DE102008008508A1 - Torsional vibration damper for the drive train of a vehicle - Google Patents

Abstract

A torsional vibration damper comprises a primary side (12) and a secondary side (14) rotatable against the action of a damper assembly with respect to the primary side (12) about an axis of rotation (A), the damper assembly comprising at least one gas spring assembly (18, 20) with pressurizable fluid Gas volume (98) and at least one Druckfluidverdrängungskammer (22, 22 ', 24, 24'), whose volume in relative rotation of the primary side (12) with respect to the secondary side (14) is variable, further comprising a rotary feedthrough (38) for the supply / discharge of Pressurized fluid and a position control valve arrangement (72) in the pressure fluid flow path between the rotary union (38) and the at least one pressure fluid displacement chamber (22, 22 ', 24, 24'), the position control valve assembly (72) being dependent on the relative rotational position of the primary side (12) with respect to Secondary side (14) the at least one pressure fluid displacement chamber (22, 22 ', 24, 24') with a Druckflui dzuleitungsbereich (68) of the rotary feedthrough (38) connects or connects with a Druckfluidzugsitungsbereich (70) of the rotary feedthrough (38).

Description

The The present invention relates to a torsional vibration damper comprising a primary page and one against the action of a damper assembly with respect to primary about a rotation axis rotatable secondary side, wherein the damper assembly at least one gas spring assembly comprises one by pressurized fluid acted upon gas volume and at least one pressure fluid displacement chamber, whose volume can be changed relative to the secondary side when the primary side is rotated relative to one another is. In such a torsional vibration damper, a rotary feedthrough is further provided, to pressurized fluid to the at least one pressure fluid displacement chamber to be able to conduct the at least one gas spring arrangement or to derive from this.

Such a torsional vibration damper is in circuit diagram-like representation in 1 shown. The generally constructed in the form of a dual mass flywheel torsional vibration damper 10 comprises a schematically indicated primary side 12 and one upon occurrence of torque fluctuations or in the torque transmission with respect to the primary side 12 rotatable or movable secondary side 14 , This relative rotation takes place against the return action of a damper assembly 16 , which in the example shown two gas spring arrangements 18 . 20 includes. The gas spring arrangement 18 has a pressure fluid displacement chamber 22 on. The gas spring arrangement 20 In a corresponding manner, a pressure fluid displacement chamber 24 on. In relative rotation of the primary side with respect to the secondary side, for example in the 1 when shifting the secondary side 14 concerning the primary side 12 to the right, the volume of the pressure fluid displacement chamber decreases 22 the gas spring assembly 18 , wherein by the displacement of the pressurized fluid 22 a non-illustrated gas volume is compressed, for example, via a piston or a membrane of the pressurized fluid of the gas spring assembly 18 ge is disconnected. Upon relative movement in the opposite direction, the volume of the pressure fluid displacement chamber decreases 24 and accordingly, a gas volume of the gas spring assembly becomes 20 compressed.

The relative movement between the primary side 12 and the secondary side 14 is via a Wegsensoranordnung 26 detects their signals in a control device 28 for the torsional vibration damper 10 be directed. This is over a connecting line 30 also in conjunction with an engine control unit.

The control device 28 controls two pressure control valves 32 . 34 at. The pressure control valve 32 is above a pressure fluid line 36 , a rotary union 38 and another in the rotating system area of the torsional vibration damper 10 arranged pressure fluid line 40 in conjunction with the pressure fluid displacement chamber 24 the gas spring assembly 20 , In a similar way is the pressure control valve 34 via a pressure fluid line 42 , the rotary union 38 and one in the rotating system area of the torsional vibration damper 10 existing pressure fluid line 44 in conjunction with the pressure fluid displacement chamber 22 the gas spring assembly 18 , Depending on the control state connect the pressure control valves 32 . 34 via the respective pressure fluid lines or the rotary feedthrough 38 the associated pressure fluid displacement chambers 24 . 22 with a fluid pump 46 and a fluid reservoir 48 comprehensive source of pressurized fluid 50 or a respective return area 52 respectively. 54 via which a return of fluid into the fluid reservoir 58 can be done. The fluid reservoir 48 and the return areas 52 . 54 are kept essentially unpressurized.

By the targeted adjustment of the pressure fluid supply or pressure fluid discharge to / from the pressure fluid displacement chambers 24 . 22 becomes possible to be active on the vibration damping characteristic of the torsional vibration damper 10 act. For example, that of the pressure fluid displacement chambers 24 . 22 , which is reduced by occurring torques in their volume, by means of the respective associated Druckregelven tils 32 respectively. 34 with the source of pressurized fluid 50 while the other is connected to the respective return areas 52 . 54 is switched substantially depressurized.

A problem with such systems is the comparatively high driving effort for the two pressure control valves 32 . 34 both outside the rotating system range of the torsional vibration damper 10 lie.

It Therefore, the object of the present invention to provide a torsional vibration damper to provide with simplified structure or reduced driving effort.

According to the invention, this object is achieved by a torsional vibration damper comprising a primary side and a secondary side rotatable against the action of a damper arrangement with respect to the primary side about an axis of rotation, wherein the damper arrangement comprises at least one gas spring arrangement with a gas volume to be acted upon by pressurized fluid and at least one pressure fluid displacement chamber, the volume of which during relative rotation the primary side is variable with respect to the secondary side, further comprising a rotary feedthrough for the supply / discharge of pressurized fluid, characterized by a Lageregelventilanordnung in Druckfluidströmungsweg between the rotary feedthrough and the at least one pressure fluid displacement chamber, wherein in dependence on the relative rotational position of the primary side relative to the secondary side by the Lageregelventilanordnung the at least one pressure fluid displacement chamber with a feed region of the rotary feedthrough or with a discharge region of the rotary feedthrough is connectable.

By providing the bearing valve assembly in the rotating system area the torsional vibration damper, So between the rotary feedthrough and the pressure fluid displacement chambers will it be possible in which to the rotary feedthrough subsequent non-rotating system area with only one pressure control valve too work, or to provide a different design, the only for it must ensure that a defined fluid pressure is provided or can be maintained. This simplifies the driving effort as well as the design effort.

Around in the torsional vibration damper according to the invention in both relative directions of rotation by compression of a gas volume generated damping property to be able to provide It is suggested that the damper assembly at least one first gas spring arrangement and associated therewith at least a pressurized fluid displacement chamber includes, wherein the gas volume of the first gas spring assembly in relative rotation of the primary in terms of the secondary side in a first relative direction of rotation through the at least one Pressure fluid displacement chamber the compressed compressed fluid displaced the first gas spring assembly is assigned, and at least one second gas spring assembly and this at least one pressure fluid displacement chamber comprising, wherein the gas volume of the second gas spring assembly upon relative rotation the primary side in terms of the secondary side in a second relative to the first relative direction of rotation Relative direction of rotation by the at least one pressure fluid displacement chamber the second gas spring assembly compressed compressed fluid compressed becomes.

there may preferably be further provided that the position control valve arrangement then, if they have the at least one pressure fluid displacement chamber the first gas spring assembly connects to the discharge region of the rotary duct, the at least one pressure fluid displacement chamber of the second gas spring assembly connects to the supply area of the rotary feedthrough, and then if they are the at least one pressure fluid displacement chamber of the second gas spring arrangement connects to the discharge area of the rotary feedthrough, the at least a pressurized fluid displacement chamber the first gas spring assembly connects to the supply area of the rotary feedthrough.

at in a neutral relative rotational position with respect to each other primary and secondary side can all pressure fluid displacement chambers be completely completed by the position control valve assembly. alternative Is it possible, in that in a neutral relative rotational position with respect to each other primary and secondary side the position control valve assembly all Druckfluidverdrängungskammern connects to the supply area of the rotary feedthrough. To this Way is for that ensured that in all pressure fluid displacement chambers equal pressure conditions prevail as this for the Neutral relative rotational position can also be provided. Nevertheless, possible Fluid leaks in the range of with respect to each other movable components may occur, be compensated.

Around at deflection of the primary side in terms of the secondary side starting from a neutral relative rotational position a gradual Pressure increase in the corresponding pressurized pressure fluid displacement chambers to ensure, It is proposed that with relative rotation of the primary side with respect to secondary side starting from a neutral relative rotational position of the primary side with respect to secondary side a connection flow area provided in the position control valve assembly for supplying / removing pressurized fluid to / from the at least one pressure fluid displacement chamber progressively increases.

For example The structure may be such that the position control valve arrangement with the primary side or the secondary side rotatable valve cylinder and one in the valve cylinder during relative rotation the primary side in terms of the secondary side movable Includes valve slide.

Around in particular, the construction of the rotary feedthrough for To simplify the supply or removal of pressurized fluid is further proposed that the valve cylinder or the valve slide a rotatable Part of the rotary union forms.

at an embodiment variant according to the invention the valve cylinder can be rotatable with the primary side and the Valve slide can be a rotatable with the secondary side rotary valve be.

It should be noted in this context that in general the primary side of such a torsional vibration damper is the side which is rotatably coupled to a drive unit, such as the crankshaft of an internal combustion engine, while the secondary side then forms that system area, which is a connection to the drive train following system che, such as B. a transmission input shaft or a friction clutch, provides. Of course, another assignment of the primary side or the secondary side to the various system areas of a drive train is possible.

In the rotary valve can at least a part of the supply line and the discharge area of the rotary feedthrough.

Around the supply area of the rotary feedthrough in connection with the at least one pressure fluid displacement chamber to be able to bring proposed that in the rotary valve at least one radially open first feed opening of the supply area is formed and in the valve cylinder at least one to a formed the rotary valve receiving cylinder opening open second feed opening is, further in the secondary side one leading away from the at least one pressure fluid displacement chamber feed is formed, depending on from the relative rotational position of the primary side in terms of the secondary side over the at least one second feed opening in communication with the at least one first feed opening can be brought.

Around for the gradual Increase in pressure when making the connection, it is proposed that the at least one second feed opening and / or the at least a first feed opening an end profile is limited, which in relative rotation of the primary side with respect to Secondary side starting from the neutral relative rotational position a progressive increase the overlap the at least one first feed opening with which generates at least one second feed opening.

To the Enable the fluid discharge from the at least one pressure fluid displacement chamber proposed that in the rotary valve at least one radially open first discharge opening of the discharge area is formed and in the valve cylinder at least one to a formed the rotary valve receiving cylinder opening open second discharge opening is, further in the secondary side one leading away from the at least one pressure fluid displacement chamber discharge channel is formed, depending on from the relative rotational position of the primary side in terms of the secondary side over the at least one second discharge opening in connection with the at least one first discharge opening can be brought.

The Design of the rotary valve may be such that in the rotary valve a substantially axially extending lead portion is provided, which over the at least one first feed opening radially it is open that in the rotary valve a substantially axially extending discharge section is provided, which over the at least one first discharge opening radially open is, and that the supply line section and the discharge section not in communication with each other. In particular, it is possible that the supply line section and the discharge section in the direction follow the axis of rotation of the torsional vibration damper successive.

Especially then when the torsional vibration damper in both directions of relative rotation with gas spring return characteristic should be designed, it is advantageous if in the valve cylinder in Assignment to each pressure fluid displacement chamber of the first gas spring assembly and in association with each pressure fluid displacement chamber of the second gas spring assembly provided a second feed opening is. It is also possible in the valve cylinder associated with each pressure fluid displacement chamber the first gas spring arrangement or the second gas spring arrangement provided a second discharge opening is. This can be realized, for example, by the fact that in the valve cylinder one of the number of Druckfluidverdrängungskammern the first gas spring arrangement or the number of pressure fluid displacement chambers the second gas spring arrangement corresponding number of second discharge openings is provided and that depending from the relative rotational position of the primary side in terms of the secondary side the pressure fluid displacement chambers the first gas spring assembly or the pressure fluid displacement chambers the second gas spring assembly via the second discharge openings in connection with the first discharge openings can be brought.

at an alternative embodiment variant of the torsional vibration damper according to the invention is suggested that the valve cylinder rotatable with the secondary side and the valve spool is in a cylinder opening of the valve cylinder slidable in the direction of the axis of rotation and against rotation relative to the Valve cylinder locked valve piston is.

Around to be able to obtain the displacement of the valve piston, it is suggested that on the primary side a cam member is provided which moves with the valve piston the same cooperates in relative rotation of the primary side with respect to the secondary side.

The defined return of the Valve piston can be obtained by the fact that the valve piston biasing a biasing member in a first axial direction is and through the cam member in a second axial direction is displaceable against the biasing action of the biasing member.

there is then advantageously provided that the biasing element in a limited by the valve piston and the valve cylinder Chamber is arranged and that in the chamber accumulated fluid via a drainage channel is deductible.

In the valve piston can at least a part of the supply area and the discharge area the rotary union be formed.

Around the supply of pressurized fluid to the at least one pressurized fluid displacement chamber to be able to gain It is proposed that in the valve piston at least one radial open first feed opening formed in that at least one second feed opening is formed in the valve cylinder is which over a connection channel in communication with the at least one pressure fluid displacement chamber is, and that in dependence from the relative rotational position of the primary side in terms of the secondary side the extent of the overlap the at least one first feed opening with the at least one second feed opening changeable is.

Likewise for obtaining the pressure fluid discharge from the at least one pressure fluid displacement chamber be provided that in the valve cylinder at least a first Discharge opening provided is which over the connection channel in communication with the at least one pressure fluid displacement chamber in that at least one second discharge opening is provided in the valve cylinder is, which is in connection with a discharge section of the rotary feedthrough, and that at least one bypass channel is provided in the valve piston, in dependence from the relative rotational position of the primary side in terms of the secondary side a connection between the at least one first discharge opening and the at least produces a second Abführöffung.

Of the Torsional vibration damper according to the invention can be constructed such that when Relaitvdrehung the primary side with respect to the secondary side either a connection between the at least one first feed opening and the at least one second feed opening can be produced is or over the bypass channel a connection between the at least one first discharge opening and the at least one second discharge opening can be produced is.

Around thereby the progressive, thus increasing increase of the fluid pressure or the Druckfluidzuführmenge to be able to provide It is further proposed that the at least one first feed opening and / or the at least one second feed opening with is formed such Endprofile that during relative rotation of the primary in terms of the secondary side starting from a neutral relative rotational position, the extent of overlap the at least one first feed opening with the at least one second feed opening progressive increases.

Around also in such a configuration of the position control valve arrangement in generate two relative directions of rotation a gas spring damping characteristic to be able to It is further proposed that the at least one pressure fluid displacement chamber of the first gas spring arrangement over a connection channel in connection with at least one second Feed opening is and the at least one pressure fluid displacement chamber of the second gas spring assembly via a Connecting channel in conjunction with at least one other second Feed opening is, and that in dependence from the relative position of the primary side in terms of the secondary side by moving the valve piston, the at least one first supply opening in coverage with the at least one second feed opening or at least another second feed opening can be brought is.

Further For example, the structure may be such that the at least one pressure fluid displacement chamber the first gas spring assembly over the connecting channel in connection with at least one first Abführöffnung is and the at least one pressure fluid displacement chamber of the second gas spring assembly via the Connecting channel in conjunction with at least one other second Discharge opening is, and in that the at least one first discharge opening has an at least second one Discharge opening and a bridging channel are assigned and the at least one further first discharge opening at least another second discharge opening and another connection channel are assigned.

The both sides, ie to both directions of relative rotation, effective damping characteristics can be generated, for example, by shifting of the valve piston in a first displacement direction, starting from the neutral relative rotational position of the primary side with respect to the secondary side the at least one first feed opening in Connection with the at least one second feed opening occurs and at least another first discharge opening over the further bypass channel in Connection with the at least one further second discharge opening occurs and that upon displacement of the valve piston in one of the first Displacement direction opposite second direction of displacement starting from the neutral relative rotational position of primary in terms of the secondary side the at least one first feed opening in Connection with the at least one further second feed opening occurs and the at least one first discharge opening via the bypass passage in communication with the at least one second discharge opening occurs.

at an alternative type of flow guidance can be provided that when the at least one first feed opening in Connection with the at least one further second feed opening, the at least one second feed opening via a bridging channel is in connection with a discharge opening, and when the at least one first feed opening coincides with the at least one a second feed opening, the at least one further second feed opening via a further discharge opening a drainage channel is in communication.

Around in the torsional vibration damper according to the invention for generating the damping force required pressure for To provide the pressurized fluid, it is proposed that one in connection with the supply area of the rotary feedthrough or bringable pressure fluid source is provided. This preferably comprises a pressure fluid pump with a pressure fluid pump drive.

Of the Pressure fluid pump may be associated with a pressure accumulator. The one in one Accumulator stored energy can, if necessary, so at spontaneously occurring relative rotations between the primary side and Secondary side, be released spontaneously, so that without delays, which occur, for example, until the start of a pressure fluid pump would occurring rotational irregularities can be counteracted quickly.

Farther it can be provided that the pressure fluid pump is a pressure limiting valve arrangement is assigned to limit the on an output side of the pressure fluid pump existing pressure fluid pressure to a default value. Such Pressure relief valve arrangement ensures that the at a Pressure fluid pump output side, so applied to the feed line of the rotary feedthrough Pressure can not exceed a certain maximum value, so that on the one hand, defined resetting conditions guaranteed on the other hand by an overly high Fluid pressure generated damage various system components can be avoided.

One to unnecessary Energy losses leading permanent operation of the pressure fluid pump or the pressure fluid pump drive With high front efficiencies can be avoided that the Eligibility of the Pressure fluid pump in dependence the pressure fluid pressure existing at an exit side of the pressure fluid pump is changeable. This means that if the output side of the pressure fluid pump existing pressure fluid pressure increases, corresponding to the delivery capacity of the pressure fluid pump decreases, so that, for example, the pressure fluid pump only in Pressure fluid promoting and correspondingly pressure increasing Way is effective when this is actually required.

This can be realized, for example, that the Druckfluidpum PE at least one funding agency whose conveying effect dependent on changeable by the pressure fluid pressure is.

The Provision of the pressure fluid pump with a in its conveying effect changeable conveying member is particularly advantageous when the pressure fluid pump drive a vehicle drive unit comprises. In this case, ultimately, without any operational changes at the pressure fluid pump drive, namely to make the drive unit of a vehicle, the delivery behavior to be influenced. As a result, then, if so, too is not required, no unnecessary drive power from the drive unit is tapped to activate the pressure fluid pump.

at a further embodiment variant can be provided that the pressure fluid pump drive in response to the pressure fluid pressure activatable and deactivatable and / or in its driving effect is variable.

For this It is particularly advantageous if the pressure fluid pump drive a Electric drive motor includes the pressure-dependent, so switched, for example by a pressure switch, on or off or in his Speed is set.

According to the present The invention is further a generic or with the foregoing described features constructed torsional vibration damper so formed, that the at least one pressure fluid displacement chamber a primary-side Displacement chamber assembly and a secondary-side Displacement chamber assembly is limited, wherein the primary-side displacement chamber assembly comprises two end walls and a peripheral wall, and wherein the secondary side Displacement chamber assembly or a subsequent to this rotating part of the rotary union one of the end walls interspersed, this end wall a having annular axial shoulder, wherein at the Axialansatz a bearing radially supported is over which either the primary side in terms of a non-rotating part of the rotary union or with respect to secondary Extrusion chamber assembly or of the rotating part of the rotary feedthrough is mounted.

To avoid overdetermination in the axial positioning, it is proposed that the bearing is a floating bearing.

The Integration of such a torsional vibration damper in a drive system can be particularly easy to do that the rotating part of the rotary feedthrough has a form-fitting engagement formation, preferably Hirth gearing, for torque-transmitting coupling with a having the following module.

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

1 a circuit-like representation of a known torsional vibration damper;

2 one of the 1 corresponding representation of a torsional vibration damper according to the invention;

3 a simplified cross-sectional view of a torsional vibration damper with gas spring damper assembly;

4 a longitudinal sectional view of a torsional vibration damper according to the invention of a first embodiment;

5 a perspective view of the primary side of the torsional vibration damper of 4 ;

6 a perspective view of the secondary side of the torsional vibration damper of 4 ;

7 a perspectively considered cross-sectional view of the torsional vibration damper of 4 , cut in a plane VII-VII in 4 ;

8th a perspectively considered cross-sectional view of the in 4 shown torsional vibration damper, cut in a plane VIII-VIII in 4 ;

9 one of the 7 corresponding representation in a deflection state of the primary side with respect to the secondary side;

9a one of the 8th corresponding representation in the deflection state;

10 a perspective, partially sectioned view of a torsional vibration damper according to the invention according to a second embodiment variant;

11 a perspectively considered longitudinal sectional view of the torsional vibration damper of 10 ;

12 a view of a cam element and a valve piston comprising assembly;

13 a perspective view of the cam member;

14 a further perspective view of the cam member;

15 a perspective view of a rotation lock for the valve piston;

16 a longitudinal sectional view of the torsional vibration damper of 10 in a first relative rotational state of the primary side with respect to the secondary side;

17 a longitudinal sectional view of the torsional vibration damper of 10 , in a second relative rotational state of the primary side with respect to the secondary side with respect to the representation of 16 opposite relative direction of rotation;

18 one of the 10 corresponding view of a modification of the second embodiment variant;

19 one of the 2 corresponding representation of a modified embodiment of a torsional vibration damper according to the invention;

20 one of the 2 corresponding representation of a modified embodiment of a torsional vibration damper according to the invention;

21 one of the 2 corresponding representation of a modified embodiment of a torsional vibration damper according to the invention.

The 2 shows in circuit diagram representation of a torsional vibration damper constructed according to the invention 10 , This includes two gas spring arrangements 18 . 20 , wherein the gas spring arrangement here two pressure fluid displacement chambers 22 . 22 ' includes and the gas spring assembly 20 the two pressure fluid displacement chambers 24 . 24 ' includes. With relative rotation of the primary side 12 with respect to the secondary side 14 in a first direction of relative rotation, the volumes of the pressure fluid displacement chambers 22 . 22 ' the gas spring assembly 18 decreases with appropriate compression and reduction of the volume of these pressure fluid displacement chambers 22 . 22 ' associated Gasvo lumina of the gas spring assembly 18 , Upon relative rotation in the opposite direction, the volumes of the pressure fluid displacement chambers become 24 . 24 ' decreases, with the result that the pressure fluid displacement chambers 24 . 24 ' associated gas volumes of the gas spring assembly 20 be compressed.

In the non-rotating system area is only a single pressure control valve 60 provided that under control of the drive device 28 stands. The pressure control valve 60 is in two positions can be brought, in which a pressure fluid line 62 that to the rotary union 38 leads, either in conjunction with the source of pressurized fluid 50 , or with a return area 64 is. The pressure in the pressure fluid line 62 is by a pressure sensor 66 detects its signal in the drive device 28 is fed. Based on this pressure signal controls the drive device 28 the pressure control valve 60 such that in the pressure fluid line 62 a defined fluid pressure can be adjusted. A fluid line 66 connects the rotary union 38 with the fluid reservoir 48 , This has the consequence that the rotary feedthrough 38 basically a supply area 68 provides, so this is the area that also has a connection of the pressure fluid line 62 with a defined fluid pressure generated by the interaction of the pressure control valve 60 with the source of pressurized fluid 50 , provides. A derivation area 70 the rotary union 38 is essentially depressurized, as it passes over the fluid line 67 in conjunction with the also pressureless fluid reservoir 48 is.

In the rotating system area of the torsional vibration damper 10 is a common with 72 designated position control valve provided. This position control valve 72 So it turns with the primary page 12 or the secondary side 14 about an axis of rotation of the torsional vibration damper 10 , The position control valve 72 has one in the 2 only schematically indicated valve cylinder 74 and in this movable a valve spool 76 on. By a dashed line indicated mechanical coupling of the valve cylinder 74 or the valve spool 76 with the primary side 12 and the secondary side 14 can be a relative movement between the valve cylinder 74 and Ven valve slide 76 be obtained. This has the consequence that, depending on the position of the position control valve 76 , either the two pressure fluid displacement chambers 22 . 22 ' in connection with the supply area 68 while the pressure fluid displacement chambers 24 . 24 ' in connection with the discharge area 70 or, conversely, the pressure fluid displacement chambers 24 . 24 ' in connection with the supply area 68 while the pressure fluid displacement chambers 22 . 22 ' in connection with the discharge area 70 are or the pressure fluid displacement chambers 22 . 22 ' . 24 . 24 ' essentially completely closed against fluid exchange, that is substantially none of the pressure fluid displacement chambers 22 . 22 ' . 24 . 24 ' in connection with the discharge area 70 is or in connection with the supply area 68 is. The latter condition is generally reached when the primary side 12 in a neutral rotational position with respect to the secondary side 14 is, so z. B. substantially no torque over the torsional vibration damper 10 is transmitted. The other two states, in which each one of the gas spring arrangements 18 respectively. 20 associated pressure fluid displacement chambers 22 . 22 ' respectively. 24 . 24 ' in connection with the supply area 68 are states in which the primary side 12 with respect to the secondary side 14 is deflected in each one of the possible relative directions of rotation.

With such a torsional vibration damper 10 the driving effort can be significantly reduced while simplifying the hydraulic circuit. The position control valve 72 becomes automatic without any control measures solely by the mechanical coupling with the primary side 12 or the secondary side 14 a defined fluid supply or fluid discharge to the respective gas spring arrangements 18 . 20 to adjust. It then only has to be arranged by the only pressure control valve arranged outside the rotating system area 60 be taken care that at the supply area 68 a defined fluid pressure is provided, which of course also depends on the operating state of such a torsional vibration damper 10 or also by the driving state or the driving state of a vehicle can be varied.

In the following, various design variants of a torsional vibration damper 10 or in particular a position control valve 72 described.

A first embodiment variant is in the 3 to 9 shown. At first one recognizes in the representation of the 3 the basic structure of the torsional vibration damper 10 with the primary side 12 and the secondary side 14 , The primary side 12 is with two axially spaced disc parts 80 . 82 constructed radially outward by a cylindrical wall 84 connected, for example, with the disc part 80 can be integrally formed. From this cylindrical wall 84 extend with an angular distance of 180 ° two partitions 86 . 86 ' radially inward.

The secondary side 14 comprises a substantially cylindrically shaped component 88 , which is essentially in the primary side 14 is inserted and at its outer periphery with an angular distance of 180 ° two radially outwardly spaced partitions 90 . 90 ' having. The dividing walls 86 . 86 ' . 90 . 90 ' are each configured or dimensioned so that they each directly to the outer peripheral surface 92 or to the inner peripheral surface 94 the other module from the primary side 12 and secondary side 14 extend. Through these dividing walls 86 . 86 ' . 90 . 90 ' is the one between the wall 84 and the cylindrical component 88 formed annular space divided into four chambers. These four chambers are the pressure fluid displacement chambers 22 . 22 ' the first gas spring assembly 18 respectively. 24 . 24 ' the second gas spring assembly 20 , It can be seen that the respective pressure fluid displacement chambers assigned to a gas spring arrangement are also conditioned by the partitions arranged in each case at an angular distance of 180 ° 86 . 86 ' . 90 . 90 ' are diametrically opposite each other and, for example, in a neutral relative rotational position with respect to each other arranged primary side 12 and secondary side 14 may have the same circumferential extent.

The gas spring arrangements 18 . 20 include outside around the cylindrical wall 84 distributes a plurality of approximately radially extending cylinders 96 , Part of these cylinders 96 is the first gas spring arrangement 18 assigned while the remaining part of the second gas spring assembly 20 assigned. In each of the cylinders 96 is a schematically indicated gas volume 98 included by a separator 99 for example one in a cylinder 96 displaceable piston, is separated from the pressure fluid of those pressure fluid displacement chamber or pressure fluid displacement chambers, with which a respective cylinder 96 interacts. So can all of the first gas spring assembly 18 associated cylinder 96 with both pressure fluid displacement chambers 22 . 22 ' cooperate, ie, via respective connecting chambers with these in conjunction, while correspondingly all cylinders 96 the second gas spring assembly 20 with all pressure fluid displacement chambers 24 . 24 ' can interact. Of course, it is also possible, each pressure fluid displacement chamber own gas volumes 98 or cylinder 96 assigned, which are then acted upon only by the pressure fluid in this respective pressure fluid displacement chamber. The with the or the pressure fluid displacement chambers of a respective gas spring assembly 18 respectively. 20 interacting gas volumes 98 then form the "gas volume" loaded when a respective gas spring arrangement takes effect or the spring characteristic unfolds.

With relative rotation of the primary side 12 with respect to the secondary side 14 starting from the in 3 Neutral-relative rotational position shown so are, for example, the volumes of the pressure fluid displacement chambers 22 . 22 ' thereby reducing that the dividing walls 86 and 90 ' approach each other, as well as the dividing walls 86 ' and 90 , That from the pressure fluid displacement chambers 22 . 22 ' then displaced fluid loaded via the connecting chambers, not shown, then in the associated cylinders 96 enclosed gas volumes 98 under appropriate compression of the same. By the compression of these gas volumes, a restoring force is generated, so that with increasing deflection from the neutral relative rotational position and an increasing restoring force is generated. The same is done in association with the pressure fluid displacement chambers 24 . 24 ' with relative rotation of the opposite direction. In the central area of the torsional vibration damper 10 is the position control valve 72 arranged. Its structure or function will be described below with reference to the 4 to 9 explained in detail.

One recognizes in the 4 the valve spool 76 of the position control valve 72 that with the essentially cylindrical component 88 the secondary side 14 firmly connected, that is rotatable with this about the rotation axis A. Correspondingly, the valve cylinder 74 with the primary side 12 , here the disc part 80 firmly connected and thus with the primary side 12 rotatable. The valve spool 76 , so the rotary valve, at the same time forms part of the rotary feedthrough 38 namely, a radially inner and with the torsional vibration damper 10 rotating part. In the 4 you can see the supply area on the right 68 the rotary union 38 , lying on the left in the non-illustrated part of the valve spool 76 a corresponding embodiment for the discharge area 70 can be provided. A feeder section 98 is as a central bore or opening in the valve spool 76 educated. Near the axial end of the valve spool 76 is this supply area 98 over openings 100 open radially outward. Axial on both sides of these openings 100 sealing elements may be provided which have a substantially fluid-tight closure of these openings or corresponding openings in a non-rotating part of the rotary feedthrough 38 to generate. Axial then to the supply area 98 For example, is also coaxial with the axis of rotation A in the valve spool 76 a derivation section 102 educated. This can also be open radially not shown through openings, in order to connect via a connection with a likewise non-rotating part of the rotary feedthrough 38 then a connection to the fluid line 66 to manufacture in 2 is shown. Between the supply line section 98 and the derivation section 102 there is a partition wall 104 providing a direct flow of pressurized fluid from the supply area 68 to the derivation area 70 prevented.

At his inside the valve cylinder 76 lying end portion is the lead portion 98 as well as in 7 recognizes two arranged at an angular distance of 180 ° to each other and radially outwardly open first feed openings 106 . 106 ' open radially outward. In the valve cylinder 74 are four second feed ports 108 . 108 ' . 108 '' and 108 ''' intended. These four second feed openings 108 . 108 ' . 108 '' and 108 ''' are arranged with respect to each other so that in the in 7 Also shown neutral relative rotational position of the secondary side 14 concerning the primary side 12 no connection or overlap between the first feed openings 106 . 106 ' and the second feed openings 108 . 108 ' . 108 '' and 108 ''' consists.

In the secondary side or the cylindrical component 88 the same are four supply channels 110 . 110 ' . 110 '' and 110 ''' intended. Each of these feeder channels 110 . 110 ' . 110 '' and 110 ''' leads to one of the pressure fluid displacement chambers 22 . 22 ' . 24 . 24 ' , For example, assume that the feed channel 110 to the pressure fluid displacement chamber 22 leads, the feed channel 110 '' to the pressure fluid displacement chamber 22 ' leads, the feed channel 110 ' to the pressure fluid displacement chamber 24 leads and the feed channel 110 ''' to the pressure fluid displacement chamber 24 ' leads. These feed channels 110 . 110 ' . 110 '' and 110 ''' are radially inward to a valve cylinder 74 in the component 88 receiving coaxial opening 112 open while the second feed openings 108 . 108 ' . 108 '' and 108 ''' radially inward to a valve spool 76 receiving coaxial opening 114 in the valve cylinder 76 are open.

The 8th shows the torsional vibration damper 10 of the 3 and 4 cut in another to the rotation axis A orthogonal plane. One recognizes in 8th in the valve spool 76 the discharge section 102 , which here over four with an angular offset of 180 ° to each other arranged radially open first discharge openings 116 . 116 ' . 116 '' and 116 ''' radially outward, so to the cylinder opening 114 is open. In the valve cylinder 74 are two arranged with an angular distance of 180 ° second discharge openings 118 . 118 ' intended. At the in 8th recognizable neutral relative rotational position of the primary side 12 with respect to the secondary side 14 are the first discharge openings 116 . 116 ' . 116 '' and 116 ''' with respect to the two second discharge openings 118 . 118 ' arranged so that there is no overlap and thus no fluid exchange can take place.

In the cylindrical component 88 the secondary side 14 are four discharge channels 120 . 120 ' . 120 '' and 120 ''' intended. These discharge channels 120 . 120 ' . 120 '' and 120 ''' are each in communication with one of the pressure fluid displacement chambers. For example, the discharge channel 120 the pressure fluid displacement chamber 22 be assigned, the discharge channel 120 '' can the pressure fluid displacement chamber 22 ' be assigned, the discharge channel 120 ' can the pressure fluid displacement chamber 24 be assigned and the discharge channel 120 ''' can the pressure fluid displacement chamber 24 ' be assigned.

In the in the 7 and 8th shown relative positioning of the primary side 12 with respect to the secondary side 14 , which also the in 3 represented relative positioning corresponds, so there is neither at the feed 68 a connection of the pressure fluid line 62 with any of the pressure fluid displacement chambers 22 . 22 ' . 24 . 24 ' , There is still a connection of any of the pressure fluid chambers 22 . 22 ' . 24 . 24 ' with the fluid line 66 at the discharge area 70 , Twists in torque transmission or torsional vibration, the primary side 12 with respect to the secondary side 14 in a first direction of relative rotation, for example, at the feed area 68 the in 9 recognizable condition occur. It can be seen here that the valve cylinder 74 and with this the primary side with respect to the secondary side 14 has rotated counterclockwise. This causes the pressure fluid displacement chambers 22 . 22 ' have been compressed or reduced in volume and that further the first feed openings 106 . 106 ' with the second feed openings 108 . 108 '' cover while the second feed openings 108 ' and 108 ''' are still closed. In this state, so the Zuführabschnitt 98 of the feed area 68 the rotary union 38 over the first feed openings 106 . 106 ' , the second feed openings 108 . 108 '' and the feed channels 110 . 110 '' in conjunction with the pressure fluid displacement chambers 22 . 22 ' , which in this way in connection with the pressure fluid line 62 stand. It can thus by appropriate control of the pressure control valve 60 also the pressure of the pressure fluid in these pressure fluid displacement chambers 22 . 22 ' be further increased, which causes an increased "spring stiffness" and a correspondingly increased restoring force in the direction of the neutral relative rotational position 9a recognizable, equally in the discharge area 70 an overlap of the second discharge openings 118 . 118 ' with the first discharge openings 116 ' . 116 ''' adjust so that via the discharge channels 120 ' and 120 '' the pressure fluid displacement chambers 24 . 24 ' in connection with the fluid line 66 and thus the pressureless fluid reservoir 48 stand.

With the position control valve 72 So it is possible, depending on the relative direction of rotation of the primary side 12 with respect to the secondary side 14 optionally, a connection of the source of pressurized fluid 50 with the pressure fluid displacement chambers 22 . 22 ' the first gas spring assembly 18 or the pressure fluid displacement chambers 24 . 24 ' the second gas spring assembly 20 to be generated by this Connection is then ensured in each case that a defined return takes place in the neutral relative rotational position.

In the neutral relative rotational position, as already shown, all pressure fluid displacement chambers 22 . 22 ' . 24 . 24 ' completed by not existing overlap of the various feed openings. At the beginning of deflection from the neutral rotary position a pressure surge by spontaneously establishing the connection with the pressure fluid source 50 to avoid are, as in 7 recognizable, the second feed openings 108 . 108 ' . 108 '' and 108 ''' each with by bevels or bevels 122 profiled edges limited. When deflecting these chamfering occur first 122 in overlap with the first feed openings 106 . 106 ' , so that initially only a small, gradually increasing connection cross-section, which ensures a gradual increase in pressure, while only at larger angles of rotation then a greater increase of the connecting cross-section is generated. It is of course possible, by a variety of profiling of the second feed openings 108 . 108 ' . 108 '' . 108 ''' limiting walls in making the cover with the first supply openings 106 . 106 ' to ensure a defined progressive course of the connection cross-section. It goes without saying that a correspondingly progressive profile of the connecting cross-section can also be achieved by shaping the walls delimiting the first feed openings.

In an alternative variant, it may be provided that in the neutral relative rotary position a slight overlap of the first connection openings 106 . 106 ' with all second connection openings 108 . 108 ' . 108 '' . 108 ''' consists. Thus, then lies at all pressure fluid displacement chambers 22 . 22 ' . 24 . 24 ' the pressure of the pressurized fluid source 50 at. This ensures that the neutral relative rotational position can be reliably maintained as long as only small torques or torque fluctuations occur. Furthermore, the maintenance of a defined fluid pressure is ensured, even if leakages occurring in interspaces cause a permanent fluid outflow in the direction of the discharge area 70 is available. Upon deflection from the neutral relative rotational position then takes the overlap of the first feed openings 106 . 106 ' with two opposite of the second feed openings 108 . 108 ' . 108 '' and 108 ''' to, while the first remaining coverage with the other two second supply ports decreases or is reduced to zero.

The coordination of the flow or connection cross sections at the feed area 68 and at the discharge area 70 successive may be such that upon deflection from the neutral relative rotational position initially only one connection of the respective first supply openings is generated with the second supply ports, while the first discharge openings are not yet brought into overlap with the second discharge openings at the discharge. Only when reaching a predetermined relative rotation angle can then also the overlaps at the discharge 70 to be generated. It can also be ensured in principle that the flow cross section at the discharge area 70 is smaller than that at the feed area 68 ,

If the fluid pressure is too low in the pressure fluid displacement chambers reduced in their relative rotation in their volume, or if the torques or torque fluctuations that occur are too great, so that a very strong relative rotation is generated with corresponding increase in volume of the respective other pressure fluid displacement chambers, it may well be that in the discharge area 70 a reverse fluid flow occurs, ie via this or the fluid line 66 Fluid is sucked in to increase the volume, which is then no longer due to corresponding increase in volume of gas volumes 98 the associated cylinder 96 can be compensated to ensure.

An alternative embodiment of the torsional vibration damper according to the invention 10 or the position control valve 72 will be described below with reference to the 10 to 17 described. Here, corresponding components are also denoted by the same reference numeral with the addition of an appendix "a".

In the in the 10 to 17 shown embodiment is the valve cylinder 74a of the position control valve 72a firmly connected to the secondary side for common rotation. The valve spool 76a is designed here as in the direction of the axis of rotation A displaceable valve piston and in the valve cylinder 74a formed opening 114a displaceable. With the primary side 12a or the disc part 80a connected for common rotation is a cam member 130a that with the valve spool 76a interacts with its displacement. This assembly is in 12 shown enlarged.

You can see the cam element 130a with in 13 and in 14 also visible cam surfaces 132a . 134a , With a circular disc-like body section 136a is the cam element 130a in a corresponding recess of the primary side 12a recorded, in such a way that it basically with this primary page 12a is rotatable by inserting a tool into a tool receiving recess 138a , For example, a Allen opening, but is rotatable for adjusting the positioning.

The valve spool 76a has an axial extension 140a on, with the two cam surfaces 136a . 138a cooperates or rests on these. Furthermore, this extension 140a , which is rectangular in cross-section, through a corresponding recess 142a one in 15 shown disc-like locking element 144a passed. This locking element 144a is in the opening 114a the valve cylinder is received such that there is an axial displacement of the valve spool 76a but this does not allow itself in the valve cylinder 76a can twist. One turn of the one with the primary side 12a non-rotatable cam element 130a with respect to the secondary side 14a and thus the thus rotatable assemblies valve cylinder 74a and valve spool 76a Thus, when looking at the 10 or also the 11 a shift of the valve spool 76a in the direction of the axis of rotation result. To make sure that the extension 140a permanently in contact with the cam surfaces 136a . 138a is, is between a ground 146a of the valve cylinder 74a and an axial end surface 148a of the valve spool 76a an Indian 10 indicated biasing spring element 150a for example in the form of a helical compression spring. This biasing spring element 150a clamps the valve spool 76a in the direction of the cam element 130a before, allowing a relative rotation of the primary side 12a with respect to the secondary side 14a in a first relative direction of rotation, a displacement of the valve spool 76a in a first displacement direction with respect to the valve cylinder 74a causes and causes a relative rotation in the opposite direction relative rotation according to a shift in the opposite direction of displacement.

In the valve spool 76a is in the central region a substantially axially extending feed section 98a educated. This is about radial openings 100a to a circumferential groove 152a open so that the corresponding openings in the valve cylinder 74a lie opposite and thus a fluid supply via the rotary feedthrough 38a allow. One recognizes in the 10 that the valve cylinder 74a with its outer peripheral region a part of the rotary feedthrough, in particular of the feed region 68a , provides.

Axially offset to the openings 110a points the valve spool 76a radially outwardly open first supply openings 106a on, in one on the outer circumference of the valve spool 76a provided circumferential groove 154a are open radially outward.

At the valve cylinder 74a are at axial distance from each other and distributed over the circumference second feed openings 108a respectively. 108a ' intended. In the 11 recognizable neutral relative rotational position are the first feed openings 106a or the circumferential groove 154a positioned such that there are essentially no overlaps with the second feed openings lying on either side thereof 108a respectively. 108a ' consists.

The second feed openings 108a respectively. 108a ' are radially outward to in the circumferential direction about the axis of rotation A extending annular spaces 156a respectively. 156a ' open. The first gas spring arrangement 18a associated pressure fluid displacement chambers 22a respectively. 22a ' are each via a connecting channel, of which in 10 that of the pressure fluid displacement chamber 22a assigned connection channel 158a recognizable, in conjunction with the annulus 156a , Similarly, the pressure fluid displacement chambers 24a . 24a ' the second gas spring assembly 20a of which in 10 only the pressure fluid displacement chamber 24a can be seen, via respective connection channels 160a (This is the pressure fluid displacement chamber 24a assigned) in conjunction with the other annulus 156a ' , Each of these connection channels 158a each for one of the pressure fluid displacement chambers 22a . 22a the first gas spring assembly 18a respectively. 160a each for one of the pressure fluid displacement chambers 24a . 24a ' the second gas spring assembly 20a forms, as set forth below, both a channel for supplying pressurized fluid, as well as a channel for the removal of pressurized fluid.

Each axially outside the second feed openings 108a respectively. 108a ' are in the valve cylinder 74a first discharge openings 162a respectively. 162a ' intended. These are also to the rooms 156a respectively. 156a ' open and thus also in connection with the connecting channels 158a . 160a , Further axially removed with respect to the second feed opening 108 respectively. 108a ' are in the valve cylinder 74a second discharge openings 164a respectively. 164a ' formed, wherein in the 11 left recognizable second discharge opening 164a ' essentially also through the axial end of the valve cylinder 74a , the disc part 80a the primary side 12a and the cylindrical member 88a the secondary side 14a is limited. The two second discharge openings or groups of discharge openings 164a . 164a ' are over execution sections 170a of which a plurality may be provided distributed in circumference about the axis of rotation, in conjunction with another the discharge area 70a providing part of the rotary union 38a , which now on the cylindrical component 88a the secondary side 14a and formed with a larger diameter than that of the valve cylinder 74a formed area of the rotary union 38a ,

In association with each pair, each comprising one or more first discharge openings 162a . 162a ' and axially offset to one or more second discharge openings 164a . 164a ' , is in the valve spool 76a a radially outwardly open bypass channel 166a respectively. 166a ' educated. Here is particular especially in the 11 Left recognizable bridging channel 166a ' essentially also in the region of the axial end of the valve slide 76a , that is, in the area in which also the extension 140a lies, educated. Furthermore, in the locking element 142a two openings 168a formed, which the passage of fluid through this bridging channel 166a ' allow.

The configuration is such that if the primary side 12a and the secondary side 14a in the neutral relative rotational position with respect to each other, on the one hand, the first supply openings 106a not in registration with the second feed openings 108a and not in registration with the other second feed openings 108a ' are. This means that the feed area 68a the rotary union 38a not with any of the connection channels 158a . 160a connected to the different pressure fluid displacement chambers. In the same way, the two axially offset from each other bridging channels 166a . 166a ' arranged in this situation so that they are indeed in overlap with the second discharge openings 164a respectively. 164a ' but not in overlap with the first discharge openings 162a . 162a ' , Thus, also the discharge area 70a the rotary union 38a not in conjunction with any of the pressure fluid displacement chambers.

Finds a rotation of the primary side starting from the neutral relative rotational position 12a with respect to the secondary side 14a in a first direction of relative rotation, this is due to the interaction of the cam member 130a with the extension 140a on the valve spool 76a As a result, how to get in 16 detects, the valve spool 76a with respect to the valve cylinder 74a is moved, for example so that it in the representation of 16 is moved to the left. This means that the first feed openings 106a over the surrounding annular groove 154a in overlap with the second feed openings 108a , It will thus pass over the annulus 156a ' a connection to the connection channels 160a which in turn connects to the pressure fluid displacement chambers 24a . 24a ' produce. The first discharge openings 162a ' stay in this state or in this phase of the valve spool 76a locked. By shifting the valve spool 76a However, the bypass channel 166a now also in overlap with the first discharge openings 162a on the other axial side of the first feed openings 108a and 108a ' while the second feed openings 108a continue from the valve spool 76a stay closed. Thus, over the annulus 156a now that to the pressure fluid displacement chambers 22 respectively. 22a leading connection channels 158a in conjunction with the in 11 recognizable execution sections 170a and thus the discharge area 70a the rotary union 38a , This means that the fluid pressure in the pressure fluid displacement chambers reduced in volume in this state 24a . 24a ' through the connection with the in 2 recognizable pressure fluid line 62 and thus the source of pressurized fluid 50 is increased, while the enlarged in their volume Druckfluidverdrängungskammern 22a . 22a ' in conjunction with in 2 recognizable and to the fluid reservoir 48 leading fluid line 66 be brought or stand. By the extent of the overlap, so also the extent of the axial displacement of the valve spool 76a that with the extent of relative rotation between the primary side 12a and secondary side 14a corresponds, the flow or connection cross-section is influenced.

At the in 17 illustrated relative rotation in the other direction of relative rotation, the in 17 recognizable pressure fluid displacement chambers 22a . 22a ' reduced in volume. At the same time, the interaction of the cam element 130a with the lead 140a of the valve spool 76a this valve slide 76a now contrary to the biasing action of the spring already mentioned above 150a shifted in the opposite axial direction. This causes the first feed openings 106a now on the surrounding annular groove 154a in overlap with the second feed openings 108a are brought while the lying on the other axial side second feed openings 108a ' stay locked. Thus, there is a connection between the feed section 98a and the annulus 156a in which the to the pressure fluid displacement chambers 22a . 22a ' leading connection channels 158a open out. The first discharge openings 162a stay in this state through the valve spool 76a locked. The lying on the other axial side further first discharge openings 162a ' However, now over the on the axial end portion of the valve spool 76a formed bridging channel 166a ' associated with the at the axial end of the valve cylinder 74a lying another second discharge opening 164a ' and thus also in the 11 recognizable execution sections 170a , This means that in this relative rotational state, the two pressure fluid displacement chambers 22a . 22a ' in conjunction with the source of pressurized fluid 50 while the other pressure fluid displacement chambers 24a . 24a ' in connection with the fluid reservoir 48 stand.

Basically, this results in the same functionality in the transmission of torque or torsional vibrations, as described above. By increasing the fluid pressure in the region of one of the gas spring arrangements, the gas volumes which are also present or associated therewith are compressed more strongly, while those of the other gas spring arrangement associated gas volumes are relaxed. By increasing the fluid pressure also via the position control valve 72a it becomes possible the primary side 12a accelerated in the neutral relative rotational position with respect to the secondary side 14a to bring and keep in this.

Again, it is possible to ensure that in the neutral relative rotational position all pressure fluid displacement chambers are completely completed or by providing a slight overlap of the annular groove 154a both with the second feed openings 108a as well as the other second feed openings 108a ' to provide a slight permanent bias of the fluid pressure, in particular also to compensate for leakage currents. Also, by appropriate design of the peripheral edges of the groove 154a or the second feed openings 108a . 108a ' possible to achieve a progressive increase in the cross-section of the connection when producing an overlap.

Another embodiment variant of a torsional vibration damper 10a is in 18 shown. This design variant corresponds in many areas with respect to the 10 to 17 shown embodiment, so that below the essential differences will be discussed.

First, it should be noted that in the 18 not just the one essentially through the valve cylinder 74a provided rotating part of the rotary union 38a is recognizable, but also the stationary, non-rotating part 200a , This surrounds the rotating part, so the valve cylinder 74a , About a example designed as a ball bearing fixed bearing 202a and a trained example as a loose bearing (needle bearing o. The like.) Bearings 204a are the valve cylinder 74a and the stationary part 200a the rotary union 38a mounted radially with respect to each other.

One recognizes in 18 further, that the end wall providing disc part 82a , which together with the another end wall providing disc part 80a and the cylindrical wall 84a a primary-side displacement chamber assembly 206a provides an axially projecting annular attachment 208a having, which the rotating part of the rotary feedthrough 38a So the valve cylinder 74a , radially outward surrounds. Between this approach 208a and the rotating part is a designed for example as a needle bearing Loselager 210a provided, which is a radial guidance of the primary-side displacement chamber assembly 206a with respect to a fluid displacement chambers radially inwardly limiting secondary-side displacement chamber assembly 212a supported. This secondary-side displacement chamber assembly 212a , in which also the different in 18 unrecognizable connection channels 158a . 160a extend to the pressure fluid displacement chambers is with the valve cylinder 74a rotation. This one is still at his in 18 left axial end over another Loselager 214a , For example, also needle roller bearings, on the other disc part 80a radially supported. Thus, the primary-side displacement chamber assembly is 206a over the two camps 214a . 210 with respect to the valve cylinder 74a , So the rotating part of the rotary feedthrough 38a , stored while over the two camps 204a and 202a this rotating part of the rotary union 38a with respect to the stationary part 200a is stored. The defined axial relative positioning of the rotating assemblies with respect to the stationary part 200a the rotary feedthrough 38a takes place via the fixed storage 202a ,

In the stationary part 200a the rotary union 38a is a feed connection 216a provided for the supplied by a pressurized fluid source pressure fluid. About at least one in the valve cylinder 74a formed opening 218a is this feed connection 216a to the radial openings 100a in the valve spool 76a open. The pressurized fluid thus passes independently of the axial positioning of the valve spool 76a over the radial openings 100a in the axially extending feed section 98a and thus to the radially outwardly open first feed openings 106a , In the in 18 shown neutral position are these first feed openings 106a completed. Shifts the valve spool 76a starting from the in 18 shown positioning to the left, then the first feed openings 106a associated with those in the valve cylinder 74a formed second feed openings 108a ' and thus via the communicating with them and not shown connecting channels the associated pressure fluid displacement chambers. The second feed openings 108a are in this state then on the valve spool 76a formed and radially outwardly open bypass channel 166a in connection with a discharge connection 220a in the stationary part 200a the rotary union 38a , which in this embodiment is at the same radial level as the feed port 216a , While in this state then with the second feed ports 108a ' connected pressure fluid displacement chambers via the supply port 216a supplied pressurized fluid can, from the with the second supply openings 108a related pressure fluid displacement chambers and the bypass channel 166a or the discharge connection 220a Pressure fluid are discharged.

When displaced in the opposite direction are then the first feed openings 106a in connection with the second feed openings 108a and thus the pressure fluid displacement chambers associated therewith. The second feed openings 108a ' and thus also the associated pressure fluid displacement chambers are no longer from the axial end portion of the valve spool 76a Covered so that over a substantially from the axial end of the valve spool 76a and the valve cylinder 74a limited bypass channel 166a ' and a subsequent discharge opening 164a ' Fluid over in the 18 unrecognizable channel in the area of the two camps 210a . 204a can be directed. This volume range can be via one in the non-rotating part 200a the rotary union 38a formed drainage channel 222a be emptied. This drainage channel 222a leads to a drainage connection 224a in the non-rotating part of the rotary union 200a ,

It can be seen further that in the transition region between the non-rotating part 200a and the rotating part 74a the rotary union 78a on both sides of the feed connection 216a pressure seals 226a . 228a are provided. Also on both sides of the discharge connection 220a are such pressure seals 230a . 232a intended. By means of these pressure seals, a substantially, but generally not completely fluid-tight seal is created in the transition between the two components rotating relative to one another. Outside these two groups of pressure seals then continue to be two mass flow seals 234a . 236a intended. In the area between the two groups of pressure seals 226a . 228a respectively. 230a respectively. 232a opens a drainage channel 238 one. In the area between the pressure seal 226a and the mass flow seal 234a opens a drainage channel 240 on, and in the area between the pressure seal 232a and the mass flow seal 236a joins next to the already described leakage channel 222a another drainage channel 242a one. All of these drainage channels lead to the leakage connection 224a ,

Another drainage channel 244a leads from the drainage port 224a in the area in which the non-rotating part 200a the rotary union 38a a the biasing element 150a receiving chamber 250a surrounds. This chamber 250a may be open radially outwardly via an opening, not shown, and thus in communication with the drainage channel 244a stand. Thus, a leakage fluid flow, which in the abutment region of the valve spool 76a to the inner circumference of the valve piston 74a in the area of the chamber 250a has moved, to the accumulation of fluid in the chamber 250a to prevent.

In integration of such a torsional vibration damper 10a in a drive system, the valve cylinder is used 74a So also the rotating part of the rotary union 38a , For torque transmission from the secondary side to a subsequent module, such as a clutch o. The like .. For this purpose, the front end 252a of the valve cylinder 74a be formed with an engagement formation, for example in the manner of a Hirth toothing, which can then be brought into rotational coupling engagement with a corresponding formation on the following assembly and held by a clamping element o.

In 19 is shown in principle representation of another embodiment of an inventively constructed torsional vibration damper. This corresponds in terms of structural design, in particular the primary side 12 , the secondary side 14 , the position control valve 72 and various system areas assigned to these, for example the embodiment variants described in detail above. In this respect, the same components or system areas are also denoted by reference symbols, as described above, in particular also in FIG 2 , already used.

In the 19 can be seen in the lower part of the generally with the reference numeral 46 designated pressure fluid pump with a pressure fluid pump drive 300 and a pressurized fluid pump delivery area 302 , In the example shown, the pressure fluid pump drive 300 provided by a drive unit, for example, an internal combustion engine 304 , a vehicle. This internal combustion engine 304 drives the pressure fluid pump delivery area in a permanently coupled manner 302 to pressurized fluid from the fluid reservoir 48 in the to the rotary union 38 leading line 62 in which a general with 306 designated check valve is arranged. The pressure fluid delivery area 302 can be formed in various ways, so act with different conveying members, which contribute to the conveying of the pressurized fluid. Here you can use impellers, cell wheels, rotary pistons or reciprocating pistons.

The pressure fluid pump 46 or the pressure fluid delivery area 302 the same is a pressure-dependent effective adjustment arrangement 308 assigned. This attacks the in the line 62 , So the output side of the pressure fluid pump 46 prevailing pressure of the pressure fluid and according to this tapped pressure, the conveying capacity of the pressure fluid conveying area 302 one. For this purpose, one on the pressure fluid delivery area 302 , For example, an effective therein conveying member, acting, depending on the pressure fluid displaceable adjusting plunger 310 be provided, which contributes directly or indirectly with such a conveying member for varying the conveying effect. For example, in the case of a conveyor designed as a piston Goose, it is possible to vary by an eccentric the stroke of the reciprocating piston and therefore also the per stroke conveyed amount. In their conveying capacity variable fluid pumps are known in the art and therefore need not be further described here. Of importance here, however, is that acting on such a variable pressure fluid pump size of the pump provided by this substantially and in the supply area for rotary feedthrough 38 tapped pressure fluid pressure itself. It is thus ensured that despite the permanently existing drive connection with the pressure fluid pump drive 300 then when the pressure fluid pressure in the supply area 68 is sufficiently high, the conveying capacity is reduced and therefore virtually no further pressure increase by the pressure fluid pump 46 is generated and thus of the drive unit 304 worn drive energy share can be reduced.

The pressure fluid pump 46 is also a pressure accumulator 312 associated, wel cher pressure fluid or energy stores. Occur spontaneous relative rotation between the primary side 12 and the secondary side 14 on, the accumulator can 312 Spontaneously pressurized pressurized fluid, so that spontaneously corresponding to the relative rotation can be counteracted. For this purpose, it is advantageous, for example, to design the pressure accumulator such that the pressure fluid volume required for such spontaneous changes can be provided substantially completely by it as well. For example, it is advantageous to design the pressure accumulator with a storage volume of about 250 ml at a maximum required volume flow of 35 l / min. This allows the pressure fluid pump 46 to dimension correspondingly smaller, so to design with a lower maximum delivery rate.

The pressure fluid pump 46 is also a pressure relief valve 314 assigned, which rises above a default value in the line 62 Pressurized fluid in the direction of the fluid reservoir 48 gives off and thus provides a pressure limit. The further provided pressure sensor 66 detects the output side of the pressure fluid pump 46 existing pressure fluid pressure and can then, if an unexpected or excessively high rise occurs, provide a corresponding signal that can lead, for example, to an emergency shutdown or a corresponding diagnosis.

One recognizes in 19 a torsional vibration damper 10 which can essentially operate completely independently, that is to say without any control-related interaction with other system components of a vehicle. Both the position control valve 72 , as well as the source of pressurized fluid 50 work alone triggered by respective occurring in the system variables, especially pressure fluctuations. Such a self-sufficient working system, in which no controlled switching valves are required, is particularly advantageous in vehicles in which such a torsional vibration damper 10 is to be combined with a manual gearbox to be switched. In contrast to automatic transmissions, there are basically no system states or size-defining signal values or control variables which are also available in the torsional vibration damper in the case of transmissions to be manually shifted 10 can be used. This is at the in 19 However, in principle also not required structure shown.

A modification of this system is in 20 shown. In the following, only the embodiment according to 19 existing differences explained. One recognizes in 20 in that the source of pressurized fluid 50 again the pressure fluid pump 46 with the example by an internal combustion engine 304 provided pressurized fluid pump drive 300 includes. The pressurized fluid pump delivery area 302 However, no adjustment arrangement is assigned, so that when the drive unit, so the internal combustion engine 304 , is set in operation, according to also the pressure fluid pump delivery area 302 works and promotes pressurized fluid. Because of this permanent action comes the pressure relief valve 314 , in this embodiment, with respect to the check valve 306 is arranged on the pump side, a special meaning, since due to the permanently present conveying effect of the pressure fluid pump 46 even if there is no relative rotation between the primary side for a long time 12 and the secondary side 14 This means that if such a situation exists without consumption of pressurized fluid, permanent fluid will be delivered via the pressure relief valve 314 is circulated. Although this means a greater expenditure of energy, since a larger proportion of the drive energy from the internal combustion engine 304 is tapped, but simplifies the structure compared to in 19 illustrated embodiment variant. In the 20 shown variant is therefore particularly in systems into consideration, in which a more or less continuous consumption of pressurized fluid is present, as for example in very large-sized vehicle drives such. B. in marine propulsion, the case.

The 21 shows a further modification of in 19 variant shown. The pressurized fluid source includes as a pressure fluid pump drive 300 here an electric drive motor 316 , which is the pressure fluid pump delivery area 302 drives. A pressure switch 318 take the line 62 in front existing pressure fluid pressure and leads to appropriate activation or deactivation of the electric drive motor 316 , So exceeds the pressure in the line 62 or in the accumulator 312 an upper limit, becomes the electric drive motor 316 off. If the pressure falls below a lower limit, the electric drive motor 316 switched back on. This can also be ensured that in the area of the line 62 and also the accumulator 312 In case of completely self-sufficient operation of the system, a permanently high pressure can be provided. It should be noted here that, of course, the electric drive motor 316 Also, a drive device may be assigned, for example, the pressure signal of the pressure sensor 66 receives and accordingly the drive behavior of the electric drive motor 16 influenced, that is, the driving speed increases or decreases, a comparatively constant pressure fluid pressure in the line 62 maintain. However, a completely autonomous mode of operation is also ensured in this case, since no control-technical linkage with other system areas in a vehicle is required. A significant advantage of this embodiment is that, regardless of whether a drive unit of a vehicle is in operation or not, a sufficiently high pressure fluid pressure can be provided, so that in particular in a start phase of a drive system already by prior activation of the pressure fluid pump 46 it can be ensured that sufficient pressure is present when the rotational speed of a drive train is moving upwards in the direction of idling speed and thereby a resonance frequency range of the torsional vibration damper 10 is going through.

Claims (42)

Torsional vibration damper comprising a primary side ( 12 ; 12a ) and one against the action of a damper assembly with respect to the primary side ( 12 ; 12a ) about a rotational axis (A) rotatable secondary side ( 14 ; 14a ), wherein the damper arrangement comprises at least one gas spring arrangement ( 18 . 20 ; 18a . 20a ) comprises a volume of gas which can be acted upon by pressurized fluid ( 98 ) and at least one pressure fluid displacement chamber ( 22 . 22 ' . 24 . 24 '; 22a . 22a ' . 24a . 24a ' ) whose volume during relative rotation of the primary side ( 12 ; 12a ) with respect to the secondary side ( 14 ; 14a ) is variable, further comprising a rotary feedthrough ( 38 ; 38a ) for the supply / removal of pressurized fluid characterized by a position control valve arrangement ( 72 ; 72a ) in the pressure fluid flow path between the rotary feedthrough ( 38 ; 38a ) and the at least one pressure fluid displacement chamber ( 22 . 22 ' . 24 . 24 '; 22a . 22a ' . 24a . 24a ' ), wherein, depending on the relative rotational position of the primary side ( 12 ; 12a ) with respect to the secondary side ( 14 ; 14a ) by the position control valve arrangement ( 72 ; 72a ) the at least one pressure fluid displacement chamber ( 22 . 22 ' . 24 . 24 '; 22a . 22a ' . 24a . 24a ' ) with a supply area ( 68 ; 68a ) of the rotary feedthrough ( 38 ; 38a ) or with a derivation area ( 70 ; 70a ) of the rotary feedthrough ( 38 ; 38a ) is connectable. Torsional vibration damper according to claim 1, characterized in that the damper arrangement comprises at least one first gas spring arrangement ( 18 ; 18a ) and associated therewith at least one pressure fluid displacement chamber ( 22 . 22 '; 22a . 22a ' ), wherein the gas volume ( 98 ) of the first gas spring arrangement ( 18 ; 18a ) during relative rotation of the primary side ( 12 ; 12a ) with respect to the secondary side ( 14 ; 14a ) in a first relative direction of rotation through the at least one pressure fluid displacement chamber ( 22 . 22 '; 22a . 22a ' ) of the first gas spring arrangement ( 18 ; 18a ) compressed compressed fluid is compressed, and at least one second gas spring arrangement ( 20 ; 20a ) and associated therewith at least one pressure fluid displacement chamber ( 24 . 24 '; 24a . 24a ' ), wherein the gas volume ( 98 ) of the second gas spring arrangement ( 20 ; 20a ) during relative rotation of the primary side ( 12 ; 12a ) with respect to the secondary side ( 14 ; 14a ) in a second relative direction of rotation opposite to the first relative direction of rotation, from the at least one pressure fluid displacement chamber ( 24 . 24 '; 24a . 24a ' ) of the second gas spring arrangement ( 20 ; 20a ) compressed compressed fluid is compressed. Torsional vibration damper according to claim 2, characterized in that the position control valve arrangement ( 72 ; 72a ), if they contain the at least one pressure fluid displacement chamber ( 22 . 22 '; 22a . 22a ' ) of the first gas spring arrangement ( 18 ; 18a ) with the discharge area ( 70 ; 70a ) of the rotary duct ( 38 ; 38a ) connecting at least one pressure fluid displacement chamber ( 24 . 24 '; 24a . 24a ' ) of the second gas spring arrangement ( 20 ; 20a ' ) with the supply area ( 70 ; 70a ) of the rotary feedthrough ( 38 ; 38a ), and when they contain the at least one pressure fluid displacement chamber ( 24 . 24 '; 24a . 24a ' ) of the second gas spring arrangement ( 20 ; 20a ) with the discharge area ( 70 ; 70a ) of the rotary feedthrough ( 38 ; 38a ) connecting at least one pressure fluid displacement chamber ( 22 . 22 '; 22a . 22a ' ) of the first gas spring arrangement ( 18 ; 18a ) with the supply area ( 68 ; 68a ) of the rotary feedthrough ( 38 ; 38a ) connects. Torsional vibration damper according to one of claims 1 to 3, characterized in that in a neutral relative rotational position with respect to each other arranged primary side ( 12 ; 12a ) and secondary side ( 14 ; 14a ) the position control valve arrangement ( 72 ; 72a ) all pressure fluid displacement chambers ( 22 . 22 ' . 24 . 24 '; 22a . 22a ' . 24a . 24a ' ) completes completely. Torsional vibration damper according to one of Claims 1 to 3, characterized in that be in a neutral relative rotational position be arranged each other arranged primary side ( 12 ; 12a ) and secondary side ( 14 ; 14a ) the position control valve arrangement ( 72 ; 72a ) all pressure fluid displacement chambers ( 22 . 22 . 24 . 24 '; 22a . 22a ' . 24a . 24a ' ) with the supply area ( 68 ; 68a ) of the rotary feedthrough ( 38 ; 38a ) connects. Torsional vibration damper according to one of claims 1 to 5, characterized in that during relative rotation of the primary side ( 12 ; 12a ) with respect to the secondary side ( 14 ; 14a ) starting from a neutral relative rotational position of the primary side ( 12 ; 12a ) with respect to the secondary side ( 14 ; 14a ) in the position control valve arrangement ( 72 ; 72a ) provided connection flow cross-section for the supply / discharge of pressurized fluid to / from the at least one pressure fluid displacement chamber ( 22 . 22 ' . 24 . 24 '; 22a . 22a ' . 24a . 24a ' ) progressively increases. Torsional vibration damper according to one of claims 1 to 6, characterized in that the position control valve arrangement ( 72 ; 72a ) one with the primary side ( 12 ; 12a ) or the secondary side ( 14 ; 14a ) rotatable valve cylinder ( 74 ; 74a ) and one in the valve cylinder during relative rotation of the primary side ( 12 ; 12a ) with respect to the secondary side ( 14 ; 14a ) movable valve slide ( 76 ; 76a ). Torsional vibration damper according to claim 7, characterized in that the valve cylinder ( 74a ) or the valve slide ( 76 ) a rotatable part of the rotary feedthrough ( 38 ; 38a ). Torsional vibration damper according to claim 7 or 8, characterized in that the valve cylinder ( 74 ) with the primary side ( 12 ) is rotatable and the valve slide ( 76 ) with the secondary side ( 12 ) is rotatable rotary valve. Torsional vibration damper according to claim 9, characterized in that in the rotary valve ( 76 ) at least a part of the supply area ( 68 ) and the derivation area ( 70 ) of the rotary feedthrough ( 38 ) is formed. Torsional vibration damper according to claim 10, characterized in that in the rotary valve ( 76 ) at least one radially open first feed opening ( 106 . 106 ' ) of the supply area ( 68 ) is formed and in the valve cylinder ( 74 ) at least one to a rotary valve ( 76 ) receiving cylinder opening ( 114 ) open second feed opening ( 108 . 108 ' . 108 '' . 108 ''' ), wherein further in the secondary side ( 14 ) one of the at least one pressure fluid displacement chamber ( 22 . 22 ' . 24 . 24 ' ) leading feed channel ( 110 . 110 ' . 110 '' . 110 ''' ) is formed, which depends on the relative rotational position of the primary side ( 12 ) with respect to the secondary side ( 14 ) via the at least one second feed opening ( 108 . 108 ' . 108 '' . 108 ''' ) in connection with the at least one first feed opening ( 106 . 106 ' ) can be brought. Torsional vibration damper according to claim 6 and claim 11, characterized in that the at least one second feed opening ( 108 . 108 ' . 108 '' . 108 ''' ) and / or the at least one first feed opening ( 106 . 106 ' ) is limited by an end profile, the relative rotation of the primary side ( 12 ) with respect to the secondary side ( 14 ) starting from the neutral relative rotational position a progressive increase of the overlap of the at least one first feed opening ( 106 . 106 ' ) with the at least one second feed opening ( 108 . 108 ' . 108 '' . 108 ''' ) generated. Torsional vibration damper according to one of claims 10 to 12, characterized in that in the rotary valve ( 76 ) at least one radially open first discharge opening ( 116 . 116 ' . 116 '' . 116 ''' ) of the derivation area ( 70 ) is formed and in the valve cylinder ( 74 ) at least one to a rotary valve receiving the cylinder opening ( 114 ) open second discharge opening ( 118 . 118 ' ) is formed, where further in the secondary side ( 14 ) one of the at least one pressure fluid displacement chamber ( 22 . 22 ' . 24 . 24 ' ) leading discharge channel ( 120 . 120 ' . 120 '' . 120 ''' ) is formed, which depends on the relative rotational position of the primary side ( 12 ) with respect to the secondary side ( 14 ) via the at least one second discharge opening ( 118 . 118 ' ) in connection with the at least one first discharge opening ( 116 . 116 ' . 116 '' . 116 ''' ) bring bar is. Torsional vibration damper according to claim 11 and claim 13, characterized in that in the rotary valve ( 76 ) a substantially axially extending lead portion ( 98 ) is provided, which via the at least one first feed opening ( 106 . 106 ' ) is radially open, that in the rotary valve ( 76 ) a substantially axially extending discharge section ( 99 ) is provided, which via the at least one first discharge opening ( 116 . 116 ' . 116 '' . 116 ''' ) is radially open, and that the lead portion ( 98 ) and the derivation section ( 99 ) are not in communication with each other. Torsional vibration damper according to claim 2 and one of claims 11 to 14, characterized in that in the valve cylinder ( 76 ) associated with each pressure fluid displacement chamber ( 22 . 22 ' ) of the first gas spring arrangement ( 18 ) and in association with each pressure fluid displacement chamber ( 24 . 24 ' ) of the second gas spring arrangement ( 20 ) a second feed opening ( 108 . 108 ' . 108 '' . 108 ''' ) is provided. Torsional vibration damper according to claim 2 and one of claims 13 to 15, characterized in that in the valve cylinder ( 74 ) associated with each pressure fluid displacement chamber ( 22 . 22 ' . 24 . 24 ' ) of the first gas spring arrangement or of the second gas spring arrangement ( 20 ) a second discharge opening ( 118 . 118 ' ) is provided. Torsional vibration damper according to claim 16, characterized in that in the valve cylinder ( 76 ) one of the number of pressure fluid displacement chambers ( 22 . 22 ' ) of the first gas spring arrangement ( 18 ) or the number of pressure fluid displacement chambers ( 24 . 24 ' ) of the second gas spring arrangement ( 20 ) corresponding number of second discharge openings ( 118 . 118 ' ) is provided and that in dependence on the relative rotational position of the primary side ( 12 ) with respect to the secondary side ( 14 ) the pressure fluid displacement chambers ( 22 . 22 ' ) of the first gas spring arrangement ( 18 ) or the pressure fluid displacement chambers ( 24 . 24 ' ) of the second gas spring arrangement ( 20 ) via the second discharge openings ( 118 . 118 ' ) in connection with the first discharge openings ( 116 . 116 ' . 116 '' . 116 ''' ) are brought. Torsional vibration damper according to claim 7 or 8, characterized in that the valve cylinder ( 74a ) with the secondary side ( 14a ) is rotatable and the valve slide ( 76a ) in a cylinder opening ( 114a ) of the valve cylinder ( 74a ) in the direction of the axis of rotation (A) displaceable and against rotation with respect to the valve cylinder ( 74a ) is locked valve piston. Torsional vibration damper according to claim 20, characterized in that on the primary side ( 12a ) a cam element ( 130a ) is provided, which with the valve piston ( 76a ) for shifting the same during relative rotation of the primary side ( 12a ) with respect to the secondary side ( 14a ) cooperates. Torsional vibration damper according to claim 19, characterized in that the valve piston ( 76a ) by a biasing element ( 150a ) is biased in a first axial direction and by the cam element ( 130a ) in a second axial direction against the biasing action of the biasing member (FIG. 150a ) is displaceable. Torsional vibration damper according to claim 20, characterized in that the biasing element ( 150a ) in a through the valve piston ( 76a ) and the valve cylinder ( 74a ) limited chamber ( 250a ) and that in the chamber ( 250a ) accumulated fluid via a drainage channel ( 244a ) is dissipatable. Torsional vibration damper according to one of claims 18 to 21, characterized in that in the valve piston ( 76a ) at least a part of the supply area ( 68a ) and the derivation area ( 70a ) of the rotary feedthrough ( 38a ) is formed. Torsional vibration damper according to claim 22, characterized in that in the valve piston ( 76a ) at least one radially open first feed opening ( 106a ) is formed, that in the valve cylinder ( 74a ) at least one second feed opening ( 108a . 108a ' ) is formed, which via a connecting channel ( 158a . 160a ) in conjunction with the at least one pressure fluid displacement chamber ( 22a . 22a ' . 24a . 24a ' ), and that depending on the relative rotational position of the primary side ( 12a ) with respect to the secondary side ( 14a ) the extent of overlap of the at least one first feed opening ( 106a ) with the at least one second feed opening ( 180a . 108a ' ) is changeable. Torsional vibration damper according to claim 23, characterized in that in the valve cylinder ( 74a ) at least one first discharge opening ( 162a . 162a ' ) is provided, which via the connecting channel ( 158 . 160 ) in conjunction with the at least one pressure fluid displacement chamber ( 22 . 22a ' . 24a . 24a ' ) is that in the valve cylinder ( 74a ) at least one second discharge opening ( 164a . 164a ' ), which in conjunction with a derivative section ( 170a ) of the rotary feedthrough ( 38a ), and in that in the valve piston ( 76a ) at least one bridging channel ( 166a . 166a ' ) is provided, which depends on the relative rotational position of the primary side ( 12a ) with respect to the secondary side ( 14a ) a connection between the at least one first discharge opening ( 162a . 162a ' ) and the at least one second Abführöffung ( 164a . 164a ' ). Torsional vibration damper according to claim 24, characterized in that when Relaitvdrehung the primary side ( 12a ) with respect to the secondary side ( 14a ) either a connection between the at least one first feed opening ( 106a ) and the at least one second feed opening ( 108 . 108a ' ) or via the bypass channel ( 166a . 166a ' ) a connection between the at least one first discharge opening ( 162a . 162a ' ) and the at least one second discharge opening ( 164a . 164a ' ) can be produced. Torsional vibration damper according to claim 6 and any one of claims 12 to 25, characterized in that the at least one first feed opening ( 106a ) and / or the at least one second feed opening ( 108a . 108a ' ) is formed with such end profile that when relative rotation of the primary side ( 12a ) with respect to the secondary side ( 14a ) Starting from a neutral relative rotational position, the extent of the coverage of the little at least one first feed opening ( 106a ) with the at least one second feed opening ( 108a . 108a ' ) progressively increases. Torsional vibration damper according to claim 2 and one of claims 24 to 26, characterized in that the at least one pressure fluid displacement chamber ( 22a . 22a ' ) of the first gas spring arrangement ( 18a ) via a connection channel ( 158a ) in connection with at least one second feed opening ( 108a ' ) and the at least one pressure fluid displacement chamber ( 24a . 24a ' ) of the second gas spring arrangement ( 20a ) via a connection channel ( 160a ) in connection with at least one further second feed opening ( 108a ), and in dependence on the relative rotational position of the primary side ( 12a ) with respect to the secondary side ( 14a ) by moving the valve piston ( 76a ) the at least one first feed opening ( 106a ) in register with the at least one second feed opening ( 108a ) or the at least one further second feed opening ( 108a ' ) can be brought. Torsional vibration damper according to claim 27, characterized in that the at least one pressure fluid displacement chamber ( 22a . 22a ' ) of the first gas spring arrangement ( 18a ) via its connection channel ( 158 ) in connection with at least one first discharge opening ( 162a ) and the at least one pressure fluid displacement chamber ( 24a . 24a ' ) of the second gas spring arrangement ( 20a ) via its connection channel ( 160 ) in connection with at least one further second discharge opening ( 162a ), and that the at least one first discharge opening ( 162a ) at least one second discharge opening ( 164a ) and a bridging channel ( 166a ) and the at least one further first discharge opening ( 162a . 162a ' ) at least one further second discharge opening ( 164a ' ) and another connection channel ( 166a ' ) assigned. Torsional vibration damper according to claim 28, characterized in that upon displacement of the valve piston ( 76a ) in a first displacement direction starting from the neutral relative rotational position of the primary side ( 12a ) with respect to the secondary side ( 14a ) the at least one first feed opening ( 106a ) in connection with the at least one second feed opening ( 108a ) and the at least one further first discharge opening ( 162a ' ) via the further bridging channel ( 166a ' ) in connection with the at least one further second discharge opening ( 164a ' ) occurs, and that upon displacement of the valve piston ( 76a ) in a first direction of displacement opposite second displacement direction starting from the neutral relative rotational position of the primary side ( 12a ) with respect to the secondary side ( 14a ) the at least one first feed opening ( 106a ) in conjunction with the we at least one further second feed opening ( 108a ' ) and the at least one first discharge opening ( 162a ) via the bypass channel ( 166a ) in connection with the at least one second discharge opening ( 164a ) occurs. Torsional vibration damper according to claim 27, characterized in that when the at least one first feed opening ( 106a ) in connection with the at least one further second feed opening ( 108a ' ), the at least one second feed opening ( 108a ' ) via a bridging channel ( 166a ) in connection with a discharge opening ( 164a ), and when the at least one first feed opening ( 106a ) in register with the at least one second feed opening ( 108a ), the at least one further second feed opening ( 108a ) via a further discharge opening ( 164a ' ) with a drainage channel ( 222a ). Torsional vibration damper according to one of the preceding claims, characterized by a in connection with the supply area ( 68 ) of the rotary feedthrough ( 38 ) pressurized fluid source ( 50 ). Torsional vibration damper according to claim 31, characterized in that the pressure fluid source ( 50 ) a pressurized fluid pump ( 46 ) with a pressure fluid pump drive ( 300 ). Torsional vibration damper according to claim 32, characterized in that the pressure fluid pump ( 46 ) an accumulator ( 312 ) assigned. Torsional vibration damper according to claim 32 or 33, characterized in that the pressure fluid pump ( 46 ) a pressure limiting valve arrangement ( 314 ) is assigned to limit the on an output side of the pressure fluid pump ( 46 ) existing pressure fluid pressure to a default value. Torsional vibration damper 32 to 34, characterized in that the conveying capacity of the pressure fluid pump ( 46 ) in dependence on at an output side of the pressure fluid pump ( 46 ) existing pressure fluid pressure is variable. Torsional vibration damper according to claim 35, characterized in that the pressure fluid pump ( 46 ) has at least one conveying member whose conveying effect is variable in dependence on the pressure fluid pressure. Torsional vibration damper according to one of claims 32 to 36, characterized in that the pressure fluid pump drive ( 300 ) a vehicle drive unit ( 304 ). Torsional vibration damper according to claim 35 or 36, characterized in that the pressure fluid pump drive ( 300 ) can be activated and deactivated as a function of the pressure fluid pressure and / or varied in its driving action. Torsional vibration damper according to claim 38, characterized in that the pressure fluid pump drive ( 300 ) an electric drive motor ( 316 ). Torsional vibration damper according to the preamble of claim 1 or one of the preceding claims, characterized in that the at least one pressure fluid displacement chamber ( 22a . 22a ' . 24a . 24a ' ) through a primary-side displacement chamber assembly ( 206a ) and a secondary-side displacement chamber assembly ( 212a ), the primary-side displacement chamber assembly ( 206a ) two end walls ( 80a . 82a ) and a peripheral wall ( 84a ), and wherein the secondary-side displacement chamber assembly ( 212a ) or a subsequent rotating part ( 74a ) of the rotary feedthrough ( 38a ) one of the end walls ( 80a . 82a ), this end wall ( 82a ) an annular axial extension ( 208a ), wherein at the Axialansatz ( 208a ) a warehouse ( 210a ) is radially supported, via which the primary side either with respect to a non-rotating part ( 200a ) of the rotary feedthrough ( 38a ) or with respect to the secondary-side displacement chamber assembly or the rotating part ( 74a ) of the rotary feedthrough ( 38a ) is stored. Torsional vibration damper according to claim 40, characterized in that the bearing ( 210a ) is a floating bearing. Torsional vibration damper according to one of claims 40 to 41, characterized in that the rotating part ( 74a ) of the rotary feedthrough ( 38a ) has a form-fitting engagement formation, preferably a serration, for torque-transmitting coupling with a following assembly.