DE102007054570A1 - torsional vibration damper - Google Patents

Abstract

A torsional vibration damper assembly comprising a primary side (20) and a secondary side (44) rotatable against the action of a damper fluid assembly about an axis of rotation (A) relative to the primary side (20), the damper fluid assembly comprising two sets of displacement chambers (32) filled with first damper fluid of lower compressibility. comprising in each case at least one displacement chamber (32) and in association therewith at least one compensation chamber (36) filled with a second damper fluid of higher compressibility, wherein upon rotation of the primary side (20) with respect to the secondary side (44) first damper fluid from the at least one displacement chamber (32) displacing one of the groups thereby compressing the second damper fluid in at least one compensation chamber (36), the displacement chambers (32) being bounded by a primary-side displacement chamber assembly (24) and a secondary-side displacement chamber assembly (46) one of the displacement chamber assemblies (24, 46) forms a structural unit with a rotating part (54) of a rotary leadthrough (52), through which rotary leadthrough (52) via a first fluid connection (88) in a non-rotating part (56) of the rotary leadthrough (52) first damper fluid from and to the at least one displacement chamber (32) of a first group of displacement chambers can be conducted and via a first fluid connection (88) at least axially offset second fluid connection (110) in the non ...

Description

The The present invention relates to a torsional vibration damper assembly, comprising a primary page and one against the action of a damper fluid assembly around one Rotary axis with respect the primary side rotatable secondary side, wherein the damper fluid assembly two groups of with first damper fluid less compressibility filled displacement chambers each with at least one displacement chamber and in association to at least one with second damper fluid higher compressibility filled compensation chamber wherein, upon rotation of the primary side with respect to the secondary side first damper fluid from the at least one displacement chamber one of the groups displaced and thereby the second damper fluid is compressed in at least one compensation chamber, wherein the displacement chambers through a primary-side Displacement chamber assembly and a secondary-side Displacement chamber assembly are limited and wherein one of the displacement chamber assemblies a Forming unit with a rotating part of a rotary union, through which rotary feedthrough over a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is controllable and over a first fluid connection at least axially offset second Fluid connection in the non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a second Group of displacement chambers is conductive.

such torsional vibration damper, commonly known as gas spring dual mass flywheels, are therefore of comparatively complex construction, in particular because the possibility must be created over one Rotary union with the displacement chambers first damper fluid to supply or first damper fluid to be able to deliver from these. It is important to ensure that the structural design so is that to be transferred Torques even without mechanical overload of the various Transfer components can be. At the same time, care must be taken to ensure that there are operational impairments be largely avoided by any pressure fluid leaks.

It Therefore, the object of the present invention to provide a Torsionsschwingungsdämpferanordnung, where the above problems do not substantially occur.

According to one First aspect of the present invention, this object is achieved by a torsional vibration damper arrangement, comprising a primary page and one against the action of a damper fluid assembly around one Rotary axis with respect the primary side rotatable secondary side, wherein the damper fluid assembly two groups of with first damper fluid less compressibility filled displacement chambers each with at least one displacement chamber and in association to at least one with second damper fluid higher compressibility filled compensation chamber wherein, upon rotation of the primary side with respect to the secondary side first damper fluid from the at least one displacement chamber one of the groups displaced and thereby the second damper fluid is compressed in at least one compensation chamber, wherein the displacement chambers through a primary-side Displacement chamber assembly and a secondary-side Displacement chamber assembly are limited and wherein one of the displacement chamber assemblies a Forming unit with a rotating part of a rotary union, through which rotary feedthrough over a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is controllable and over a first fluid connection at least axially offset second Fluid connection in the non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a second Group of displacement chambers is conductive, wherein in the assembly an axial opening and therein an insert part are provided, wherein the insert part a first fluid channel for connecting the first fluid port with the at least one displacement chamber the first group limited and a second fluid channel for connection the second fluid port with the at least one displacement chamber limited to the second group.

By providing the rotating part of the rotary union with an insert it is possible in a simple manner, the two required fluid channels to define about which the two groups of displacement chambers with pressurized fluid, namely the first damper fluid be fed or emptied.

A Connection between the fluid channels and can be provided in the non-rotating part of the rotary union fluid connections be realized in a simple manner that in the axial region the fluid connections in the rotating part of the rotary feedthrough at least one connection opening between the first fluid port and the first fluid passage and at least a connection opening are provided between the second fluid port and the second fluid passage.

Of the second fluid channel may at least partially the first fluid channel be arranged surrounding, in which case preferably the first fluid channel at least one substantially axial, preferably coaxial with An axis of rotation, in the insert part extending opening comprises. At this Design can then be a connection between the first fluid channel and the associated fluid connection, possibly via one or more connection openings, be realized in a simple manner that the first fluid channel in the axial region of the first fluid port to the axial opening in the Unit is open.

Of the second fluid channel can in a simple manner between a Outer peripheral surface of the insert part and an inner peripheral surface be formed of the assembly, ie an inner peripheral surface, which also the axial opening limited in the unit.

Around a communication between the two fluid channels or the two so in Connecting fluid connections It is further suggested that in an area between the first fluid port and the second fluid port a fluid-tight Termination between the insert and the unit is formed.

The Connection of the displacement chambers the associated fluid channels can for example be realized by being assigned to every displacement chamber the first group in the assembly at least one connection opening between this and the first fluid channel is provided and that in association to every displacement chamber the second group in the assembly at least one connection opening between this and the second fluid channel is provided, wherein further can advantageously be provided that at one in the axial Area of the displacement chambers lying end portion of the insert at least one to the axial extending opening open in the insert and with the at least one displacement chamber the first group associated with at least one connection opening in the unit in communication connecting opening provided is.

There especially if one of the fluid channels between opposite surface areas the unit and the insert is formed, the risk of Fluid leakage from this adjoining area out is further suggested that the insert in his in the field the displacement chambers lying end portion of the assembly by material connection is fixed. In this way, not only is a fluid density, but especially under the prevailing high pressures of created up to 70 bar stable connection.

The Previously addressed high pressures can be compared to a comparatively strong axial load of the insert then lead, if its In the two axial directions loaded surfaces differently are big. It is therefore proposed that the first fluid channel and with this related fluid flow areas in the insert part or / and the second fluid channel in a first axial Direction through a first end surface of the insert part are limited and in a second axial direction through a second end surface of the insert part are limited and that the size of the first end surface substantially the size of the second end face equivalent.

According to one Another aspect of the present invention is the aforementioned Task solved by a torsional vibration damper arrangement, comprising a primary page and one against the action of a damper fluid assembly around one Rotary axis with respect the primary side rotatable secondary side, wherein the damper fluid assembly two Groups of with first damper fluid less compressibility filled Displacement chambers with in each case at least one displacement chamber and in association therewith, at least one compensation chamber filled with a second damper fluid of higher compressibility wherein, upon rotation of the primary side with respect to the secondary side first damper fluid from the at least one displacement chamber one of the groups displaced and thereby the second damper fluid is compressed in at least one compensation chamber, wherein the displacement chambers through a primary-side Displacement chamber assembly and a secondary side displacement chamber assembly are limited and wherein one of the displacement chamber assemblies a Forming unit with a rota-generating part of a rotary union, through which rotary feedthrough over a first fluid connection in a non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is controllable and over a first fluid connection at least axially offset second fluid port in the non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber of a second Group of displacement chambers is conductive, wherein in the assembly between the axial region the displacement chambers and the axial portion of the second fluid port a plurality of is provided in substantially axially extending openings, which in terms of the axis of rotation are radially offset and an angular distance from each other exhibit.

Also in this embodiment, a sufficient fluid exchange between the displacement chambers and the fluid connections allows namely about one Majority of openings that as a second fluid channel, a connection between displacement chambers realize one of the groups and the associated fluid connection.

there For example, it may be provided that the angular distance W1 in the Essentially defined by W1 = 360 ° / n1, where n1 is the number of openings is, so one over the circumference evenly and thus not to imbalances or locally excessive weakening premier Arrangement is created.

A Connection of these openings to the associated fluid port or the associated displacement chambers This can be done by having each opening in its in the axial Range of the second fluid port end region over at least a connection opening is open to the second fluid port and in its axial Area of the displacement chambers lying end region over at least one connection opening to the at least one displacement chamber the second group is open.

Around also the displacement chambers connect the first group to the associated fluid port to be able to It is suggested that in the assembly between the axial Area of the displacement chambers and the axial portion of the first fluid port is in the Substantially axially extending fluid channel is provided.

This Fluid channel may be substantially coaxial with the axis of rotation. Alternatively it can be provided that a plurality of openings is provided, which are radially offset from the axis of rotation and have an angular distance from each other and provide the fluid channel.

Especially then, if several openings are provided of the fluid channel, whose angular distance W2 in Essentially defined by W2 = 360 ° / n2, where n2 is the number of openings is.

Preferably the arrangement is such that in the circumferential direction openings of the fluid channel and the second fluid channel forming openings alternate, then continue for a very stable and unbalanced avoiding arrangement can be ensured by the fact that the angular distances between circumferentially consecutive openings are the same size.

Also in the case of the fluid channel can for a connection to the fluid connection or the associated displacement chambers be ensured that the fluid channel in his in the axial Range of the second fluid port end region over at least a connection opening to the first fluid port is open and its in the axial region the displacement chambers lying end region over at least one connection opening is open to at least one connecting chamber of the first group.

According to one Another aspect of the above-mentioned object is achieved by a torsional vibration damper arrangement, comprising a primary page and one against the action of a damper fluid assembly around one Rotary axis with respect the primary side rotatable secondary side, wherein the damper fluid assembly two groups of with first damper fluid less compressibility filled displacement chambers each with at least one displacement chamber and in association to at least one with second damper fluid higher compressibility filled compensation chamber wherein, upon rotation of the primary side with respect to the secondary side first damper fluid from the at least one displacement chamber one of the groups displaced and thereby the second damper fluid is compressed in at least one compensation chamber, wherein the displacement chambers through a primary-side Displacement chamber assembly and a secondary-side Displacement chamber assembly are limited and wherein one of the displacement chamber assemblies a Forming unit with a rotating part of a rotary union, through which rotary feedthrough over a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is controllable and over a first fluid connection at least axially offset second Fluid connection in the non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a second Group of displacement chambers is conductive, wherein the fluid ports in the non-rotating Part of the rotary union each comprise at least one connection opening and wherein no port opening the first fluid port in axial alignment with a port of the second fluid connection is located.

at This arrangement is therefore for it taken care that between two axially consecutive connection openings a circumferential offset is present. This allows the axial distance the connection openings To keep very small, so in principle also the rotary feedthrough axially short design, but at the same time also sufficient stability provide.

According to another aspect of the present According to the invention, the object mentioned at the outset is achieved by a torsional vibration damper arrangement comprising a primary side and a secondary side rotatable against the action of a damper fluid arrangement about an axis of rotation relative to the primary side, the damper fluid arrangement comprising two groups of displacement chambers filled with first damper fluid of lower compressibility, each having at least one displacement chamber and in association with this, at least one compensation chamber filled with a second damper fluid of higher compressibility, wherein upon rotation of the primary side with respect to the secondary side, first damper fluid is displaced from the at least one displacement chamber of one of the groups and thereby the second damper fluid is compressed in at least one compensation chamber, the displacement chambers passing through a primary-side displacement chamber assembly and a secondary-side displacement chamber assembly are limited and wherein ei ne of the displacement chamber assemblies forms a structural unit with a rotating part of a rotary feedthrough through which rotary feedthrough via a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is conductive and offset from one to the first fluid connection second fluid connection in the non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a second group of displacement chambers is guided, wherein in the non-rotating part of the rotary feedthrough an insert sleeve firmly connected thereto is provided, the inner peripheral surface of an outer peripheral surface of the rotating part lies opposite the rotary feedthrough.

By the provision of an insert sleeve in the non-rotating part of the rotary union, it becomes possible, on the one hand the mechanical stress that occurs due to mutual friction to intercept that for the insert sleeve very stable, for example, hardened material is used. On the other hand, as part of the non-rotating part of the Rotary union to be considered insert sleeve very easy with different surface geometries or structuring be provided to different flow paths for the first damper fluid to provide in the non-rotating part of the rotary feedthrough.

For example can be provided that in association with at least one fluid connection in the inner peripheral surface the insert sleeve or / and the outer peripheral surface of the rotating part of the rotary feedthrough a circumferential groove is provided, in which at least one connection opening of a fluid connection or a connection opening opens.

According to one Another aspect of the present invention is the aforementioned Task solved by a torsional vibration damper arrangement, comprising a primary page and one against the action of a damper fluid assembly around one Rotary axis with respect the primary side rotatable secondary side, wherein the damper fluid assembly two Groups of with first damper fluid less compressibility filled Displacement chambers with in each case at least one displacement chamber and in association therewith, at least one compensation chamber filled with a second damper fluid of higher compressibility wherein, upon rotation of the primary side with respect to the secondary side first damper fluid from the at least one displacement chamber one of the groups displaced and thereby the second damper fluid is compressed in at least one compensation chamber, wherein the displacement chambers through a primary-side Displacement chamber assembly and a secondary side displacement chamber assembly are limited and wherein one of the displacement chamber assemblies a Assembly with a rotating part of a rotary union bil det, through which rotary feedthrough over a first fluid connection in a non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is controllable and over a first fluid port offset second fluid port in the non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber of a second Group of displacement chambers is conductive, wherein in one of the axial region of the displacement chambers on removed first axial end portion of the non-rotating part the rotary union the rotating part of the rotary feedthrough via a first bearing arrangement is mounted and in an axial region of the displacement chambers closer lying second axial end portion of the non-rotating part of the rotary feedthrough of rotating part of the rotary union over a second bearing assembly is mounted, wherein one of the bearing assemblies includes a floating bearing.

By This configuration makes it possible at stable arrangement an over-determination to avoid, for example, what would happen if none of the bearing assemblies would be a floating bearing, but both bearing arrangements fixed bearing, so even with fixed predetermining Axial positioning would be.

Preferably the second bearing arrangement is designed as a floating bearing.

The Bearing arrangements can axially afterwards to the insert sleeve be provided.

According to one Another aspect of the above-mentioned object is achieved by a torsional vibration damper arrangement, comprising a primary page and one against the action of a damper fluid assembly around one Rotary axis with respect the primary side rotatable secondary side, wherein the damper fluid assembly two groups of with first damper fluid low compressibility filled displacement chambers each with at least one displacement chamber and in association to at least one with second damper fluid higher compressibility filled compensation chamber wherein, upon rotation of the primary side with respect to the secondary side first damper fluid from the at least one displacement chamber one of the groups displaced and thereby the second damper fluid is compressed in at least one compensation chamber, wherein the displacement chambers through a primary-side Displacement chamber assembly and a secondary-side Displacement chamber assembly are limited and wherein one of the displacement chamber assemblies a Forming unit with a rotating part of a rotary union, through which rotary feedthrough over a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is controllable and over a first fluid port offset second fluid port in the non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber of a second Group of displacement chambers is conductive, wherein the other displacement chamber assembly two end walls at an axial distance from each other and thus firmly connected to a peripheral wall includes and the end walls each over a bearing assembly with respect the unit are stored.

at This type of design will be very easy to implement and yet stable storage between the two displacement chamber assemblies or the primary side and the secondary side realized.

Around an over-determination To avoid mutual positioning, it is suggested that the bearing assemblies include floating bearings. For example, can be provided be that closer to the non-rotating part of the rotary feedthrough End wall has a substantially cylindrical neck on which one of the bearing assemblies is radially supported.

A Protection against unwanted fluid leakage can be obtained by that between the cylindrical approach and the unit acts as a fluid seal and that in the space area between the fluid seal and the bearing assembly, a drainage channel opens.

According to one Another aspect of the above-mentioned object is achieved by a torsional vibration damper arrangement, comprising a primary page and one against the action of a damper fluid assembly around one Rotary axis with respect the primary side rotatable secondary side, wherein the damper fluid assembly two groups of with first damper fluid less compressibility filled displacement chambers each with at least one displacement chamber and in association to at least one with second damper fluid higher compressibility filled compensation chamber wherein, upon rotation of the primary side with respect to the secondary side first damper fluid from the at least one displacement chamber one of the groups displaced and thereby the second damper fluid is compressed in at least one compensation chamber, wherein the displacement chambers through a primary-side Displacement chamber assembly and a secondary-side Displacement chamber assembly are limited and wherein one of the displacement chamber assemblies a Forming unit with a rotating part of a rotary union, through which rotary feedthrough over a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is controllable and over a first fluid port offset second fluid port in the non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber of a second Group of displacement chambers is conductive, wherein on both sides of the first fluid port and the second fluid port each having a first fluid seal between the non-rotating part of the rotary union and the rotating part of the rotary feedthrough acts and on both end areas the non-rotating part of the rotary union between this and the Assembly or the other displacement chamber assembly one each second fluid seal acts, with each in between two following formed of these fluid seals space area in the non-rotating part of the rotary union provided drainage channel opens wherein the drainage channels with a drainage port in the non-rotating part of the rotary union in FIG Connection stand.

Also in this embodiment, by providing various drainage channels ensured, that over Seals passed fluid leaks defined to be dissipated can and do not leave in an inappropriate place.

In this case, for example, the first fluid seals may be pressure seals, that is to say seals which are designed to withstand very high pressures, while the second fluid seals may be volume flow seals, that is, sealing which, in principle, lesser Pressure loads are designed, but then can provide a very high density.

According to one Another aspect of the above-mentioned object is achieved by a torsional vibration damper arrangement, comprising a primary page and one against the action of a damper fluid assembly around one Rotary axis with respect the primary side rotatable secondary side, wherein the damper fluid assembly two groups of with first damper fluid less compressibility filled displacement chambers each with at least one displacement chamber and in association to at least one with second damper fluid higher compressibility filled compensation chamber wherein, upon rotation of the primary side with respect to the secondary side first damper fluid from the at least one displacement chamber one of the groups displaced and thereby the second damper fluid is compressed in at least one compensation chamber, wherein the displacement chambers through a primary-side Displacement chamber assembly and a secondary-side Displacement chamber assembly are limited and wherein one of the displacement chamber assemblies a Forming unit with a rotating part of a rotary union, through which rotary feedthrough over a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is controllable and over a first fluid port offset second fluid port in the non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber of a second Group of displacement chambers is conductive, wherein in association with at least one of the fluid connections and / or a drainage port of the non-rotating part of the rotary feedthrough a Sensor arrangement for pressure detection and / or volume flow detection is provided.

By the possibility, pressures or volume flows in different areas to detect in which fluid to or dissipated becomes possible, it becomes possible to close the operating state and, for example, too to detect if an excessively large leakage current is available.

The one of the positive displacement subassemblies and the rotating part of the rotary feedthrough can be used to provide the Assembly be integrally formed, so on one and the same Component be realized without requiring a further process of joining would. This is therefore particularly advantageous, since this connection points, should be secured against fluid leakage, be avoided.

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

1 a part of a known type of drive train to a gas spring dual mass flywheel and a rotary feedthrough;

2 a cross-sectional view of the gas spring dual mass flywheel of 1 ;

3 the displacement chamber assemblies and the rotary feedthrough of a design according to the invention;

4 the arrangement of 3 without the non-rotating part of the rotary union;

5 an enlarged detail of the arrangement of 4 in an axial end region of two fluid channels;

6 in a slightly enlarged view of the other axial end portion of the fluid channels of the arrangement of 4 ;

7 a cross-sectional view of the arrangement of 4 , taken along a line VII-VII in 4 ;

8th one of the 7 corresponding cross-sectional view, taken along a line VIII-VIII in 4 ;

9 a partial view of the in 3 shown view;

10 a structural unit formed from a displacement chamber assembly and the rotating part of the rotary union according to an alternative embodiment;

11 one of the 3 corresponding representation of an alternative embodiment,

12 a perspective longitudinal sectional view of the Ausgestaltungsart the 11 , cut in one to the cutting plane of the 11 90 ° rotated cutting plane;

13 a cross-sectional view of the central part of the rotary feedthrough of 12 , taken along a line XIII-XIII in 12 ;

14 one of the 12 corresponding view of an alternative embodiment;

15 a cross-sectional view of the central part of the rotary feedthrough of 14 , cut along a line XV-XV in 14 ;

16 the non-rotating part of a rotary feedthrough in longitudinal section;

17 a partial longitudinal sectional view of an insert sleeve of in 16 shown non-rotating part of a rotary feedthrough;

18 an axial view of a rotary feedthrough;

19 a radial view of a rotary feedthrough;

20 in the representations a) to m), various types of sealing arrangements designed in the manner of piston seals;

21 in the representations a) to k) a plurality of sealing arrangements designed in the manner of rod seals.

The torsional vibration damper assembly 12 includes a primary page 20 which have a flexplate arrangement 22 o. The like. With the drive shaft 16 is coupled or can be coupled to the common rotation about the axis of rotation A. This primary page 20 in turn, includes a first displacement chamber assembly 24 that with two end walls 26 . 28 and an outer peripheral wall 30 a plurality of circumferentially successive displacement chambers 32 . 33 axially and radially outwardly limited. On the outside of the outer peripheral wall 30 is a with respect to the axis A star-shaped arrangement of balancing cylinders 34 provided, in each of which a compensation chamber 36 is formed. The assignment may be such that each displacement chamber 32 . 33 a compensation chamber 36 is assigned, or that of a displacement chamber 32 . 33 several equalization chambers 36 are assigned, or that a compensation chamber 36 with several displacement chambers 32 . 33 interacts. This interaction takes place via an assignment to each displacement chamber 32 . 33 provided passage opening 38 in the outer peripheral wall 30 and a circumferential direction along the outer peripheral wall 28 extending connecting chamber 40 , A respective one in the compensating cylinder 34 movable separating piston 42 separates this in the displacement chamber (s) 32 . 33 included first damper fluid that is substantially non-compressible and may be, for example, oil, from that in the associated compensation chamber 36 contained second damper fluid which is compressible, for example, may be air or other gas.

A secondary side 44 the torsional vibration damper assembly 12 includes a second displacement chamber assembly 46 which have a bearing 48 at the first displacement chamber assembly 24 is rotatably mounted. The second displacement chamber assembly 46 limits the displacement chambers 32 radially inward and is about corresponding sealing arrangements with respect to the side walls 26 . 28 guided fluid-tight.

Around the displacement chambers 32 . 33 in the circumferential direction are at the two displacement chamber assemblies 24 respectively. 46 each circumferentially extending projections extending radially toward the other displacement chamber assembly 60 . 62 provided so that each displacement chamber 32 by a peripheral limiting projection 60 the primary-side first displacement chamber assembly 24 is limited and a peripheral limiting projection 62 the secondary-side second displacement chamber assembly 46 is limited. With relative rotation of the primary side 20 with respect to the secondary side 44 in a first direction of relative rotation, for example, the volume of the in the 1 overhead displacement chamber 32 decreases, so that first damper fluid from this into the associated connection chamber 40 is displaced and the second damper fluid in one or more compensation chambers 36 is compressed while correspondingly increases the volume of another displacement chamber. When relative rotation in the opposite direction of relative rotation, the volume of the other displacement chamber is then reduced, so that the first damper fluid displaced from this second damper fluid in associated compensation chambers 36 loaded. It should be noted that, of course, the two displacement chamber assemblies 24 . 46 a plurality, for example, four circumferentially successive displacement chambers can limit, of which two act in parallel, so reduced or increased in volume at the same time.

For adjusting the damping characteristic or the pressure conditions of the first damper fluid in the displacement chambers 32 . 33 can this over in the 1 and 2 recognizable channels 49 . 50 supplied to first damper fluid or be deducted from these. This is still a generally with 52 designated rotary feedthrough, whose rotating part 54 in communication with the second displacement chamber assembly 46 , and its non-rotating part 56 , is in communication with a source of pressurized fluid for first damper fluid or a reservoir. By valve arrangements, not shown here, it can be ensured that in the various displacement chambers 32 . 33 the fluid pressure of the first damper fluid is increased or decreased, so that in this way the Dämpfungscharakteris tik can be influenced, as well as the biasing pressure, which the first damper fluid on the separating pistons 42 exerts and which on the principle held under pressure with respect to the environment second damper fluid in the compensation chambers 36 acts, is changeable.

The rotating part 54 the rotary union 52 is with a friction clutch as exemplified here as separating / starting element 58 connected for common rotation. For this purpose, the rotating part 54 and the friction clutch 58 in their axially opposite areas a toothing, for example in the manner of a Hirth toothing on. One through the friction clutch 58 radially inside clamping sleeve 66 holds together with one in the rotating part 54 the rotary union 52 screwed fastening bolts 68 the friction clutch 58 in rotation with the rotating part 54 ,

While previously referring to the 1 and 2 the basic structure of such a torsional vibration damper assembly 12 which operates on the principle of a gas spring dual-mass flywheel, has been described below, reference is made to various aspects of such a torsional vibration damper assembly and its construtive embodiment.

The 3 shows enlarged the rotary feedthrough 52 and the two displacement chamber assemblies 24 . 46 the torsional vibration damper assembly 12 , In particular, the 3 clearly indicate that the second displacement chamber assembly 46 and the rotating part 54 the rotary feedthrough are integrally formed, so an integral unit 70 form. This leads to the advantage that in the fluid guide of the rotary feedthrough 52 into the various displacement chambers 32 respectively. 33 can be dispensed with additional sealing measures at a joint.

In the 3 and 4 you realize that in this unit 70 one to the axis of rotation A coaxial and one in the 3 left lying, so motor-side end of this unit 70 open axial opening 72 is provided. In this axial opening 72 is an insert 74 used. This insert 74 also has a preferably coaxial to the axis of rotation A and axially extending opening 76 on. A closed end area 78 the opening 72 in the unit 70 nearby end area 80 of the insert part 74 ends at an axial distance to a ground area 82 the opening 72 , The axial opening 76 in the insert 74 is thus open to the axial opening 72 in the unit 70 , with axial distance to the ground area 82 ,

In between the floor area 82 and the axial end portion 80 of the insert part 74 formed space region open preferably a plurality of circumferentially successive connection openings 84 one, which is the rotating part 54 or the unit 70 essentially penetrate radially. Through these connection openings 84 is a connection created between the opening 72 in the unit 70 and a first fluid channel 86 providing axial opening 76 in the insert 74 , A first fluid connection 88 , which in the example shown a connection opening 90 is in the non-rotating part 56 the rotary union 52 trained and stands over the connection openings 84 in connection with the first fluid channel 86 ,

At the other axial end region 92 of the insert part 74 open into the first fluid channel 86 three substantially radially extending connection openings 94 one. The insert part 74 is in this axial end region 92 expanded and in a correspondingly enlarged area of the second displacement chamber assembly 46 used. At the outer peripheral portion of the disk-like extension 96 is a raidal externally open circumferential groove 98 provided in which the three connection openings 94 open out.

As the 7 This is shown in the second displacement chamber assembly 46 For example, two substantially radially extending connection openings 100 provided, which radially inward to the circumferential groove 98 are open and about this in conjunction with the connection openings 94 and thus the first fluid channel 86 stand. Radially outside are the two connection openings 100 open to the pairwise mutually associated displacement chambers, for example, the in 2 shown displacement chambers 32 which are here as a first group 102 be considered by displacement chambers. In this way, therefore, these two displacement chambers 32 the first group 102 over the connection openings 100 , the ring groove 98 , the connection openings 94 , the first fluid channel 86 So the axial opening 76 in the insert 74 , and the connection openings 84 in the rotating part 54 the pressure implementation 52 in connection with the connection opening 90 of the first fluid port 88 , Depending on whether this connection is associated with a source of pressurized first damper fluid or a reservoir for this first damper fluid, thus, the fluid pressure or the amount of fluid in the displacement chambers 32 the first group 102 be increased or reduced accordingly.

A second fluid channel 104 is between an outer peripheral surface 106 of the insert part 74 and an inner peripheral surface 108 the building unit 70 limited. The second fluid channel 104 extends near the axial end region 80 of the insert part 74 up to an axial region of an in 3 recognizable second fluid port 110 in the non-rotating part 56 the rotary union 52 , Also this second fluid connection 110 includes in the example shown a connection opening 112 ,

A plurality of distributed around the axis of rotation and approximately radially extending connection openings 114 connects the connection opening 112 with the second fluid channel 104 , To here a pressure fluid connection between the second fluid channel 104 and the first fluid channel 86 or between the insert part 74 and the floor 82 the axial opening 72 To prevent the formed area of space lies in the end area 80 the insert part 74 on the inner surface 108 the assembly 70 at. How to get in 5 recognizes is in this end area 80 the insert part 74 radially slightly expanded compared to that area in which it is also the second fluid channel 104 limited. In a radially outwardly open groove of the insert 74 is a trained example as an O-ring sealing element 116 intended. Complementary to the extension of the outer diameter of the insert 74 is the axial opening 72 in the unit 70 or her in the rotating part 54 lying area in the range of a slope 118 formed rejuvenating. This slope 118 allows the insertion of the with the sealing element 116 already equipped insert 74 without the sealing element 116 damaged at a sharp edge.

In his from the second fluid connection 110 remote end region is the second fluid channel 104 axially limited by the disc-like extension 96 of the insert part 74 , This extension 96 carries on an axial end face 120 in a circumferential groove a sealing element 122 on an opposite end face 124 the second displacement chamber assembly 46 the second fluid channel 104 tightly fitting.

How to get in 8th is in the region of the axial end of the second fluid channel 104 in the second displacement chamber assembly 46 a plurality of, here two, connection openings 126 intended. These lead radially outward from the second fluid channel 104 to the other two displacement chambers 33 here's a second group 128 form of displacement chambers. These two displacement chambers 33 the second group 128 So stand over the two connection openings 26 , the second fluid channel 104 and the connection openings 114 in fluid communication with the port 112 of the second fluid port 110 , Also, depending on whether this second fluid port 110 Ver in conjunction with a source of pressurized first damper fluid or a reservoir for this, the fluid pressure or the amount of fluid in these displacement chambers 33 increased or decreased.

A fixed holder of the insert 74 in the unit 70 becomes in the area of the disk-like extension 96 obtained. At a ring-like border area 130 between this disc-like extension 96 and a corresponding extension 132 the second displacement chamber assembly 46 can be done by welding a firm connection, which at the same time also a fluid-tight seal, in particular for the annular groove 98 generated. This area 130 is from the axially open end of the here gradually widening axial opening 72 in the unit 70 accessible. In another step-like extension 134 is then formed, for example, as a Loselager bearing 48 provided, which radially inward an axial projection 136 on the front wall 26 , so the first displacement chamber assembly 24 leads or centers. This camp 48 Can be used before or after the insert 74 in the axial opening 72 arranged therein initially held under axial pressure and then fixed by welding. The inner diameter of the bearing 48 may be larger than the disk-like extension 96 of the Einstzteils 74 but may be smaller, especially if this bearing 48 is introduced after the insert part 74 on the unit 70 was determined.

The various substantially radially extending communication openings in the assembly 70 , that is, in association with the first fluid channel 86 provided connection openings 84 and 100 or in association with the second fluid channel 104 provided connection openings 114 . 126 , can in the unit 70 be provided before the insert part 74 is used in this. Alternatively, it is also possible, first the insert part 74 insert and set and only then to produce the various connection openings by drilling. Due to the presence of the cone-like slope, for example 118 the axial opening 72 It is possible, for example, the connection openings 114 already provide before the insert part 74 is introduced, as a possible damage to the sealing element 116 leading interaction with the sharp-edged ends of the connection openings 114 can not save. Damage to this sealing element 116 when applied to the insert 74 can be avoided that this is tapered at its axial end.

In the embodiment described above acts on the insert 74 an axial pressure of the first damper fluid in the region of the second fluid channel 104 axial and motor side be bordering ring surface 138 , as well as in the area of the end area 80 formed and the first fluid channel 86 surrounding end face 140 , The on these two surfaces 138 . 140 acting fluid pressure loads the insert 74 in the direction of the opening 72 out. One on one face 142 at the radial extension of the insert 74 acting fluid pressure loads the insert in the opposite direction. So here at least a slight compensation takes place, so that the total of the insert part 74 in the direction of the engine, that is out of the opening 72 stressing out load not to overload the material connection of the insert part 74 with the unit 74 leads.

In order to achieve a sealed seal, especially in the transition between the rotating part 54 the rotary union and the non-rotating part 56 to receive the rotary feedthrough, as well as the 5 clearly shows, on both sides of the connection openings 84 respectively. 114 on the rotating part 54 in corresponding radially outwardly open circumferential grooves 144 sealing elements 146 used. These trained example as pressure seals sealing elements 146 lie radially outward on an inner surface of the non-rotating part 56 the rotary feedthrough, which is provided here by an insert sleeve 148 , This insert sleeve 148 points in the axial region of the fluid connections 88 . 110 each in 16 also recognizable radially inwardly open circumferential grooves 150 . 152 to which the connection openings 84 respectively. 114 are radially open. Like this the 17 shows, these circumferential grooves 150 . 152 in the insert sleeve 148 on both flanks with inclined surfaces 154 be provided when inserting the rotating part 54 in the insert sleeve 148 damage to the sealing elements 146 avoid sharp-edged steps.

In association with the two circumferential grooves 150 . 152 and to every connection opening 90 respectively. 112 is in the insert sleeve 148 a passage opening 156 respectively. 158 formed, which a connection between the respective connection opening 90 respectively. 112 and the associated circumferential groove 150 . 152 manufactures.

On both axial sides of the insert sleeve 148 is each a warehouse 158 respectively. 160 intended. This in particular in the presentation of 16 left, so recognizable bearings on the engine side 160 is designed as a floating bearing. The bearing located on the other axial side 158 is designed as a fixed bearing, so for example conventional ball bearing. Regarding the rotating part 54 is this camp 158 through a securing ring 162 on the one hand and a radial shoulder 164 on the other hand fixed axially. Regarding the non-rotating part 56 this camp is by a radial shoulder 166 and one to the non-rotating part 56 bolted disc-like closure element 168 axially fixed. About this camp 158 In essence, therefore, is also a defined positioning of the non-rotating part 56 the rotary union 52 with respect to the rotating part 54 and thus the assembly 70 specified.

About another in the 3 also recognizable bearing 170 is the primary side 20 or the front wall 28 the same radially supported on the unit 70 , For this purpose, the end wall 28 an annular axial extension 172 on that the camp 170 surrounds radially on the outside. This camp 170 that is axially adjacent to the already mentioned bearing 160 is positioned, is supported on the outer peripheral surface of the unit 70 from. Because except the camp 158 none of the other camps 48 . 160 . 170 is designed as a fixed bearing, these other camp 48 . 160 . 170 Thus, all as a floating bearing, such as needle roller bearings o. The like., Are formed, there is no over-determination in the axial positioning of the assembly 70 or the primary side 20 and the non-rotating part 56 the rotary union 52 , At the two axial ends of the non-rotating part 56 the rotary union 52 are more sealing elements 174 . 176 intended. The sealing element 174 is essentially between that on the non-rotating part 56 fixed conclusion element 168 and the outer peripheral surface of the rotating part 54 provided so that the bearing 158 between the axially last sealing element 146 and this sealing element 174 is arranged. It should be noted that the final element 168 via another example, O-ring-like sealing element 178 with respect to the non-rotating part 56 is tightly closed. The sealing element 176 is axial between the non-rotating part 56 and a further disc-like launcher attached thereto 180 held and is located radially on the annular cylindrical projection 172 the front wall 28 at. The warehouse 160 lies between this sealing element 176 and the next axially following of the sealing elements 146 ,

While the above-mentioned sealing elements 146 are formed substantially as pressure seals, the sealing elements 174 . 176 formed essentially as a flow rate seals. Above all, the pressure seals are designed to absorb the high pressure loads that occur in the area of the fluid connections 88 respectively. 110 prevalence. For this purpose, they put themselves under load of the high fluid pressure against the circumferential walls of the grooves supporting them 144 at. These can be provided for example by hard turning and subsequent axial grinding and complete Ausfeuern to achieve by appropriate surface quality excellent sealing effect. The sealing elements 146 Kings NEN be provided with a hydrodynamics in Reibkontaktbereich improved microstructuring.

In order to absorb the occurring fluid leaks, various drainage channels are provided which lead to a drainage connection 182 to lead. A drainage channel 184 also leads through the insert sleeve 148 through into the area between the two sealing elements 146 which is between the two annular grooves 150 . 152 in the insert sleeve 148 lie. A drainage channel 186 leads into the axial area between the bearing 160 and the immediately following sealing element 146 , A drainage channel 188 leads into the area between the two camps 160 . 162 extending radially outward through the sealing element 176 fluid-tight is completed and continues through a between the front wall 28 and the second displacement chamber assembly 46 acting example two-stage seal assembly 188 is sealed fluid-tight. It should be noted that a corresponding seal arrangement 188 also between the front wall 26 and the second displacement chamber assembly 46 can produce a fluid-tight seal. At the other axial end of the non-rotating part 56 the rotary union 52 leads a drainage channel 190 to the axial area between the bearing 158 and the immediately following sealing element 46 , A drainage channel 192 leads into the area between the camp 158 and the final element 168 , which is axially closed fluid-tight manner by the formed as a flow seal gasket 174 ,

How this particular the 3 and 16 show all these drainage channels through holes in the non-rotating part 56 and, if necessary, the insert sleeve 148 are provided, which are guided so as to be between the non-rotating part 56 and a drainage port 182 providing attachment part 194 formed space area 196 lead, which in turn to Drainageananschluss 182 is open. The drainage connection 182 can be brought into connection with a reservoir for the first damper fluid.

It should be noted that, of course, various variations are possible on the structure described above. For example, on the groove 98 in the disc-like extension 96 of the insert part 74 be omitted, in which case in association with each of the connection openings 100 for example, a connection opening 94 in the insert 74 is to be provided. However, then an exact circumferential alignment must be generated, which can be done by a positioning pin through the connection openings 100 . 94 is passed through, the insert 74 then set and then this pin is removed again. The setting of this insert part 74 can in addition to the already mentioned weld also by other material connection types, such. B. gluing, or by screwing done. The insert part can also be formed in several parts and joined in addition to the illustrated one-piece design.

In the area of the insert sleeve 148 is a variation z. As far as possible, as provided there circumferential grooves 150 . 152 also in the outer circumference of the rotating part 54 the rotary union 52 can be provided. The two fluid connections 88 . 110 or their connection openings 90 . 112 may differ from the illustrated axially aligned positioning circumferentially offset relative to each other. This makes it possible, while maintaining a sufficiently large wall thickness between them to realize a smaller axial distance and consequently also a smaller axial size.

The insert sleeve 148 can in the non-rotating part 56 For example, be introduced by pressing, wherein at its front end when inserting the insert sleeve may be tapered, as for example in the 17 at the left end of this insert sleeve 148 is recognizable. Accordingly, in the non-rotating part 56 trained and the insert sleeve 148 receiving opening may be formed radially widening at its end portion. The sealing elements provided as volume flow seals 174 . 176 can be designed as closed sealing lip geometries, which under bias on the rotating part 54 or the end wall 28 issue. In particular, they can also be designed as dry-running seals. In particular, where relative movements occur between different bearings or sealing elements of the components rotating relative to one another, the surfaces involved can be refinished by hoisting or in some other way in order to provide the corresponding surface quality or roughness requirements.

The 9 shows an alternative embodiment of the storage of the primary side 20 or the side wall 28 concerning the structural unit 70 , It can be seen here that on the end wall 28 in its radially inner end region an axially in some areas in a corresponding recess of the second displacement chamber assembly 46 engaging ring-like approach 198 is provided. Between this and an outer peripheral surface of the second displacement chamber assembly 46 or the unit 70 is now the camp 170 , Axially adjacent to this bearing acts between the end wall 28 and the unit 70 another Dichtele ment 200. as a volume flow seal, in particular in order to avoid leakage of fluid from the region of the displacement chambers. Another drainage channel 202 can from this area of storage, so the area of the warehouse 170 axially into the space between the bearing 160 and the sealing element 176 lead, which then over the in 3 for example, recognizable drainage channel 188 can be emptied.

An alternative embodiment of the insert 74 is in 10 shown.

You can see the unit here 70 with the axial opening formed therein 72 , In his end area 80 is the insert part 74 now axially completed and this end 80 lies in the representation of 10 on the right side of the connection openings 84 , To this in connection with the first fluid channel 86 to bring are in the axial region of the connection openings 84 in the insert 74 corresponding connection openings 204 educated. Between the end area 80 of the insert part 74 and the rotating part 54 acts another example, O-ring-like design sealing element 206 having the function substantially no first damper fluid in the region between the axial end portion 80 and the bottom wall 82 to get to. The sealing element 206 nevertheless overcoming first damper fluid can via a drainage channel 208 from this volume area toward one of the drainage channels in the non-rotating part 56 , in the 3 and also in 16 are clearly identifiable. In this way one becomes the insert part 74 axially loaded pressure of the first damper fluid avoided.

At its other axial end, the first fluid channel 86 through an axial opening 76 in the insert 74 final closure element 210 be completed.

A significant advantage of this embodiment is that the various axially loaded by the first damper fluid surfaces of the insert 74 are substantially equal in both axial directions. That is, the end surface loaded in an axial direction and formed of all the surfaces loaded in that direction, and the end surface loaded in the other axial direction formed of all those surfaces or surfaces are loaded in the other axial direction, compensate each other substantially, so that substantially none of the insert part 74 axially straining forces occur, especially the area in which the insert part 74 with the second displacement chamber assembly 46 firmly connected, relieved.

In this embodiment, it must be ensured that the connection openings 84 and 204 aligned with each other in Umfansgrichtung, can be proceeded so that these openings only after the introduction of the insert part 74 be drilled, during and after drilling drilling remains must be removed. Alternatively, the holes or openings may be previously provided, and may then be inserted into this plug or pins before the firm connection of the insert part 74 with the unit 70 the correct orientation are obtained.

Another alternative embodiment will be described below with reference to FIGS 11 and 12 described. In this case, there is a variation, especially in the embodiment of a connection between the fluid connections 88 and 112 with the different displacement chambers 32 . 33 producing fluid channels 86 . 104 , With regard to the construction in particular of the non-rotating part 56 the rotary union and also the first displacement chamber assembly 24 reference is made to the above statements.

Also in this embodiment, the unit 70 by an integral assembly of the second displacement chamber assembly 46 and the rotating part 54 the rotary union 52 educated. However, there is no insert part. The first fluid channel 86 , which connects between the fluid port 88 or the connection opening 90 same and the displacement chambers 32 the first group 102 is here formed with two substantially parallel and axially extending openings 212 respectively. 214 , These extend from one rotating part 54 radially completely penetrating connection opening 84 which radially outward to the circumferential groove 150 in the insert sleeve 148 is open until the other axial end of the assembly 70 and are there by tight final insert elements 216 . 218 , for example Königsexpander o. The like., tightly closed. In this axial region, in which also radially outward the displacement chambers 32 the first group 102 lie, goes from each of the openings 212 . 214 radially outward a connection opening 220 . 222 out, which in each case one of the displacement chambers 32 opens.

The second connection channel 104 is how this is the 12 also provided by two substantially axially extending openings 224 . 226 in the unit 70 , These go out axially from a connection opening 114 in the axial region of the second fluid port 112 which the rotating part 54 completely penetrated radially and into the circumferential groove 152 of the insert part 148 opens. In their other axial end are the openings 224 . 226 again through completion elements 228 . 230 , for example, also Königsexpander, o. The like., Completed fluid-tight. Again, there are connection openings 232 . 234 radially outward and thus provide a connection of the openings 224 . 226 with the displacement chambers 33 the second group 128 ago.

How to get the representation of 13 can be seen, are the four axial opening 212 . 214 . 224 . 226 arranged so as to be evenly distributed about the axis of rotation A, so have substantially the same radial distance to this and each have an angular distance of about 90 °, each based on their longitudinal center line, on. In each case an axial opening of the first fluid channel 86 follows an axial opening of the second fluid channel 104 , so that overall the axial openings forming the same fluid channel have an angular spacing of approximately 180 ° relative to each other.

A modification of this design principle is in the 14 and 15 shown. One recognizes in particular in 15 again four arranged around the axis of rotation and axially extending openings 224 . 226 . 236 . 238 , which radially outward via connection openings 114 again in communication with the second fluid port 112 , All these axial openings now together form the second fluid channel 104 , In the center, so for example formed coaxially to the axis of rotation, is again the axial opening 76 , which the first fluid channel 86 forms and in its transmission-side axial end via connection openings 84 radially outward to the first fluid port 88 is open. In its engine end, the first fluid channel opens 86 in a chamber 240 by a closure element which is designed as a screw plug, as a king expander or as a material connection such as welding or gluing 242 is completed. In this chamber 240 open the connection openings, not shown here 220 . 222 of the 11 one leading to the two displacement chambers 32 the first group 102 to lead. The four axially extending openings 224 . 226 . 236 . 238 the second fluid channel 104 are closed at their motor-side axial end again by closure elements, such as Königsexpander o. The like., Of which in 14 the Elements 228 . 230 the openings 224 . 226 are shown. The openings 224 . 226 . 236 . 238 the second fluid channel 104 stand over in the 14 then unrecognizable, substantially radially extending connection openings in connection with the displacement chambers 33 the second group 128 , wherein it can be provided here, for example, that in each case two of the axial openings 224 . 226 . 236 . 238 lead to one of the Verdindungskammer.

The 18 and 19 essentially show the non-rotating part 56 the rotary union 52 with the fluid connections provided thereon 88 . 112 and the drainage port 182 , In order to have information about the fluid conditions in the different flow regions in the rotational operation or vibration damping operation, these are different connections 88 . 112 . 182 sensors 244 . 246 . 248 assigned. These sensors can be designed to detect the pressure in the various openings or connections or alternatively or additionally to detect the volume flow of the medium flowing through a respective opening. It goes without saying that such sensors need not be provided in association with all terminals, or that different types of sensors may be provided in association with different terminals. For example, in association with the two fluid connections 88 . 112 in each case a pressure sensor may be provided while in association with the drainage connection 182 a volumetric flow sensor can be provided.

In the 20 and 21 Various types of sealing elements are shown which, for example, provide a tight seal between the rotating part 54 the rotary union 52 and the insert part 74 can act. It should be noted that such sealing elements, which may in principle be constructed in several parts, of course, in other close relative to each other to be closed areas of the Torsionsschwingungsdämpferanordnung described in detail above 12 can act, for example, as the sealing elements 146 ,

The 20 shows a variety of variants of such sealing elements, for example, for the sealing element 116 , which has already been explained above, which are designed as so-called piston seals. That is, the sealing element 116 itself is in the area of the insert part 74 or a circumferential depression provided therein 250 arranged. Basically, these sealing elements act with an elastically active biasing element 252 , which relate to the insert part 74 supports and a generally ring-like sealing body 254 against the inner surface of the non-rotating part 54 biases. The biasing element 252 may be formed, for example, as a metal or rubber spring, and the sealing body may be formed as a plastic sealing ring o. The like. In addition, it is possible, such as in 20c shown, on both sides of the sealing body support rings 256 provided. In principle, such sealing elements 116 also be constructed so that, as for example in 20f It can be seen that the prevailing pressure of the fluid also places a load on the sealing body 254 against through this generated surface to be contacted.

In the 21 shown design variants are designed according to the nature of so-called rod seals. So here is a circumferential recess 250 in the non-rotating part 54 provided and thus also the sealing element, such as the sealing element 116 , at this non-rotating part 54 intended. An elastic biasing element, so for example again metal or rubber spring 252 loads a ring-like sealing body 254 then against the outer peripheral surface of the insert 74 , Basically, the same design variants can be used here as they are in 20 are recognizable.

Claims (36)

Torsional vibration damper assembly comprising a primary side ( 20 ) and against the action of a damper fluid arrangement about an axis of rotation (A) with respect to the primary side ( 20 ) rotatable secondary side ( 44 ), wherein the damper fluid arrangement comprises two groups of displacement chambers filled with first damper fluid of lower compressibility (US Pat. 32 . 33 ) each having at least one displacement chamber ( 32 . 33 ) and in association therewith at least one compensating chamber filled with a second damper fluid of higher compressibility (US Pat. 36 ), wherein upon rotation of the primary side ( 20 ) with respect to the secondary side ( 44 ) first damper fluid from the at least one displacement chamber ( 32 . 33 ) one of the groups is displaced and thereby the second damper fluid in at least one compensation chamber ( 36 ) is compressed, the displacement chambers ( 32 . 33 ) through a primary-side displacement chamber assembly ( 24 ) and a secondary-side displacement chamber assembly ( 46 ) and wherein one of the displacement chamber assemblies ( 24 . 46 ) an assembly ( 70 ) with a rotating part ( 54 ) a rotary feedthrough ( 52 ), through which rotary feedthrough ( 52 ) via a first fluid connection ( 88 ) in a non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 32 ) of a first group ( 102 ) is guided by displacement chambers and via a first fluid connection ( 88 ) at least axially offset second fluid port ( 110 ) in the non-rotating part of the rotary union ( 52 ) first damper fluid from and to the at least one displacement chamber ( 33 ) of a second group ( 128 ) is guided by displacement chambers, wherein in the assembly ( 70 ) an axial opening ( 72 ) and therein an insert part ( 74 ) are provided, wherein the insert part ( 74 ) a first fluid channel ( 86 ) for connecting the first fluid port ( 88 ) with the at least one displacement chamber ( 32 ) of the first group ( 102 ) and a second fluid channel ( 104 ) for connecting the second fluid port ( 110 ) with the at least one displacement chamber ( 33 ) of the second group ( 128 ) limited. Torsionsschwingungsdämpferanordnung according to claim 1, characterized in that in the axial region of the fluid connections ( 88 . 110 ) in the rotating part ( 54 ) of the rotary feedthrough ( 52 ) at least one connection opening ( 84 ) between the first fluid port ( 88 ) and the first fluid channel ( 86 ) and at least one connection opening ( 114 ) between the second fluid port ( 110 ) and the second fluid channel ( 104 ) are provided. Torsionsschwingungsdämpferanordnung according to claim 1 or 2, characterized in that the second fluid channel ( 104 ) the first fluid channel ( 86 ) at least partially surrounds. Torsional vibration damper arrangement according to claim 3, characterized in that the first fluid channel ( 86 ) at least one substantially axially in the insert part ( 74 ) extending opening ( 76 ). Torsional vibration damper arrangement according to claim 4, characterized in that the first fluid channel ( 86 ) in the axial region of the first fluid port ( 88 ) to the axial opening ( 72 ) in the assembly ( 70 ) is open. Torsional vibration damper arrangement according to one of claims 3 to 5, characterized in that the second fluid channel ( 104 ) between an outer peripheral surface ( 106 ) of the insert part ( 74 ) and an inner peripheral surface ( 108 ) of the assembly ( 70 ) is formed. Torsionsschwingungsdämpferanordnung according to claim 6, characterized in that in a region between the first fluid connection ( 88 ) and the second fluid port ( 110 ) a fluid-tight seal between the insert part ( 74 ) and the assembly ( 70 ) is formed. Torsional vibration damper arrangement according to one of claims 1 to 7, characterized in that in association with each displacement chamber ( 32 ) of the first group ( 102 ) in the assembly ( 70 ) at least one connection opening ( 100 ) between this and the first fluid channel ( 86 ) and that in association with each displacement chamber ( 33 ) of the second group ( 128 ) in the assembly ( 70 ) at least one connection opening ( 126 ) between this and the second fluid channel ( 104 ) is provided. Torsionsschwingungsdämpferanordnung according to claim 4 and claim 8, characterized in that at one in the axial region of the Verdrän chambers ( 32 . 33 ) end portion of the insert part ( 74 ) at least one to the axially extending opening ( 76 ) in the insert part ( 74 ) and with the at least one displacement chamber ( 32 ) of the first group ( 102 ) associated with at least one connection opening ( 100 ) in the assembly ( 70 ) communicating connection opening ( 94 ) is provided. Torsional vibration damper arrangement according to one of claims 1 to 9, characterized in that the insert part ( 74 ) in his in the area of the displacement chambers ( 32 . 33 ) lying end portion of the assembly ( 70 ) is determined by material connection. Torsionsschwingungsdämpferanordnung according to one of claims 1 to 10, characterized in that the first fluid channel ( 86 ) and fluid flow areas in the insert part ( 74 ) and / or the second fluid channel ( 104 ) in a first axial direction through a first end face of the insert part (FIG. 74 ) are limited and in a second axial direction by a second end face of the insert part ( 74 ) and that the size of the first end surface is substantially equal to the size of the second end surface. Torsional vibration damper assembly comprising a primary side ( 20 ) and against the action of a damper fluid arrangement about an axis of rotation (A) with respect to the primary side ( 20 ) rotatable secondary side ( 44 ), wherein the damper fluid arrangement comprises two groups of displacement chambers filled with first damper fluid of lower compressibility (US Pat. 32 . 33 ) each having at least one displacement chamber ( 32 . 33 ) and in association therewith at least one compensating chamber filled with a second damper fluid of higher compressibility (US Pat. 36 ), wherein upon rotation of the primary side ( 20 ) with respect to the secondary side ( 44 ) first damper fluid from the at least one displacement chamber ( 32 . 33 ) one of the groups is displaced and thereby the second damper fluid in at least one compensation chamber ( 36 ) is compressed, the displacement chambers ( 32 . 33 ) through a primary-side displacement chamber assembly ( 24 ) and a secondary-side displacement chamber assembly ( 46 ) and wherein one of the displacement chamber assemblies ( 24 . 46 ) an assembly ( 70 ) with a rotating part ( 54 ) a rotary feedthrough ( 52 ), through which rotary feedthrough ( 52 ) via a first fluid connection ( 88 ) in a non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 32 ) of a first group ( 102 ) is guided by displacement chambers and via a first fluid connection ( 88 ) at least axially ver set second fluid connection ( 110 ) in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 33 ) of a second group ( 128 ) is guided by displacement chambers, wherein in the assembly ( 70 ) between the axial region of the displacement chambers ( 32 . 33 ) and the axial region of the first fluid port ( 88 ) a plurality of substantially axially extending openings ( 224 . 226 . 236 . 238 ) is provided, which are radially offset with respect to the axis of rotation (A) and have an angular distance from one another. Torsionsschwingungsdämpferanordnung according to claim 12, characterized in that the angular distance W1 is substantially defined by W1 = 360 ° / n1, where n1 is the number of openings ( 224 . 226 ; 236 . 238 ). Torsional vibration damper arrangement according to claim 12 or 13, characterized in that each opening ( 224 . 226 ; 236 . 238 ) in its in the axial region of the second fluid port ( 110 ) end region via at least one connection opening ( 114 ) to the second fluid port ( 110 ) is open and in its in the axial region of the displacement chambers ( 32 . 33 ) end region via at least one connection opening ( 232 . 234 ) to the at least one displacement chamber ( 33 ) of the second group ( 128 ) is open. Torsionsschwingungsdämpferanordnung according to any one of claims 12 to 14, characterized in that in the structural unit ( 70 ) between the axial region of the displacement chambers ( 32 . 33 ) and the axial region of the first fluid port ( 88 ) a substantially axially extending fluid channel ( 86 ) is provided. Torsional vibration damper arrangement according to claim 15, characterized in that the fluid channel ( 86 ) is provided substantially coaxially with the axis of rotation. Torsional vibration damper arrangement according to claim 15, characterized in that a plurality of openings ( 212 . 214 ) of the fluid channel is provided, which are offset radially to the axis of rotation (A) and have an angular distance from one another. Torsionsschwingungsdämpferanordnung according to claim 17, characterized in that the angular distance W2 is substantially defined by W2 = 360 ° / n2, where n2 is the number of openings ( 212 . 214 ). Torsionsschwingungsdämpferanordnung according to claim 12 and claim 17 or 18, characterized in that in the circumferential direction openings ( 212 . 214 ) of the fluid channel ( 86 ) and openings ( 224 . 226 ) alternate each other. Torsionsschwingungsdämpferanordnung according to claim 13 and claim 18 and claim 19, characterized in that the angular distances between circumferentially successive openings ( 212 . 214 . 224 . 226 ) are the same size. Torsionsschwingungsdämpferanordnung according to claim 15 or any one of claims 16 to 20, when dependent on claim 15, characterized in that the fluid channel ( 86 ) in its in the axial region of the first fluid port ( 88 ) end region via at least one connection opening ( 84 ) to the first fluid port ( 88 ) is open and its in the axial region of the displacement chambers ( 32 . 33 ) end region via at least one connection opening ( 220 . 221 ) to at least one connecting chamber ( 32 ) of the first group ( 102 ) is open. Torsional vibration damper assembly comprising a primary side ( 20 ) and against the action of a damper fluid arrangement about an axis of rotation (A) with respect to the primary side ( 20 ) rotatable secondary side ( 44 ), wherein the damper fluid arrangement comprises two groups of displacement chambers filled with first damper fluid of lower compressibility (US Pat. 32 . 33 ) each having at least one displacement chamber ( 32 . 33 ) and in association therewith at least one compensating chamber filled with a second damper fluid of higher compressibility (US Pat. 36 ), wherein upon rotation of the primary side ( 20 ) with respect to the secondary side ( 44 ) first damper fluid from the at least one displacement chamber ( 32 . 33 ) one of the groups is displaced and thereby the second damper fluid in at least one compensation chamber ( 36 ) is compressed, the displacement chambers ( 32 . 33 ) through a primary-side displacement chamber assembly ( 24 ) and a secondary-side displacement chamber assembly ( 46 ) and wherein one of the displacement chamber assemblies ( 24 . 46 ) an assembly ( 70 ) with a rotating part ( 54 ) a rotary feedthrough ( 52 ), through which rotary feedthrough ( 52 ) via a first fluid connection ( 88 ) in a non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 32 ) of a first group ( 102 ) is guided by displacement chambers and via a first fluid connection ( 88 ) at least axially ver set second fluid connection ( 110 ) in the non-rotating part ( 56 ) of the rotary feedthrough first damper fluid from and to the at least one displacement chamber ( 33 ) of a second group ( 128 ) is guided by displacement chambers, wherein the fluid connections ( 88 . 110 ) in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) at least one connection opening ( 90 . 112 ) and wherein no connection opening ( 90 ) of the first fluid port ( 88 ) in axial alignment with a connection opening ( 112 ) of the second fluid port ( 110 ) lies. Torsional vibration damper assembly comprising a primary side ( 20 ) and against the action of a damper fluid arrangement about an axis of rotation (A) with respect to the primary side ( 20 ) rotatable secondary side, wherein the damper fluid arrangement comprises two groups of displacement chambers filled with first damper fluid of lower compressibility ( 32 . 33 ) each having at least one displacement chamber ( 32 . 33 ) and in association therewith at least one compensating chamber filled with a second damper fluid of higher compressibility (US Pat. 36 ), wherein upon rotation of the primary side ( 20 ) with respect to the secondary side ( 44 ) first damper fluid from the at least one displacement chamber ( 32 . 33 ) one of the groups is displaced and thereby the second damper fluid in at least one compensation chamber ( 36 ) is compressed, the displacement chambers ( 32 . 33 ) through a primary-side displacement chamber assembly ( 24 ) and a secondary-side displacement chamber assembly ( 46 ) and wherein one of the displacement chamber assemblies ( 24 . 46 ) an assembly ( 70 ) with a rotating part ( 54 ) a rotary feedthrough ( 52 ), through which rotary feedthrough ( 52 ) via a first fluid connection ( 88 ) in a non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 32 ) of a first group ( 102 ) is guided by displacement chambers and via a first fluid connection ( 88 ) offset second fluid port ( 110 ) in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 33 ) of a second group ( 128 ) is guided by displacement chambers, wherein in the non-rotating part ( 56 ) of the rotary feedthrough a firmly connected with this insert sleeve ( 148 ) is provided, the inner peripheral surface of an outer peripheral surface of the rotating part ( 54 ) of the rotary feedthrough ( 52 ) is opposite. Torsionsschwingungsdämpferanordnung according to claim 23, characterized in that in association with at least one fluid connection ( 88 . 110 ) in the inner peripheral surface of the insert sleeve ( 148 ) and / or the outer peripheral surface of the rotating part ( 54 ) of the rotary feedthrough ( 52 ) a circumferential groove ( 150 . 152 ) is provided, in which at least one connection opening ( 90 . 112 ) of a fluid connection ( 88 . 110 ) or a Verbindungsöff tion ( 84 . 114 ). Torsional vibration damper assembly comprising a primary side ( 20 ) and against the action of a damper fluid arrangement about an axis of rotation (A) with respect to the primary side ( 20 ) rotatable secondary side ( 44 ), wherein the damper fluid arrangement comprises two groups of displacement chambers filled with first damper fluid of lower compressibility (US Pat. 32 . 33 ) each having at least one displacement chamber ( 32 . 33 ) and in association therewith at least one compensating chamber filled with a second damper fluid of higher compressibility (US Pat. 36 ), wherein upon rotation of the primary side ( 20 ) with respect to the secondary side ( 44 ) first damper fluid from the at least one displacement chamber ( 32 . 33 ) one of the groups is displaced and thereby the second damper fluid in at least one compensation chamber ( 36 ) is compressed, the displacement chambers ( 32 . 33 ) through a primary-side displacement chamber assembly ( 24 ) and a secondary-side displacement chamber assembly ( 46 ) and wherein one of the displacement chamber assemblies ( 24 . 46 ) an assembly ( 70 ) with a rotating part ( 54 ) a rotary feedthrough ( 52 ), through which rotary feedthrough ( 52 ) via a first fluid connection ( 88 ) in a non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 32 ) of a first group ( 102 ) is guided by displacement chambers and via a first fluid connection ( 88 ) offset second fluid port ( 110 ) in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 33 ) of a second group ( 128 ) is guided by displacement chambers, wherein in one of the axial region of the displacement chambers ( 32 . 33 ) further away from the first axial end portion of the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) the rotating part of the rotary feedthrough via a first bearing arrangement ( 158 ) is mounted and in an axial region of the displacement chambers ( 32 . 33 ) closer to the second axial end portion of the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) the rotating part ( 54 ) of the rotary feedthrough ( 52 ) via a second bearing arrangement ( 160 ), wherein one of the bearing arrangements ( 158 . 160 ) includes a floating bearing. Torsional vibration damper arrangement according to claim 25, characterized in that the second bearing arrangement ( 160 ) includes a floating bearing. Torsional vibration damper arrangement according to claim 23 or 24 and claim 25 or 26, characterized in that the bearing arrangements ( 158 . 160 ) axially adjacent to the insert sleeve ( 148 ) are provided. Torsional vibration damper assembly comprising a primary side ( 20 ) and against the action of a damper fluid arrangement about an axis of rotation (A) with respect to the primary side ( 20 ) rotatable secondary side ( 44 ), wherein the damper fluid arrangement comprises two groups of displacement chambers filled with first damper fluid of lower compressibility (US Pat. 32 . 33 ) each having at least one displacement chamber ( 32 . 33 ) and in association therewith at least one compensating chamber filled with a second damper fluid of higher compressibility (US Pat. 36 ), wherein upon rotation of the primary side ( 20 ) with respect to the secondary side ( 44 ) first damper fluid from the at least one displacement chamber ( 32 . 33 ) one of the groups is displaced and thereby the second damper fluid in at least one compensation chamber ( 36 ) is compressed, the displacement chambers ( 32 . 33 ) through a primary-side displacement chamber assembly ( 24 ) and a secondary-side displacement chamber assembly ( 46 ) and wherein one of the displacement chamber assemblies ( 24 . 46 ) an assembly ( 70 ) with a rotating part ( 54 ) a rotary feedthrough ( 52 ), through which rotary feedthrough ( 52 ) via a first fluid connection ( 88 ) in a non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 32 ) of a first group ( 102 ) is guided by displacement chambers and via a first fluid connection ( 88 ) offset second fluid port ( 110 ) in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 33 ) of a second group ( 128 ) of displacement chambers, wherein the other displacement chamber assembly ( 24 ) two end walls ( 26 . 28 ) at an axial distance from each other and thus firmly connected to a peripheral wall ( 30 ) and the end walls ( 26 . 28 ) in each case via a bearing arrangement ( 48 . 170 ) with regard to the structural unit ( 70 ) are stored. Torsional vibration damper arrangement according to claim 28, characterized in that the bearing arrangements ( 48 . 170 ) Include floating bearings. Torsional vibration damper arrangement according to claim 28 or 29, characterized in that the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) nearer end wall ( 28 ) a substantially cylindrical approach ( 172 ; 198 ), on which one of the bearing assemblies is radially supported. Torsional vibration damper arrangement according to claim 30, characterized in that between the cylindrical projection ( 172 ) and the assembly ( 70 ) a fluid seal ( 200. ) and that in the space between the fluid seal ( 200. ) and the bearing assembly ( 170 ) a Draina channel ( 202 ). Torsional vibration damper assembly comprising a primary side ( 20 ) and against the action of a damper fluid arrangement about an axis of rotation (A) with respect to the primary side ( 20 ) rotatable secondary side ( 44 ), wherein the damper fluid arrangement comprises two groups of displacement chambers filled with first damper fluid of lower compressibility (US Pat. 32 . 33 ) each having at least one displacement chamber ( 32 . 33 ) and in association therewith at least one compensating chamber filled with a second damper fluid of higher compressibility (US Pat. 36 ), wherein upon rotation of the primary side ( 20 ) with respect to the secondary side ( 44 ) first damper fluid from the at least one displacement chamber ( 32 . 33 ) one of the groups is displaced and thereby the second damper fluid in at least one compensation chamber ( 36 ) is compressed, the displacement chambers ( 32 . 33 ) through a primary-side displacement chamber assembly ( 24 ) and a secondary-side displacement chamber assembly ( 46 ) and wherein one of the displacement chamber assemblies ( 24 . 46 ) a structural unit with a rotating part ( 54 ) a rotary feedthrough ( 52 ), through which rotary feedthrough ( 52 ) via a first fluid connection ( 88 ) in a non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 32 ) of a first group ( 102 ) is guided by displacement chambers and via a first fluid connection ( 88 ) offset second fluid port ( 110 ) in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 33 ) of a second group ( 128 ) is guided by displacement chambers, wherein on both sides of the first fluid port ( 88 ) and the second fluid port ( 110 ) each have a first fluid seal ( 146 ) between the non-rotating part ( 56 ) of the rotary union and the rotating part ( 54 ) of the rotary feedthrough ( 52 ) and at both end portions of the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) between this and the assembly ( 70 ) or the other displacement chamber assembly ( 24 ) each have a second fluid seal ( 174 . 176 ), wherein in each case between two successive fluid seals ( 146 . 174 . 176 ) formed in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) provided drainage channel ( 184 . 186 . 188 . 190 ), wherein the drainage channels ( 184 . 186 . 188 . 190 ) with a drainage connection ( 182 ) in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) keep in touch. Torsional vibration damper arrangement according to claim 32, characterized in that the first fluid seals ( 146 ) Pressure seals are. Torsionsschwingungsdämpferanordnung according to claim 32 or 33, characterized in that the second fluid seals ( 174 . 176 ) Are volume flow seals. Torsional vibration damper assembly comprising a primary side ( 20 ) and against the action of a damper fluid arrangement about an axis of rotation (A) with respect to the primary side ( 20 ) rotatable secondary side ( 44 ), wherein the damper fluid arrangement comprises two groups of displacement chambers filled with first damper fluid of lower compressibility (US Pat. 32 . 33 ) each having at least one displacement chamber ( 32 . 33 ) and in association therewith at least one compensating chamber filled with a second damper fluid of higher compressibility (US Pat. 36 ), wherein upon rotation of the primary side ( 20 ) with respect to the secondary side ( 44 ) first damper fluid from the at least one displacement chamber ( 32 . 33 ) one of the groups is displaced and thereby the second damper fluid in at least one compensation chamber ( 36 ) is compressed, the displacement chambers ( 32 . 33 ) through a primary-side displacement chamber assembly ( 24 ) and a secondary-side displacement chamber assembly ( 46 ) and wherein one of the displacement chamber assemblies ( 24 . 46 ) an assembly ( 70 ) with a rotating part ( 54 ) a rotary feedthrough ( 52 ), through which rotary feedthrough ( 52 ) via a first fluid connection ( 88 ) in a non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 32 ) of a first group ( 102 ) is guided by displacement chambers and via a first fluid connection ( 88 ) offset second fluid port ( 110 ) in the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) first damper fluid from and to the at least one displacement chamber ( 33 ) of a second group ( 128 ) is guided by displacement chambers, wherein in association with at least one of the fluid connections ( 88 . 110 ) and / or a drainage connection ( 182 ) of the non-rotating part ( 56 ) of the rotary feedthrough ( 52 ) a sensor arrangement ( 244 . 246 . 248 ) is provided for pressure detection and / or volume flow detection. Torsional vibration damper arrangement according to one of the preceding claims, characterized in that the one of the displacement chamber assemblies ( 24 . 46 ) and the rotating part ( 54 ) of the rotary feedthrough ( 52 ) are integrally formed to provide the assembly.