the second damper fluid chamber arrangement is.

The at least one first pressure chamber and / or the at least one second pressure chamber may be circumferentially extending so that generally the first damper fluid chamber assembly has an annular structure about the axis of rotation.

In order to provide one or more pressure chambers in a structurally simple embodiment, it is proposed that one side of the primary side and the secondary side comprises a first substantially cylindrical chamber housing and that the other side of the primary side and secondary side inserted into the first cylindrical chamber housing and with this an annular space limiting second cylindrical chamber housing, wherein on the first chamber housing at least one on the second chamber housing to be extended erstrecksbegrenzungsvorsprung is provided and on the second chamber housing at least one to the first chamber housing to be extended second circumferential limiting projection is provided and wherein between each of a first peripheral limiting projection and a second circumferential boundary projection is a pressure chamber in the circumferential direction is limited and the volume of the pressure chamber by relative circumferential movement of the limiting this limiting boundary is changeable. In order to be able to use the volume of the chamber units of the second damper fluid chamber arrangement that are effective in different load states, that is to say draw states and thrust states, it is proposed that at least one chamber unit of the second damper fluid chamber arrangement assigned to a first pressure chamber of the first damper fluid chamber arrangement be in pressure compensation connection with at least one further chamber unit of the second damper fluid chamber arrangement which is associated with a second pressure chamber of the first damper fluid chamber arrangement. This means that in each case a larger volume of gas is compressed by the combination of the volumes of a plurality of chamber units, so that in general a softer coupling of the primary side and the secondary side can be achieved.

This can be realized, for example, in that two chamber units of the second damper fluid chamber arrangement are arranged consecutively in a common housing area in the direction of the axis of rotation, wherein the separating elements of the two chamber units are arranged axially successively in the housing area and displaceable in the direction of the axis of rotation, and wherein the second Damper fluid is disposed in the housing portion between the two separating elements.

According to a further aspect, the object mentioned is achieved by a torsional vibration damper arrangement, in particular for the drive train of a vehicle, comprising a primary side and via a damper fluid arrangement with the primary side for rotation about a rotation axis and for relative rotation with respect to each other coupled secondary side, wherein the damper fluid arrangement a Torque between the primary side and the secondary side comprises first damper fluid having lower compressibility in a first damper fluid chamber assembly and comprises a second damper fluid with higher compressibility in a second damper fluid chamber assembly loaded upon pressure increase of the first damper fluid in the first damper fluid chamber assembly, wherein the second Damper fluid chamber assembly comprises a plurality of chamber units, wherein in association with each chamber unit a first damper fluid from the second damper fluid separating and displaceable in pressure change in the chamber unit separating element is provided, wherein at least two chamber units of the second damper fluid chamber assembly, a composite chamber unit with a common volume for the form second damper fluid and the second damper fluid of each composite chamber unit is compressible by each separator of the chamber units of this composite chamber unit.

By combining the volumes of a plurality of chamber units to a total volume of a respective combined chamber unit having these chamber units, a larger gas volume can then be utilized in different load states.

In order to be able to use this increased volume in both tensile load and thrust load, it is proposed that the first damper fluid chamber arrangement has at least one first pressure chamber which can be reduced in volume relative to the secondary side relative to the secondary side in a first relative direction of rotation, which is operatively connected via a connection chamber with at least one of these associated chamber unit of a composite chamber unit of the second

Dämpferfluidkammeranordnung is, and at least one in relative rotation of the primary side relative to the secondary side in a first relative direction opposite second relative rotational direction reducible in its volume second pressure chamber, which communicates via a connecting chamber in operative connection with at least one of these associated chamber unit of the same composite chamber unit of the second damper fluid chamber assembly ,

The at least one first pressure chamber and / or the at least one second pressure chamber may be designed to extend in the circumferential direction, so that here too a substantially annular structure of the first Damper fluid chamber arrangement is obtained.

Furthermore, it may be provided that one side of the primary side and the secondary side comprises a first substantially cylindrical chamber housing and that the other side of the primary side and secondary side comprises a second cylindrical chamber housing inserted into the first cylindrical chamber housing and defining an annular space therewith Chamber housing is provided at least one to the second chamber housing to be extended Erstumfangsbegrenzungsvorsprung and on the second chamber housing at least one extending on the first chamber housing second circumferential limiting projection and wherein between each of a first peripheral boundary projection and a second peripheral limiting projection a pressure chamber is limited in the circumferential direction and the volume of the pressure chamber is variable by relative circumferential movement of these limiting peripheral boundary projections.

In at least one of the chamber units of the second damper fluid chamber arrangement, the separating element can be displaced substantially in the direction of the axis of rotation, so that, as stated above, neither centrifugal forces nor circumferentially acting mass inertia forces can influence the positioning of such a separating element.

Alternatively, it is possible for such a separating element to be displaceable substantially in the circumferential direction with respect to the axis of rotation or else to be displaced substantially radially with respect to the axis of rotation.

In a particularly advantageous embodiment, the separating element may be formed as a separating piston. In principle, it would also be conceivable to use a separating membrane which is fixed in its peripheral region and can then move with its central region in the particular intended direction. In order to be able to influence the damping behavior, it can further be provided that the first damper fluid chamber arrangement is in connection with a source or / and a reservoir for the first damper fluid via a rotary feedthrough or can be brought.

Brief description of the drawings

The present invention will be described below in detail with reference to the accompanying drawings. It shows:

Fig. 1 is a longitudinal sectional view of a Torsionsschwingungsdämpferanordnung;

FIG. 2 is a partial cross-sectional view of the torsional vibration damper assembly shown in FIG. 1; FIG.

FIG. 3 is a view corresponding to FIG. 1 of an alternative torsional vibration damper arrangement; FIG.

FIG. 4 is a partial cross-sectional view of the torsional vibration damper assembly shown in FIG. 3; FIG.

5 shows a further longitudinal sectional view of an alternative constructed torsional vibration damper assembly;

FIG. 6 is a cross-sectional view of the torsional vibration damper assembly shown in FIG. 5; FIG.

FIG. 7 is a view corresponding to FIG. 5 of an alternative torsional vibration damper arrangement; FIG.

FIG. 8 is a cross-sectional view of the torsional vibration damper assembly shown in FIG. 7. FIG. Best way to carry out the invention

In Fig. 1, a torsional vibration damper assembly is generally designated 10. This torsional vibration damper arrangement 10 described in detail below comprises a primary side 12, which is to be fixed, for example, in its radially inner region with a plurality of threaded bolts 14 on a drive shaft, for example a crankshaft of an internal combustion engine. A secondary side 18, which is coupled to the primary side 12 by means of a damper fluid arrangement 16 for transmitting torque, is coupled on the output side to a friction clutch 20, which may be of conventional design. It will be understood that the portion of a driveline of a vehicle following the torsional vibration damper assembly 10 may be implemented in a variety of ways and may include, for example, an electric machine, a hydrodynamic torque converter, a fluid coupling, or the like.

The primary side 12 comprises a first substantially ring-like chamber housing 22, in which a second substantially ring-like chamber housing 24 of the secondary side 18 is positioned radially inwardly. As can also be seen in FIG. 2, the two chamber housings 22, 24 form a first damper fluid chamber arrangement, generally designated 26. In a circumferential direction, these pressure chambers 30, 32 bounded by respective peripheral boundary projections 34 on the first chamber housing 22 and peripheral boundary projections 36 on the second Chamber housing 24. The provided on one of the chamber housing 22 and 24 perimeter limiting projections 34 and 36 each extend radially to the other chamber housing and lie there to provide a tight completion of circumferentially through these limited pressure chambers 30, 32 at the other chamber housing , It should be noted that in Fig. 2, due to the half-way representation of the torsional vibration damper assembly 10, only one of the peripheral limiting projections 36 of the chamber housing 24 can be seen. Of course, the chamber housing 24 at an angular distance of 180 ° to the circumferential limiting projection 36 shown opposite to another such circumferential boundary projection. Thus, the first damper chamber assembly 26 includes four circumferentially successive pressure chambers 30 and 32, wherein the pressure chamber 30 and the latter at an angular distance of 180 ° opposite and not visible in Fig. 2 pressure chamber is referred to as the first pressure chamber, while the Pressure chamber 32 and the pressure chamber, not shown, and this also with a circumferential distance of approximately 180 ° opposite pressure chamber is hereinafter referred to as a second pressure chamber.

The chamber housing 22 engages with a cylindrical projection 36, the second chamber housing 24 radially inward. A sleeve-like sliding bearing element 38 provides both a radial and an axial bearing function of these two chamber housing 22, 24 ready.

The first damper fluid chamber assembly 26, the pressure chambers 30, 32 are also limited in the axial direction by the first chamber housing 22 and a cover plate 40, radially outwardly surrounding a second damper fluid chamber assembly 42 is provided. In the example shown, this comprises two chamber units 44, 46, which are concentrically arranged about the axis of rotation A of the torsional vibration damper arrangement and preferably extend annularly about the axis of rotation A. The two chamber units 44, 46 are substantially cylindrical in one or by a common axis in the axial direction Circumferentially provided toroidally shaped housing portion 48. In this housing portion 48, two annular disk-like separating piston 50 and 52 are provided. Due to the cylindrical configuration of the housing region 48 or the chamber units 44, 46 in the axial direction, these separating pistons 50 and 52 are displaceable in the axial direction, wherein they respectively at their outer circumference or on its inner circumference, respectively providing a fluid-tight seal on an inner peripheral wall 54 and an external abut circumference wall 56 of the housing portion 48 and are guided there in the axial direction.

At the respectively facing away from each other axial sides of the separating piston 50, 52, a connecting chamber 58, 60 is formed in each case. By a respective annular stop member 62 and 64 of the axial travel of the piston 50, 52 is limited, so that during the movement of the separating piston 50, 52, the volumes of the connecting chambers 58, 60 can not fall below a certain minimum value.

By channel-shaped openings 66, 68 formed in the housing portion 48 and the first chamber housing 22, the connecting chambers 58, 60 in communication with the pressure chambers 30, 32. Here, each of the pressure chambers 30, by a connection opening 68 associated therewith in communication with the connecting chamber 60, while each pressure chamber 32 through its associated connection opening 66 in communication with the connecting chamber 58. This means that all the first pressure chambers 30 are in communication with the same connection chamber 60 and therefore interact primarily with the chamber unit 46 or its separating piston 52, while all the second pressure chambers 32 communicate with the same connection chamber 58 and thus primarily with the chamber unit 44 or ., The separating piston 50 cooperate.

Between the two separating pistons 50, 52 a volume 70 which is variable in size as a function of the axial position of these separating pistons 50, 52 is formed. In this volume is a compressible damper fluid, such as gas, such as air, included. Depending on which of the separating pistons 50, 52 will move axially from one abutment on the respectively associated stop element 62 or 64 to the respective other separating piston, the gas contained in the volume 70 is thus loaded by different ones of the separating pistons 50, 52. That is, this volume 70, with the compressible damper fluid contained therein, is associated with both chamber units 44, 46 to form a composite chamber unit 72. Their function in Vibration damping operation will be explained below.

In the second chamber housing 24, channels 76, 78 are provided in particular also in an axial extension 74, wherein the channel 76 leads to the pressure chambers 30, while the channel 78 leads to the pressure chambers 32. Surrounding the axial extension 74, a ring-type rotary feedthrough element 82 is provided for providing a rotary feedthrough, generally designated 80. This includes respective radial channels 84, 86 provided in association with channels 76, 78 and may be through a valve assembly in communication with a source of pressurized incompressible damper fluid. In this way, the pressure of the incompressible damper fluid fed via the channels 84, 86 or 76, 78 into the pressure chambers 30, 32 and the associated connection chambers 60, 58 can be changed.

In order to provide a tight seal for the rotary feedthrough 80, pressure seals 88, 90, 82 are respectively provided between and also axially outside the radial channels 84, 86. Bearings 94, 96 are provided on the axial outer sides of the pressure seals 90, 92, via which the rotary leadthrough element 80 is rotatably mounted axially and radially on the extension 74 of the second chamber housing 24. Axially outside of these bearings 94, 96 are then flow seals 98, 100 are arranged. The existing between the pressure seal 90 and the flow seal 98 and the bearing 94 receiving space area can be emptied via a formed in the rotary feedthrough element 82 radial passage 102. In a corresponding manner, the space area formed between the pressure seal 92 and the volume flow seal 100 and containing the bearing 96 can be emptied via a radial passage 104. In this way, through these channels 102, 104 a drainage functionality for the pressure seals 90 and 92 overcoming damper fluid can be provided.

It can be seen in Fig. 1 nor that the friction clutch 20 with the radially inner The region of a flywheel 106 thereof is in rotationally coupling engagement by intermeshing serrations. A clamping screw 108 can firmly retain this engagement via a clamping sleeve 110. In the clamping sleeve 110 may then continue to be radially mounted, for example, a transmission input shaft or the like.

To fulfill the vibration damping functionality, for example, in a non loaded with a torque state, the pressure conditions be adjusted so that are biased by the prevailing in the volume 70 pressure of the compressible damper fluid, the two separating pistons 50, 52 in their maximum remote positioning, in which they the respective associated stop elements 62 and 64 abut. In this way it is ensured that the leading to the connecting chambers 58, 60 channels 66, 68 are not covered. The two chamber housings 22, 24 can assume the relative circumferential positioning recognizable in FIG. 2 with respect to each other, in which their peripheral limiting projections 34 and 36 have a mutual circumferential distance of approximately 90 °, so that for the first pressure chambers 30 and the second pressure chambers 32 respectively same volume is provided.

If, starting from this state, a torque is transmitted, for example, from the primary side 12 to the secondary side 18, which means that the drive system is in a tensile state, and this torque is introduced in such a way that in the illustration of FIG Chamber housing 24, the first chamber housing 22 is rotated counterclockwise, this means a load of existing in the pressure chambers 30 incompressible damper fluid. Due to the increase in pressure in the pressure chambers 30, the pressure in the connecting chamber 60 assigned to these pressure chambers 30 will also increase. If this pressure then exceeds the prestressing pressure which is exerted by the compressible damper fluid on the separating piston 52, then the separating piston 52 will shift out of its basic position in the direction of the other separating piston 50. In this case, the compressible damper fluid is compressed in the volume range 70 and increases its pressure accordingly. This axial displacement of the separating piston 52 in the case of an axially stationary separating piston 50 is accompanied by the relative rotation of the two chamber housings 22, 24 which is now possible due to the displacement of the incompressible damping fluid out of the pressure chambers 22 with respect to each other. The volumes of the two first pressure chambers 30 decrease accordingly.

If the two chamber housings 22, 24 loaded in the opposite direction with respect to each other, which may occur in a thrust state, this leads to a relative rotation in the opposite direction, now under compression of the incompressible damper fluid contained in the second pressure chambers 32 and associated therewith the connecting chamber 58 , If the pressure again exceeds the prestressing pressure of the compressible damper fluid in the volume range 70, then the annular separating piston 50 will move in the axial direction to the separating piston 52 again in its basic position and due to the occurring displacement of the incompressible damper fluid from the pressure chambers 32 allow a relative rotation of the two chamber housing 22, 24 with respect to each other.

The torsional vibration damper arrangement 10 shown in FIGS. 1 and 2 has significant advantages due to its structural design with efficient space utilization. First, the separating pistons 50, 52 are arranged so that they are axially displaceable to fulfill their functionality. That is, neither the centrifugal forces occurring during rotational operation nor the circumferential accelerations occurring during torsional oscillations influence the positioning of the separating pistons 50, 52, so that they can actually fulfill their functionality in the vibration damping without significant influence by external circumstances. In principle, this would also be possible if the two chamber units 44, 46 were not combined to form a composite chamber unit 72, but if, for example, between the two separating pistons 50, 52 a volume region 70 is separated into two Chamber dividing partition would be present. It would also be possible to provide only one of the separating pistons 50 and 52, in which case a connection chamber and correspondingly also a vibration damping functionality would then also be provided only in association with the first pressure chambers 30 or the second pressure chambers 32.

A second principle, which can also be seen in the illustration of FIG. 1, relates to connecting the two chamber units 44, 46 to a composite chamber unit 72. This means that chamber units 44, 46 cooperate with the same volume area 70 of the compressible damper fluid if these are active, a larger total volume of the compressible damper fluid can be used. This leads to a much softer characteristic curve or makes it possible to specify or vary the damper characteristic in a significantly larger range by setting the pretensioning pressure of the compressible damper fluid.

A further advantage of the design shown in FIG. 1 is that a comparatively large volume, filled only with the gaseous, incompressible fluid, is present radially on the outside of the primary side 12, so that better spin acceleration values can be achieved due to the comparatively low moment of inertia.

A modified embodiment of a structure of a torsional vibration damper arrangement which utilizes the above-described functional principles or design principles is shown in FIGS. 3 and 4. Here, components that correspond to components described above in terms of structure and function are denoted by the same reference numeral with the addition of an appendix "a".

While in the embodiment described above, the second damper fluid chamber arrangement with respect to the first damper fluid chamber arrangement was arranged radially outward, is in the in FIGS. 3 and 4 shown variant, a reversal of the radial assignment. Here, therefore, the first damper fluid chamber assembly 26a is disposed radially outward of the second damper fluid chamber assembly 42a. It can be seen for this purpose that the now completely radially outer first chamber housing 22a with the radially likewise enlarged second chamber housing 24a again delimits the annular space region 28a, in which the pressure chambers 30a and 32a, respectively bounded in the circumferential direction by the peripheral boundary projections 34a and 36a, follow one another. The radial mounting of the two chamber housings 22a and 24a can take place via a bearing 38a which acts between the second chamber housing 24a and the plate 40a firmly connected to the first chamber housing 22a. Furthermore, the channels 76a and 78a leading to the pressure chambers 30a and 32a are again provided in the second chamber housing 24a. The structure of the rotary feedthrough 80a corresponds to the above-described, so that in this regard and also with respect to the coupling of the friction clutch 20a to the axial extension 74a of the second chamber housing 24a to the above statements.

The two separating pistons 50a, 52a of the chamber units 44a, 46a forming a composite chamber unit 72a are now provided radially inward in a housing region 48a provided essentially by the second chamber housing 24a. In this housing portion 48a is formed with respect to the axis of rotation A is substantially cylindrical and concentric with the axis of rotation A, axially closed space in which the circular disk-like designed here separating piston 50a, 52a are received axially displaceable. Again, they rest against an inner peripheral surface 54a of this common housing portion 48a to form a tight seal. Between the two separating pistons 50a, 52a, the volume region 70a is formed, which contains the compressible damper fluid. At the two axially facing away from each other sides of the separating piston 50a, 52a, the connecting chambers 58a and 60a are formed, in which again the channel-like openings 66a and 68a open, which connect to the pressure chambers 32a and 30a. Again, for the separating piston 50a, 52a in the direction of each other To provide an Axialbewegungsanschlag, are now provided in the radially inner region by these loaded or their Axialhub limiting stop elements 62a, 64a, so as to ensure that the separating piston 50a, 52a, the openings 66a, 68a can not close.

Even with this arrangement, the same functionality results in the vibration damping operation, as described above. Depending on which of the pressure chambers 30a, 32a are loaded by torque introduction, the pressure of the incompressible damper fluid in the connecting chamber 58a or the connecting chamber 60a, which then with a corresponding increase in pressure then a displacement of the respectively associated separating piston 50a or 52a in the axial direction on the in each case in his lying on the stop member 62a and 64a base position located other separating piston leads to.

Since in the embodiment shown in FIGS. 3 and 4 there is no accessibility in the radially inner region, the primary side 12a is coupled to the drive shaft 112a shown here via a flex plate arrangement 114a or the like, which is radially inward through the threaded bolts 14a to the drive shaft 12a is connected and is connected radially outwardly by bolt 116a or the like to the chamber housing 22a of the primary side 12a.

The embodiment variant shown in FIGS. 3 and 4 is characterized by a particularly simple construction. Here, too, it should be emphasized that, of course, the principle of utilizing an axial displacement of a separating piston or other separating element can also be used if only one chamber unit is provided or if the volume area 70a by a partition or the like into two separate and the respective Chamber units 44a and 46a associated subvolume areas is divided.

FIGS. 5 and 6 show a further embodiment of a torsional vibration damper arrangement. Here are parts or assemblies, which previously described with regard to structure or function, with the same reference numeral with the addition of the appendix "b".

First of all, it can be seen that in the embodiment shown in FIGS. 5 and 6, the second damper fluid chamber arrangement 42d, ie the one

Arrangement, which also contains substantially the compressible damper fluid, with a substantially ring-like structure and radially within the first

Damper fluid chamber assembly 26b is arranged. A housing portion 48b providing or containing substantially the second damper fluid chamber arrangement 42b is arranged with a substantially ring-like shape radially inside the second chamber housing 24b and is also non-rotatably connected thereto.

The housing portion 48b now contains four chamber units 44b, 46b, 44b ¹ , 46b 'with these respectively associated separating piston 50b, 52b, 50b ¹ , 52b'. These separating pistons move in the circumferential direction along the annular formed in the housing portion 48b, so in the circumferential direction extending recesses with a corresponding pressure load. Again, two of the chamber units 44b, 46b, 44b ', 46b ^{1 form} a composite chamber unit 72b or 72b'. In particular, it can be seen that the chamber unit 46b interacting with the pressure chamber 30b forms with its separating piston 52b and the chamber unit 44b cooperating with the pressure chamber 32b with its separating piston 50b the composite chamber unit 72b extending approximately over a circumferential extension of 180 ° with the volume area 70b. Correspondingly, the cooperating with the pressure chamber 30b ¹ chamber unit 46b ¹ form with their separating piston 52b ¹ and cooperating with the pressure chamber 32b ¹ chamber unit 44b ¹ with its separating piston 50b ^1, the composite chamber unit 72b '. Each of the chamber units 44b, 46b, 44b ', 46b ¹ interacts with the associated pressure chamber via a respective connecting chamber 60b, 58b, 60b ¹ , 58b ¹ and via the openings 68b, 66b, 68b formed in the housing area 48b or also in the second chamber housing 24b ', 66b ¹ together. These connecting chambers are again in the housing area 48b and close in the circumferential direction of the volume 70b or 70b 'closed off by the respective separating pistons 52b, 50b, 52b', 50b '. In order to keep the openings 68b, 66b, 68b ', 66b ¹ free, stop elements 64b, 62b, 64b ¹ , 62b' designed for the separating pistons 52b, 50b, 52b ', 50b ^1, for example in the form of securing rings, are provided.

With relative rotation of the two chamber housing 22b, 24b with respect to each other, the volume of either the first pressure chambers 30b, 30b ¹ or the second pressure chambers 32b, 32b ^{1 is} reduced, with the result that the cooperating with these in their volume-reduced pressure chambers

Connecting chambers 60b, 58b, 60b ', 58b ¹ are filled with incompressible damper fluid and move the associated two separating piston 52b, 52b' or 50b, 50 'under compression of the contained in the volume areas 70b, 70b' compressible, such as gaseous damper fluid.

Here, too, the effect can be used that for both relative directions of rotation, the total volume of two chamber units represented by the volume portions 70b, 70b ^1, can be used for the performance of the attenuation function, which due to the relatively large volume available a much larger Variability in the adjustment of the damping characteristic, for example, by specifying the biasing pressure or the degree of filling of the volume areas 70b, 70b ¹ allows with the compressible damper fluid.

It should be pointed out here that the possibility of supplying or removing incompressible damper fluid, for example by means of a rotary feedthrough described in the preceding embodiments, can again be provided for the pressure chambers.

FIGS. 7 and 8 show a further embodiment of a torsional vibration damper arrangement with separating pistons which are movable in the circumferential direction. Here, components which correspond to components described above in terms of structure and function are denoted by the same reference numeral with the addition of an appendix "c".

In the variant shown in FIGS. 7 and 8, the second damper fluid chamber arrangement 42c is now arranged radially outside the first damper fluid chamber arrangement 26c. This means that the housing region 48c now lies radially outside the first chamber housing 22c and is firmly connected thereto, for example. It can be seen in Fig. 8 that the housing portion 48c is here assembled, for example, of two halves, with the left half shown in Fig. 8 containing the two chamber units 46c and 44c ¹ , which together also provide the composite chamber unit 72c. The other half of the housing portion 48c contains the two chamber portions 44c and 46c ', which together form the composite chamber unit 72c'. The functionality corresponds to that described above. The end stops for the separating pistons 52c, 50c, 52c ¹ , 50c ¹ are now formed by plungers 120c, 122c, 120c ¹ , 122c ^{1 provided} thereon, which can be supported on respective intermediate walls separating the two halves of the chamber region 48c.

The advantage of this embodiment is that especially the radially inner space for a larger volume of the pressure chambers 30c, 32c, 30c ¹ and 32c ¹ can be used. Also, due to the arrangement further radially outward for the second damper fluid chamber assembly 42c, a larger overall volume can be provided.

Claims

claims A torsional vibration damper arrangement, in particular for the drive train of a vehicle, comprising a primary side (12, 12a) and a damper fluid arrangement (16, 16a) with the primary side (12; 12a) for rotation about an axis of rotation (A) and for relative rotation with respect to each other coupled secondary side (18; 18a), said damper fluid assembly (16; 16a) having a torque between said primary side (12; 12a) and said secondary side (18; 18a). transmitting first damper fluid with lower compressibility in a first Damper fluid chamber assembly (26; 26a) and a second damper fluid having a higher compressibility in a second damper fluid chamber assembly (42; 42a) loaded upon pressure increase of the first damper fluid in the first damper fluid chamber assembly (26; 26a), the second damper fluid chamber assembly (42; 42a) at least a chamber unit (44, 46; 44a, 46a) disposed radially outward and / or radially inward of the first damper fluid chamber assembly (26; 26a), associated with each chamber unit (44,46; 44a, 46a) first damper fluid separating from the second damper fluid and when changing pressure in the chamber unit (44, 46; 46a) substantially in the direction of the axis of rotation (A) displaceable separating element (50, 52, 50a, 52a) is provided. 2. Torsionsschwingungsdämpferanordnung according to claim 1, characterized in that the at least one chamber unit (44, 46) of the second damper fluid chamber assembly (42) with respect to the first damper fluid chamber assembly (26) is arranged radially outward. 3. Torsionsschwingungsdämpferanordnung according to claim 2, characterized in that the second damper fluid chamber arrangement (42) at least one ring-like the first damper fluid chamber assembly (26) surrounding the chamber unit (44, 46), wherein the first Damper fluid separating from the second damper fluid separating element (50, 52) of the at least one chamber unit (44, 46) is formed like a ring. 4. Torsionsschwingungsdämpferanordnung according to claim 1, characterized in that the at least one chamber unit (44a, 44b) of the second damper fluid chamber assembly (42a) is disposed radially inward of the first damper fluid chamber assembly (26a). 5. Torsionsschwingungsdämpferanordnung according to claim 4, characterized in that the second damper fluid chamber arrangement (42a) at least one to the rotation axis (A) substantially concentrically arranged chamber unit (44a, 46a), wherein the first damper fluid from the second damper fluid separating separator (50a, 52) of the at least one chamber unit (44a, 46a) formed substantially circular disc-like is. 6. A torsional vibration damper assembly according to any one of claims 1 to 5, characterized in that the first damper fluid chamber assembly (26; 26a) at least one in relative rotation of the primary side (12; 12a) with respect to the secondary side (18; 18a) in a first direction of relative rotation reducible in volume a first pressure chamber (30; 30a), which via a connecting chamber (60; 60a) is in operative connection with at least one of these chamber unit (46; 46a) of the second damper fluid chamber arrangement (42; 42a). 7. Torsional vibration damper arrangement according to claim 6, characterized in that the first damper fluid chamber arrangement (26; 26a) has at least one relative rotation of the primary side (12; 12a) with respect to the secondary side (18; 18a) in a second relative rotational direction opposite to that of the first relative rotational direction Volume verminderbare second pressure chamber (32; 32a), which via a connecting chamber (58; 58a) in operative connection with at least one of these associated chamber unit (44; 44a) of the second damper fluid chamber assembly (42; 42a) is. 8. Torsionsschwingungsdämpferanordnung according to claim 6 or 7, characterized in that the at least one first pressure chamber (30; 30a) or / and the at least one second pressure chamber (32; 32a) extends in the circumferential direction. 9. Torsionsschwingungsdämpferanordnung according to any one of claims 6 to 8, characterized in that one side of the primary side (12; 12a) and Secondary side (18, 18a) comprises a first substantially cylindrical chamber housing (22; 22a) and that the other side of the primary side (12; 12a) and secondary side (18; 18a) inserted into the first cylindrical chamber housing (22; 22a) and with this one annular space (28, 28a) limiting second cylindrical chamber housing (24; 24a), wherein on the first chamber housing (22; 22a) at least one on the second chamber housing (24; 24a) to be extended first circumferential limiting projection (34; 34a) is provided and on the second chamber housing (24; at least one second extending to the first chamber housing (22; 22a) A pressure chamber (30, 32; 30a, 32a) in the circumferential direction is delimited between each of a first peripheral limiting projection (34; 34a) and a second peripheral limiting projection (36; 36a) and the volume of the pressure chamber (36; 30, 32, 30a, 32a) is variable by relative circumferential movement of said limiting circumferential limiting projections (34, 36, 34a, 36a). A torsional vibration damper assembly according to claim 7 or any one of claims 8 and 9 when appended to claim 7, characterized in that at least one of a first pressure chamber (30; 30a) is associated with the first damper fluid chamber assembly (26; 26a) Chamber unit (46; 46a) of the second damper fluid chamber assembly (42; 42a) is in pressure balancing communication with at least one further chamber unit (44; 44a) of the second damper fluid chamber assembly (42; 42a) which communicates with a second pressure chamber (32; 32a) of the first damper fluid chamber assembly (26; ; 26a) is assigned. H torsional vibration damper assembly according to claim 10, characterized in that two chamber units (44, 46; 44a, 46a) of the second damper fluid chamber arrangement (26; 26a) in the direction of the axis of rotation (A) successively in a common housing portion The separating elements (50, 52, 50a, 52a) of the two chamber units (44, 46, 44a, 46a) in the housing region (48, 48a) follow one another axially and in the direction of the axis of rotation (A ) are arranged displaceable and wherein the second damper fluid in the housing portion (48; 48a) between the two separating elements (50, 52; 50a, 52a) is arranged. 12.Torsionsschwingungsdämpferanordnung, in particular for the drive train of a vehicle comprising a primary side (12; 12a; 12b, 12c) and a damper fluid arrangement (16; 16a; 16b; 16c) with the 12 (12; 12b; 12c) for rotation about a rotational axis (A) and for relative rotation with respect to each other coupled secondary side (18; 18a; 18b; 18c), wherein the damper fluid assembly (16; 16a; 16b; 16c) has a torque The first damper fluid having a lower compressibility in a first damper fluid chamber arrangement (26; 26a; 26b; 26c) and a pressure booster of the first damper fluid comprises the primary side (12; 12a; 12b; 12c) and the secondary side (18; 18a; Damper fluid in the first damper fluid chamber assembly (26; 26a; 26b; 26c) comprises second damper fluid having higher compressibility in a second damper fluid chamber assembly (42; 42a; 42b; 42c), the second damper fluid chamber assembly (42; 42a; 42b; chamber units (44, 46; 44a, 46a; 44b, 44b ¹ , 46b, 46b '; 44c), 44c ', 46c, 46c ¹ ), wherein in association with each chamber unit (44, 46; 44a, 46a; 44b, 44b ¹ , 46b, 46b ¹ ; 44c, 44c', 46c, 46c ¹ ) is a first damper fluid of separating the second damper fluid and pressure change in the chamber unit (44, 46; 44a, 46a; 44b, 44b ^1, 46b, 46b '; 44c, 44c ^1, 46c, 46c ¹⁾ displaceable separating element (50, 52; 50a, 52a; 50b, 50b ¹ , 52b, 52b ¹ ; 50c, 50c ¹ , 52c, 52c ¹ ), wherein at least two chamber units (44, 46; 44a, 46a; 44b, 44b ¹ , 46b, 46b ¹ ; 44c, 44c ¹ , 46c, 46c ¹ ) of the second damper fluid chamber arrangement (FIGS. 42; 42a; 42b; 42c) comprises a composite chamber unit (72; 72a; 72b, 72b ¹ ; 72c, 72c ¹ ) having a common volume (70; 70a; 70b, 70b ¹ ; 70c, 70c ¹ ) for the second one Damper fluid and the second damper fluid of each composite chamber unit (72; 72a; 72b, 72b ¹ ; 72c, 72c ¹ ) through each separator (50,52; 50a, 52a; 50b, 50b ¹ , 52b, 52b ¹ ; 50c, 50c ¹ , 52c, 52c ¹ ) of the chamber units (44, 46; 44a, 46a; 44b, 44b ¹ , 46b, 46b ¹ ; 44c, 44c ", 46c, 46c ¹ ) of said composite chamber unit (72; 72a; 72b, 72b ¹ , 72c, 72c ¹ ) is compressible. 13.A torsional vibration damper arrangement according to claim 12, characterized in that the first damper fluid chamber arrangement (26; 26a; 26b; 26c) at least one upon relative rotation of the primary side (12; 12a; 12b; 12c) with respect to the secondary side (18; 18a; 18b; 18c) in a first direction of relative rotation reducible in its volume first pressure chamber (30; 30a; 30b, 30b ¹ ; 30c, 30c ¹ ), which via a connecting chamber (60; 60a; 60b, 60b ¹ , 60c, 60c ¹ ) are operatively connected to at least one of said chamber unit (46; 46a; 46b, 46b ¹ ; 46c, 46c ¹ ) of a composite chamber unit (72; 72a; 72b, 72b ¹ ; 72c, 72c ¹ ) of the second damper fluid chamber assembly (42; 42a; 42b, 42b ¹ ), and at least one upon relative rotation of the primary side (12; 12a 12b, 12c) with respect to the secondary side (18, 18a, 18b, 18c) in a second relative direction of rotation opposite to the first relative rotational direction Volume verminderbare second pressure chamber (32; 32a; 32b, 32b ¹ ; 32c, 32c ¹ ) which via a connecting chamber (58; 58a; 58b, 58b ¹ , 58c, 58c ') in operative communication with at least one of said associated chamber unit (44; 44a; 44b, 44b'; 44c, 44c ') of the same composite chamber unit (72; 72a; 72b, 72b ¹ ; 72c, 72c') of the second damper fluid chamber assembly (58; 42, 42a, 42b, 42c). A torsional vibration damper arrangement according to claim 13, characterized in that the at least one first pressure chamber (30; 30a; 30b, 30b ¹ ; 30c, 30c ') and / or the at least one second pressure chamber (32; 32a; 32b, 32b'; 32c , 32c ¹ ) extends in the circumferential direction. iδ.Torsionsschwingungsdämpferanordnung according to claim 13 or 14, characterized in that one side of the primary side (12; 12a; 12b; 12c) and secondary side (18; 18a; 18b; 18c) a first substantially cylindrical chamber housing (22; 22a; 22b; 22c) and that the other side of the primary side (12; 12a; 12b; 12c) and secondary side (18; 18a; 18b; 18c) comprises a second cylindrical chamber housing (24; 24a; 24b; 24c) inserted into the first cylindrical chamber housing (22; 22a; 22b; 22c) and defining with it an annular space (28; 28a; 28b; 28c); at least one first circumferential confining projection (34; 34a; 34b; 34c) extending to the second chamber housing (24; 24a; 24b; 24c) is provided on the first chamber housing (22; 22a; 22b; 22c) and attached to the second chamber housing (24; 24a; 24b; 24c) at least one second circumferential limiting projection (36; 36a; 36b; 36c) is provided on the first chamber housing (22; 22a; 22b; 22c) and being arranged between in each case a first circumferential limiting projection (34; 34a; 34b 34c) and a second peripheral limiting projection (36; 36a; 36b; 36c) delimit a pressure chamber (30,32; 30a, 32a; 30b, 30b ', 32b, 32b ¹ ; 30c, 30c ¹ , 32c, 32c') in the circumferential direction and the volume of the pressure chamber (30, 32; 30a, 32a; 30b, 30b ¹ , 32b, 32b ¹ ; 30c, 30c ¹ , 32c, 32c ') by relative circumferential movement of these limiting circumferential limiting projections (34, 36; 34a, 36a; 34b, 36b; 34c, 36c) is changeable. The torsional vibration damper arrangement according to one of claims 12 to 15, characterized in that in at least one of the chamber units (44, 46, 44a, 46a) of the second damper fluid chamber arrangement (42, 42a) Separating element (50, 52, 50a, 52a) is displaceable substantially in the direction of the axis of rotation (A). The torsional vibration damper arrangement according to any one of claims 12 to 15, characterized in that in at least one of the chamber units (44b, 44b '; 44c, 44c') of the second damper fluid chamber assembly (42b; 42c), the separator (50b, 50b ¹ ; 50c, 50c ¹ ) is displaceable substantially in the circumferential direction with respect to the axis of rotation (A). i δ.Torsionsschwingungsdämpferanordnung according to any one of claims 12 to 15, characterized in that in at least one of the chamber units of the second damper fluid chamber arrangement, the separating element is displaceable substantially radially with respect to the axis of rotation. A torsional vibration damper assembly according to any one of claims 1 to 18, characterized in that the separator (50, 52; 50a, 52a; 50b, 50b ', 52b, 52b'; 50c, 50c ¹ , 52c, 52c ¹ ) is a separator piston. 20. Torsionsschwingungsdämpferanordnung according to any one of claims 1 to 19, characterized in that the first damper fluid chamber assembly (26; 26a) via a rotary feedthrough (80; 80a) in conjunction with a Source or / and a reservoir for the first damper fluid is or can be brought.