WO2008128641A1

WO2008128641A1 - Torsional vibration damper for the drivetrain of a vehicle

Info

Publication number: WO2008128641A1
Application number: PCT/EP2008/002763
Authority: WO
Inventors: Thomas Busold; Thomas Dögel
Original assignee: Zf Friedrichshafen Ag
Priority date: 2007-04-20
Filing date: 2008-04-08
Publication date: 2008-10-30
Also published as: EP2137430A1; DE102008008508A1

Abstract

A torsional vibration damper comprises a primary side (12) and a secondary side (14) which may rotate about a rotational axis (A) relative to the primary side (12) against the action of a damper arrangement, wherein the damper arrangement comprises at least one gas spring arrangement (18, 20) with a gas volume (98) which may be pressurised with a pressure fluid and at least one pressure fluid displacement chamber (22, 22', 24, 24'), the volume of which may change on rotation of the primary side (12) relative to the secondary side (14) and further comprises a rotating duct (38) for the introduction/removal of pressure fluid and a positional regulation valve arrangement (72) in the pressure fluid flow path between the rotating duct (38) and the at least one pressure fluid displacement chamber (22, 22', 24, 24'), wherein the positional regulation valve arrangement (72) connects the at least one pressure fluid displacement chamber (22, 22', 24, 24') to a pressure fluid supply region (68) of the rotating duct (38) or to a pressure fluid drain region (70) of the rotating duct (38), depending on the relative rotational position of the primary side (12) to the secondary side (14).

Description

Torsional vibration damper for the drive train of a vehicle

(Description)

Technical area

The present invention relates to a torsional vibration damper, comprising a primary side and a secondary side rotatable against the action of a damper assembly with respect to the primary side about an axis of rotation, the damper assembly comprises at least one gas spring assembly with a pressurizable gas volume and at least one Druckfluidverdrängängungskammer whose volume in relative rotation of the primary side with respect to the secondary side is changeable. In such a torsional vibration damper, a rotary feedthrough is further provided in order to be able to conduct pressure fluid to the at least one pressure fluid displacement chamber of the at least one gas spring arrangement or to be able to derive from this.

State of the art

Such a torsional vibration damper is shown in circuit diagram-like representation in Fig. 1. The generally constructed in the form of a dual mass flywheel torsional vibration damper 10 includes a schematically indicated primary side 12 and a rotatable upon movement of torque fluctuations or in the torque transmission with respect to the primary side 12 or movable secondary side 14. This relative rotation takes place against the return action of a damper assembly 16, in the illustrated Example comprises two gas spring assemblies 18, 20. The gas spring assembly 18 includes a pressure fluid displacement chamber 22. The gas spring assembly 20 has a Druckfluidverdrängungskammer 24 in a corresponding manner. During relative rotation of the primary side with respect to the secondary side, for example in FIG. 1 when the secondary side 14 is displaced relative to the primary side 12 to the right, the volume of the pressure fluid displacement chamber 22 of the gas spring arrangement 18 decreases, whereby the displacement of the pressure fluid 22 compresses an unillustrated volume of gas. which is separated, for example via a piston or a membrane of the pressurized fluid of the gas spring assembly 18. Upon relative movement in the opposite direction, the volume of the pressure fluid displacement chamber 24 decreases and, correspondingly, a gas volume of the gas spring assembly 20 is compressed.

The relative movement between the primary side 12 and the secondary side 14 is detected via a travel sensor arrangement 26 whose signals are conducted into a control device 28 for the torsional vibration damper 10. This is connected via a connecting line 30 also in connection with an engine control unit.

The control device 28 controls two pressure control valves 32, 34. The pressure control valve 32 is connected via a pressure fluid line 36, a rotary feedthrough 38 and another arranged in the rotating system portion of the torsional vibration damper 10 fluid line 40 in communication with the Druckfluidverdrängungskammer 24 of the gas spring assembly 20. In a corresponding manner, the pressure control valve 34 via a pressurized fluid line 42, the rotary feedthrough 38 and Depending on the control state connect the pressure control valves 32, 34 via the respective pressure fluid lines and the rotary feedthrough 38 associated with them Druckfluidverdrängungskammern 24, 22 with a fluid pump 46th and a fluid reservoir 48 comprising pressurized fluid source 50 or a respective return region 52 or 54, via which a return of fluid into the fluid reservoir 58 can take place Kan n. The fluid reservoir 48 and the return line regions 52, 54 are kept substantially unpressurized.

By selectively adjusting the pressure fluid supply or pressure fluid discharge to / from the pressure fluid displacement chambers 24, 22, it is possible to actively act on the vibration damping characteristic of the torsional vibration damper 10. For example, that of the pressure fluid displacement chambers 24, 22, by occurring torques in their Volume is reduced, are connected by means of the respectively associated pressure control valve 32 and 34 with the pressure fluid source 50, while the other is connected by connection to the respective return line areas 52, 54 substantially depressurized.

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

Presentation of the invention

It is therefore an object of the present invention to provide a torsional vibration damper to provide a simplified structure or reduced control effort.

According to the invention this object is achieved by a torsional vibration damper, comprising a primary side and against the action of a damper assembly with respect to the primary side about a rotation rotatable secondary side, wherein the damper assembly comprises at least one gas spring assembly with a pressurizable by pressurized gas volume and at least one pressure fluid displacement chamber whose volume is variable with relative rotation of the primary side with respect to the secondary side, further comprising a rotary feedthrough for supply / discharge of pressurized fluid, characterized by a Lageregelventilanordnung in Druckfluidströmungsweg between the rotary union and the at least one Druckfluidverdrängungskammer, wherein in dependence on the relative rotational position of the primary side relative to the secondary side by the position control valve arrangement the at least one pressure fluid displacement chamber with a supply area of the rotary feedthrough or with a Able range of rotation of the rotary feedthrough is connectable.

By providing the bearing valve arrangement in the rotating system area of the torsional vibration damper, ie between the rotary valve and the pressure fluid displacement chamber or chambers, it becomes possible to work with only one pressure control valve in the non-rotating system area adjoining the rotary feedthrough, or to provide a differently designed structure which merely has to ensure that a defined fluid pressure is provided or maintained can. This simplifies the control effort as well as the design effort.

In order to be able to provide a damping property generated by compression of a gas volume in the torsional vibration damper according to the invention in both directions of relative rotation, it is proposed that the damper arrangement comprise at least one first gas spring arrangement and associated therewith at least one pressure fluid displacement chamber, the gas volume of the first gas spring arrangement with relative rotation of the primary side with respect to the secondary side is compressed in a first relative rotational direction by displaced from the at least one Druckfluidverdrängungskammer the first gas spring assembly pressure fluid, and at least one second gas spring assembly and associated therewith at least one Druckfluidverdrängungskammer, wherein the gas volume of the second gas spring assembly with relative rotation of the primary side with respect to the secondary side opposite in one of the first relative rotational direction second relative rotation direction through from the at least one Druc Kfluidverdrängungskammer the second gas spring assembly displaced compressed fluid is compressed.

In this case, it may preferably be further provided that the position control valve arrangement, when connecting the at least one pressure fluid displacement chamber of the first gas spring assembly to the discharge region of the rotary union, connects the at least one pressure fluid displacement chamber of the second gas spring assembly to the supply region of the rotary union, and then if the at least one Compression fluid displacement chamber of the second gas spring assembly connects to the discharge region of the rotary feedthrough, the at least one pressure fluid displacement chamber of the first Gas spring assembly connects to the supply area of the rotary feedthrough.

In a neutral relative rotational position relative to each other arranged primary side and secondary side, all pressure fluid displacement chambers can be completely closed by the position control valve arrangement. Alternatively, it is possible that in a neutral relative rotational position relative to each other arranged primary side and secondary side, the position control valve assembly connects all pressure fluid displacement chambers with the supply area of the rotary feedthrough. In this way it is ensured that prevail in all pressure fluid displacement chambers equal pressure conditions, as may also be provided for the neutral relative rotational position. However, any fluid leaks that may occur in the area of components that are movable relative to each other can be compensated.

In order to ensure a gradual increase in pressure in the corresponding pressurized pressure displacement chambers upon deflection of the primary side with respect to the secondary side, starting from a neutral relative rotational position, it is proposed that with relative rotation of the primary side relative to the secondary side starting from a neutral relative rotational position of the primary side with respect to the secondary side Position control valve assembly provided Verbindungsströmungsquerschnitt for supply / discharge of 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 comprises a valve cylinder rotatable with the primary side or the secondary side and a valve slide which can be moved in the valve cylinder when the primary side relative rotation with respect to the secondary side.

In order to simplify in particular the construction of the rotary feedthrough for the supply or removal of pressurized fluid, it is further proposed that the valve cylinder or the valve slide forms a rotatable part of the rotary feedthrough. In an embodiment variant according to the invention, the valve cylinder can be rotatable with the primary side and the valve slide can be a rotary slide which can be rotated with the secondary side.

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 areas, such as 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, at least a part of the supply area and the discharge area of the rotary feedthrough can be formed.

In order to be able to bring the feed region of the rotary feedthrough in conjunction with the at least one pressure fluid displacement chamber, it is proposed that at least one radially open first feed opening of the feed region is formed in the rotary valve and at least one second feed opening open to a cylinder opening receiving the rotary valve is formed in the valve cylinder , wherein further in the secondary side from the at least one Druckfluidverdrängängammer away leading supply channel is formed, which can be brought in relation to the relative rotational position of the primary side with respect to the secondary side via the at least one second supply port in connection with the at least one first supply port.

In order to ensure the gradual increase in pressure during the production of the connection, it is proposed that the at least one second feed opening or / and the at least one first feed opening is delimited by an end profile, that upon relative rotation of the primary side relative to the secondary side, starting from the neutral relative rotational position, a progressive increase of the overlap of the at least one first supply port with the at least one second supply port is generated.

In order to enable the removal of fluid from the at least one pressure fluid displacement chamber, it is proposed that at least one radially open first discharge opening of the discharge region is formed in the rotary valve and at least one second discharge opening open to a cylinder opening receiving the rotary valve is formed in the valve cylinder Secondary side is formed by the at least one Druckfluidverdrängungskammer away leading discharge channel, which can be brought in relation to the relative rotational position of the primary side relative to the secondary side via the at least one second discharge opening in connection with the at least one first discharge opening.

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

In particular, when the torsional vibration damper is to be formed in both relative rotational directions with Gasfederrückstellcharakteristik, it is advantageous if a second supply port is provided in the valve cylinder in association with each Druckfluid- displacement chamber of the first gas spring assembly and in association with each Druckfluidverdrängungskammer the second gas spring assembly. Further, it is possible that in the valve cylinder in Assignment to each pressure fluid displacement chamber of the first gas spring arrangement or the second gas spring arrangement, a second discharge opening is provided. This can for example be realized in that in the valve cylinder one of the number of Druckfluidverdrängungskammem the first gas spring assembly and the number of Druckfluidverdrängungskammem the second gas spring assembly corresponding number of second discharge openings is provided and that depending on the relative rotational position of the primary side relative to the secondary side of the Druckfluidverdrängungskammem the first gas spring arrangement or the Druckfluidverdrängungskammem the second gas spring assembly via the second discharge openings in connection with the first discharge openings can be brought.

In an alternative embodiment variant of the torsional vibration damper according to the invention, it is proposed that the valve cylinder is rotatable with the secondary side and the valve slide is a valve piston which is displaceable in a cylinder opening of the valve cylinder in the direction of the rotation axis and locked against rotation with respect to the valve cylinder.

In order to obtain the displacement of the valve piston, it is proposed that a cam element is provided on the primary side, which cooperates with the valve piston for displacing the same upon relative rotation of the primary side with respect to the secondary side.

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

It is then advantageously provided that the biasing element is arranged in a limited by the valve piston and the valve cylinder chamber and that in the chamber accumulated fluid can be discharged via a drainage channel. In the valve piston, at least a part of the supply area and the discharge area of the rotary feedthrough may be formed.

In order to be able to obtain the supply of pressure fluid to the at least one pressure fluid displacement chamber, it is proposed that at least one radially open first supply opening is formed in the valve piston such that at least one second supply opening is formed in the valve cylinder which communicates via a connection channel the at least one pressure fluid displacement chamber, and in that depending on the relative rotational position of the primary side relative to the secondary side, the extent of overlap of the at least one first supply port with the at least one second supply port is variable.

Equally, to obtain the pressure fluid discharge from the at least one pressure fluid displacement chamber, it may be provided that at least one first discharge opening is provided in the valve cylinder, which is in communication with the at least one pressure fluid displacement chamber via the connection channel, that at least one second discharge opening is provided in the valve cylinder which is in connection with a discharge section of the rotary feedthrough, and in that at least one bypass channel is provided in the valve piston, which establishes a connection between the at least one first discharge opening and the at least one second discharge opening in dependence on the relative rotational position of the primary side relative to the secondary side.

The torsional vibration damper according to the invention can be constructed such that upon relative rotation of the primary side with respect to the secondary side either a connection between the at least one first supply port and the at least one second supply port can be established or via the bypass channel a connection between the at least one first Abführöffnung and the at least one second discharge opening can be produced.

In order to avoid the progressive, so increasing increase in fluid pressure or the

In order to provide Druckfluidzuführmenge, it is further proposed that the at least one first feed opening and / or the at least one second feed

Feed opening is formed with such end profile that during relative rotation of the

Primary side with respect to the secondary side starting from a neutral

Relative rotational position, the extent of overlap of the at least one first

Feed opening with the at least one second feed opening progressively increases.

In order to be able to produce a gas spring damping characteristic in both directions of relative rotation even with such a configuration of the position control valve arrangement, it is further proposed that the at least one pressure fluid displacement chamber of the first gas spring arrangement is in communication with at least one second supply opening via a connection channel and the at least one pressure fluid displacement chamber of the second gas spring arrangement a connecting channel in connection with at least one further second feed opening, and that in dependence on the relative position of the primary side with respect to the secondary side by moving the valve piston, the at least one first feed opening in registration with the at least one second feed opening or at least one further second feed opening can be brought ,

Further, the structure may be such that the at least one pressure fluid displacement chamber of the first gas spring assembly is in communication with at least one first discharge port via the communication channel thereof and the at least one pressure fluid displacement chamber of the second gas spring assembly is in communication with at least one further second discharge port via the communication channel thereof at least one first discharge opening is associated with an at least second discharge opening and a bypass channel and the at least one further first discharge opening at least one further second discharge opening and a further connection channel are assigned.

The two-sided, so to both directions of relative rotation, effective damping characteristic can be generated, for example, that upon displacement of the valve piston in a first displacement direction from the neutral relative rotational position of the primary side relative to the secondary side, the at least one first supply port in communication with the at least one second supply port and the at least one further first discharge opening occurs via the further bridging channel in conjunction with the at least one further second discharge opening, and in that, when the valve piston is displaced in an opposite second displacement direction from the neutral relative rotational position of the primary side relative to the secondary side, the at least one second displacement direction the first feed opening in connection with the at least one further second feed opening and the at least one first discharge opening via the bridging passage in V connection with the at least one second discharge opening occurs.

In an alternative type of flow guidance, it may be provided that when the at least one first supply port is in communication with the at least one further second supply port, the at least one second supply port is in communication with a discharge port via a bypass passage, and then when the at least one first feed opening is in register with the at least one second feed opening, which is at least one further second feed opening via a further discharge opening with a drainage channel in connection.

In order to be able to provide the pressure required for generating the damping force for the pressurized fluid in the torsional vibration damper according to the invention, it is proposed that a pressurized fluid source standing or be brought into connection with the supply region of the rotary feedthrough be provided. This preferably comprises a pressure fluid pump with a pressure fluid pump drive. The pressure fluid pump may be associated with a pressure accumulator. If necessary, the energy stored in a pressure accumulator can be spontaneously released, ie, spontaneously occurring relative rotations between the primary side and the secondary side, so that rotation can be quickly counteracted without delays which would occur, for example, until the start of a pressure fluid pump.

Furthermore, it can be provided that the pressure fluid pump is assigned a pressure limiting valve arrangement for limiting the pressure fluid pressure existing on an outlet side of the pressure fluid pump to a preset value. Such a pressure limiting valve arrangement ensures that the pressure applied to a pressure fluid pump on the supply side of the rotary feedthrough pressure can not exceed a certain maximum value, so that on the one hand defined reset ratios can be ensured, on the other hand can be avoided by an excessively high fluid pressure generated damage to various system components.

A permanent operation of the pressure fluid pump or of the pressure fluid pump drive with high front-efficiencies leading to unnecessary energy losses can be avoided by modifying the pumping capacity of the pressure fluid pump as a function of the pressure fluid pressure present on an output side of the pressure fluid pump. This means that when the pressure fluid pressure present on the output side of the pressure fluid pump increases, the delivery capacity of the pressure fluid pump decreases correspondingly, so that, for example, the pressure fluid pump is only effective in pressure fluid-conveying and correspondingly pressure-increasing manner, if this is actually necessary.

This can be realized, for example, by virtue of the fact that the pressure fluid pump has at least one conveying element whose conveying effect can be changed as a function of the pressure fluid pressure. The provision of the pressure fluid pump with a variable in its conveying action conveying member is particularly advantageous if the pressure fluid pump drive comprises a vehicle drive unit. In this case, ultimately, without making any changes in the operating pressure fluid pump drive, namely to make the drive unit of a vehicle, the delivery behavior can be influenced. This has the consequence that, if this is actually not required, no unnecessary drive power is tapped from the drive unit to activate the pressure fluid pump.

In a further embodiment variant, it can be provided that the pressure fluid pump drive can be activated and deactivated and / or varied in its drive effect as a function of the pressure fluid pressure.

For this purpose, it is particularly advantageous if the pressure fluid pump drive comprises an electric drive motor, the pressure-dependent, so for example switched by a pressure switch, on or off or adjusted in its speed.

According to the present invention, a torsional vibration damper constructed generically or with the features described above is further configured such that the at least one pressure fluid displacement chamber is bounded by a primary side displacement chamber assembly and a secondary side displacement chamber assembly, the primary side displacement chamber assembly comprising two end walls and a peripheral wall, and wherein the secondary-side displacement chamber assembly or an adjoining rotating part of the rotary feedthrough passes through one of the end walls, said end wall having an annular Axialansatz, wherein on the Axialansatz a bearing is radially supported, via which the primary side either with respect to a non-rotating part of the rotary feedthrough or with respect to the secondary-side displacement chamber assembly or the rotating part of the rotary union is stored.

In order to avoid overdetermination in the axial positioning, it is proposed that the bearing is a floating bearing.

The incorporation of such a torsional vibration damper in a drive system can be particularly simple in that the rotating part of the rotary feedthrough a Formschlusseingriffsformation, preferably Hirth toothing, for torque-transmitting coupling having a following assembly.

Brief description of the drawings

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

Fig. 1 is a circuit diagram-like representation of a known torsional vibration damper;

Fig. 2 is a representation corresponding to Figure 1 of a torsional vibration damper according to the invention.

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

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

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

Fig. 6 is a perspective view of the secondary side of the torsional vibration damper of Fig. 4; 7 is a perspective view of a cross-sectional view of the torsional vibration damper of FIG. 4, cut in a plane VII - VII in FIG. 4;

Fig. 8 is a perspective view in cross-section of the torsional vibration damper shown in Fig. 4, taken in a plane VIII - VIII in Fig. 4;

FIG. 9 shows a representation corresponding to FIG. 7 in a deflection state of the primary side with regard to the secondary side; FIG.

FIG. 9a shows a representation corresponding to FIG. 8 in the deflection state; FIG.

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

11 is a perspective view of a longitudinal section of the torsional vibration damper of FIG. 10;

FIG. 12 is a view of an assembly comprising a cam member and a valve piston; FIG.

Fig. 13 is a perspective view of the cam member;

Fig. 14 is another perspective view of the cam member;

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

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

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

FIG. 18 shows a view corresponding to FIG. 10 of a modification of the second embodiment variant; FIG.

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

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

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

BEST MODE FOR CARRYING OUT THE INVENTION FIG. 2 shows a torsional vibration damper 10 constructed in accordance with the invention, comprising two gas spring arrangements 18, 20, wherein the gas spring arrangement here comprises two pressure fluid displacement chambers 22, 22 'and the gas spring arrangement 20 comprises the two pressure fluid displacement chambers 24, 24'. includes. Upon 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 'of the gas spring assembly 18 are reduced under appropriate compression and Reducing the volume of these pressure fluid displacement chambers 22, 22 'associated gas volumes of the gas spring assembly 18. When relative rotation in the opposite direction, the volumes of

Pressure fluid displacement chambers 24, 24 'reduced, with the result that the pressure fluid displacement chambers 24, 24' associated gas volumes of the gas spring assembly 20 are compressed.

In the non-rotating system area only a single pressure control valve 60 is provided which is under control of the drive device 28. The pressure regulating valve 60 can be brought into two positions in which a pressure fluid line 62 leading to the rotary leadthrough 38 is either in connection with the pressure fluid source 50 or with a return region 64. The pressure in the pressure fluid line 62 is detected by a pressure sensor 66 whose signal is fed to the drive device 28. Based on this pressure signal, the drive device 28 controls the pressure control valve 60 in such a way that in the pressure fluid line 62, a defined fluid pressure can be adjusted. A fluid line 66 connects the rotary leadthrough 38 to the fluid reservoir 48. This has the consequence that the rotary leadthrough 38 basically provides a supply region 68, ie that region which also forms 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 pressure fluid source 50, provides. A discharge region 70 of the rotary leadthrough 38 is substantially depressurized, since it is in communication with the likewise pressureless fluid reservoir 48 via the fluid line 67.

In the rotating system portion of the torsional vibration damper 10, a position control valve, generally designated 72, is provided. This position control valve 72 thus rotates with the primary side 12 and the secondary side 14 about an axis of rotation of the torsional vibration damper 10. The position control valve 72 has a valve cylinder 74 indicated only schematically in FIG. 2 and a valve slide 76 movably therein. By a dashed line indicated mechanical coupling of the valve cylinder 74 and the valve spool 76 with the primary side 12 and the secondary side 14, a relative movement between the valve cylinder 74 and valve slide 76 can be obtained. As a result, depending on the position of the position control valve 76, either the two pressure fluid displacement chambers 22, 22 'are in communication with the supply area 68, while the pressure fluid displacement chambers 24, 24' are in communication with the discharge area 70, or vice versa The pressurized fluid displacement chambers 24, 24 'are in communication with the supply area 68 while the pressure fluid displacement chambers 22, 22' are in communication with the discharge area 70, or the pressure fluid displacement chambers 22, 22 ', 24, 24' are substantially completely closed to fluid exchange, Thus, essentially none of the pressure fluid displacement chambers 22, 22 ', 24, 24' is in connection with the discharge region 70 or is also in connection with the supply region 68. The latter state will generally be reached when the primary side 12 is in a neutral relative rotational position relative to the secondary side 14, that is, for example, substantially no torque is transmitted via the torsional vibration damper 10. The two other states, in which each one of the gas spring assemblies 18 and 20 associated pressure fluid displacement chambers 22, 22 'and 24, 24' in connection with the supply line 68 are states in which the primary side 12 with respect to the secondary side 14 in each case one of the possible relative directions of rotation is deflected.

With such a torsional vibration damper 10, the control effort can be significantly reduced while simultaneously simplifying the hydraulic circuit. The position control valve 72 will automatically set a defined fluid supply or fluid discharge to the respective gas spring assemblies 18, 20 without any activation measures solely through the mechanical coupling to the primary side 12 or the secondary side 14. It is then only necessary to ensure that a defined fluid pressure is provided at the supply region 68 by means of the only pressure regulating valve 60 arranged outside the rotating system region, 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.

Various design variants of a torsional vibration damper 10 or in particular a position control valve 72 will be described below.

A first embodiment variant is shown in FIGS. 3 to 9. 3 shows the basic structure of the torsional vibration damper 10 with the primary side 12 and the secondary side 14. The primary side 12 is constructed with two axially spaced disc parts 80, 82, which are radially outwardly by a cylindrical wall 84 are connected, which may be formed integrally with the disc part 80, for example. From this cylindrical wall 84 extend at an angular distance of 180 ° two dividing walls 86, 86 'radially inward.

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

The gas spring assemblies 18, 20 comprise a plurality of approximately radially extending cylinders 96 distributed outside the cylindrical wall 84. A portion of these cylinders 96 are associated with the first gas spring assembly 18, while the remaining portion is associated with the second gas spring assembly 20. Contained in each of the cylinders 96 is a schematically indicated gas volume 98 which is separated by a separating element 99, for example a piston displaceable in a cylinder 96, from the pressure fluid of that pressure fluid displacement chamber or pressure fluid displacement chambers with which a respective cylinder 96 cooperates. Thus, all cylinders 96 associated with the first gas spring assembly 18 may cooperate with both pressure fluid displacement chambers 22, 22 ', i. via respective connecting chambers with these in conjunction, while correspondingly all cylinder 96 of the second gas spring assembly 20 with all Druckfluidverdrängungskammem 24, 24 'can cooperate. Of course, it is also possible to assign each pressure fluid displacement chamber own gas volumes 98 and cylinder 96, which can then be acted upon only by the pressure fluid in this respective pressure fluid displacement chamber. The cooperating with the or the Druckfluidverdrängungskammem a respective gas spring assembly 18 and 20, gas volumes 98 then form the loaded at the effective date of a respective gas spring assembly and the spring characteristic unfolding "gas volume".

With relative rotation of the primary side 12 relative to the secondary side 14, starting from the neutral relative rotational position shown in FIG. 3, for example, the volumes of the pressure fluid displacement chambers 22, 22 'are reduced by the fact that the partition walls 86 and 90' approach each other, as well as the partition walls 86 The fluid then displaced from the pressurized fluid displacement chambers 22, 22 'then loads the gas volumes 98 enclosed in the associated cylinders 96 via the connecting chambers, not shown, with corresponding compression thereof. 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 'upon relative rotation of the opposite direction. In the central region of the torsional vibration damper 10, the position control valve 72 is arranged. Its structure or function will be explained in detail below with reference to FIGS. 4 to 9.

It can be seen in Fig. 4, the valve spool 76 of the position control valve 72 which is fixedly connected to the substantially cylindrical member 88 of the secondary side 14, that is rotatable about this with the rotation axis A. In a corresponding manner, the valve cylinder 74 with the primary side 12, here the disk part 80 is firmly connected and thus rotatable with the primary side 12. The valve spool 76, so the rotary valve, at the same time forms part of the rotary feedthrough 38, namely a radially inner and rotating with the torsional vibration damper 10 part. In FIG. 4, the supply line region 68 of the rotary leadthrough 38 can be seen to lie on the right-hand side, whereby a corresponding configuration for the discharge region 70 can be provided on the left-hand side in the non-illustrated part of the valve slide 76. A supply section 98 is formed as a central bore or opening in the valve spool 76. Near the axial end of the valve spool 76, this supply region 98 is open via openings 100 radially outward. Axially on both sides of these openings 100, sealing elements can be provided which generate a substantially fluid-tight closure of these openings or corresponding openings in a non-rotating part of the rotary leadthrough 38. Axially adjacent to the feed region 98, for example, a discharge section 102 is likewise formed coaxially to the axis of rotation A in the valve slide 76. This can also be open radially beyond the openings, not shown, to then connect to the fluid line 66 via a connection with a likewise non-rotating part of the rotary feedthrough 38, which is shown in FIG. Between the supply line section 98 and the discharge section 102 is located a partition 104 which prevents direct flow of the pressurized fluid from the supply section 68 to the discharge section 70.

At its end region located inside the valve cylinder 76, the supply section 98, as can also be seen in FIG. 7, is open radially outward via two first supply openings 106, 106 'which are arranged at an angular distance of 180 ° from each other and open radially outwards. In the valve cylinder 74 four second supply ports 108, 108 ', 108 "and 108"' are provided. These four second feed openings 108, 108 ', 108 "and 108"' are arranged relative to one another such that in the neutral relative rotational position of the secondary side 14 with respect to the primary side 12 also shown in FIG. 7, no connection or overlapping between the first feed openings 106 , 106 'and the second feed openings 108, 108', 108 "and 108" '.

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

FIG. 8 shows the torsional vibration damper 10 of FIGS. 3 and 4 cut in another plane orthogonal to the axis of rotation A. It can be seen in Fig. 8 in the valve spool 76 Abführabschnitt 102, here via four with an angular offset of 180 ° to each other radially open first discharge openings 116, 116 ', 116 "and 116'" radially outward, ie to the Cylinder opening 114 is open. In the valve cylinder 74 two arranged at an angular distance of 180 ° second discharge openings 118, 118 'are provided. In the case of the neutral relative rotational position of the primary side 12 with respect to the secondary side 14, which can be seen in FIG. 8, the first discharge openings 116, 116 ', 116 "and 116'" are arranged with respect to the two second discharge openings 118, 118 'such that there is no overlap and thus no fluid exchange can take place.

In the cylindrical component 88 of the secondary side 14 four discharge channels 120, 120 ', 120 "and 120'" are provided. These discharge channels 120, 120 ", 120" and 120 "'are in each case associated with one of the pressure fluid displacement chambers, for example, the discharge channel 120 can be assigned to the pressure fluid displacement chamber 22, the discharge channel 120" can be assigned to the pressure fluid displacement chamber 22', the discharge channel 120 'can be assigned. may be associated with the pressure fluid displacement chamber 24 and the discharge channel 120 '' may be associated with the pressure fluid displacement chamber 24 '.

In the relative positioning of the primary side 12 relative to the secondary side 14, which also corresponds to the relative positioning shown in FIG. 3, there is neither a connection of the pressure fluid line 62 to any of the pressure fluid displacement chambers 22, 22 'at the feed region 68, 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. When torque transmission or torsional vibration, the primary side 12 rotates with respect to the secondary side 14 in a first direction of relative rotation, so For example, it can be seen that the valve cylinder 74 and with it the primary side has rotated counterclockwise relative to the secondary side 14. This results in the pressure fluid displacement chambers 22, 22 'being compressed or compressed have been reduced in volume and that further The first supply ports 106, 106 'overlap the second supply ports 108, 108 "while the second supply ports 108' and 108 '" are still closed. In this state, so the Zuführabschnitt 98 of Feed section 68 of the rotary feedthrough 38 via 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 conjunction with the pressure fluid line 62nd It can thus be further increased by appropriate control of the pressure control valve 60 and the pressure of the pressure fluid in these pressure fluid displacement chambers 22, 22 ', which causes an increased "spring stiffness" and a correspondingly increased restoring force in the direction of neutral relative rotational position. During this rotation, as can be seen in FIG. 9 a, an overlap of the second discharge openings 118, 118 'with the first discharge openings 116', 116 "'is likewise established in the discharge area 70, 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 are.

With the position control valve 72, it is thus possible, depending on the direction of relative rotation of the primary side 12 with respect to the secondary side 14 selectively generate a connection of the pressure fluid source 50 with the pressure fluid displacement chambers 22, 22 'of the first gas spring assembly 18 or the pressure fluid displacement chambers 24, 24' of the second gas spring assembly 20 , which is then ensured by this connection 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' are closed by no overlapping of the various supply openings. In order to avoid a pressure surge by spontaneously establishing the connection with the pressure fluid source 50 at the beginning deflection from the neutral relative rotational position, as shown in Fig. 7, the second feed openings 108, 108 ', 108 "and 108"' each with by bevels or bevels 122 profiled edges limited. Upon deflection, first of all, these chamfering regions 122 overlap the first supply openings 106, 106 ', so that initially only a small, gradually increasing connecting cross-section exists, which is a gradual one Pressure increase ensured while only at larger angles of rotation then a greater increase of the connecting cross-section is generated. It is of course possible to ensure a defined progressive course of the connecting cross-section through the most varied profiling of the walls which bound the second supply openings 108, 108 ', 108 ", 108'" when the cover is produced with the first supply openings 106, 106 '. 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 rotational position there is a slight overlap of the first connection openings 106, 106 'with all second connection openings 108, 108', 108 ", 108 '". Thus, the pressure of the pressure fluid source 50 is then applied to all pressure fluid displacement chambers 22, 22 ', 24, 24'. 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 there is a permanent fluid outflow in the direction of the discharge region 70 due to leaks which occur forcibly in interspaces. Upon deflection from the neutral relative rotational position, the overlap of the first supply openings 106, 106 'with two mutually opposite ones of the second supply openings 108, 108', 108 "and 108" 'increases, while the overlap, which is still present, with the other two second ones Zuführöffnungen decreases or is reduced to zero.

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

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

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

In the embodiment shown in Figs. 10 to 17, the valve cylinder 74a of the position control valve 72a is fixedly connected to the secondary side for common rotation. The valve slide 76a is designed here as a valve piston movable in the direction of the axis of rotation A and displaceable in the opening 114a formed in the valve cylinder 74a. Connected to the primary side 12a and the disk part 80a for common rotation is a cam member 130a which cooperates with the valve spool 76a to displace it. This assembly is shown in Fig. 12 enlarged. It can be seen the cam member 130a with in Fig. 13 and in Fig. 14 also visible cam surfaces 132a, 134a. With a circular disk-like body portion 136a, the cam member 130a is received in a corresponding recess of the primary side 12a such that it is basically rotatable with this primary side 12a by inserting a tool into a tool receiving recess 138a, for example one Allen opening, but for setting the positioning is rotatable.

The valve spool 76a has an axial extension 140a which cooperates with the two cam surfaces 136a, 138a. Furthermore, this extension 140a, which is rectangular in cross-section, is guided through a corresponding recess 142a of a disk-like locking element 144a shown in FIG. This locking element 144a is received in the opening 114a of the valve cylinder such that it permits an axial displacement of the valve slide 76a, but this can not rotate in the valve cylinder 76a. A rotation of the rotationally fixed to the primary side 12a cam member 130a with respect to the secondary side 14a and thus the thus non-rotatable assemblies valve cylinder 74a and valve spool 76a thus has a consideration of Fig.10 or Fig. 11, a displacement of the valve spool 76a in the direction of the axis of rotation Episode. In order to ensure that the extension 140a is permanently in contact with the cam surfaces 136a, 138a, between a bottom 146a of the valve cylinder 74a and an axial end surface 148a of the valve spool 76a is a biasing spring element 150a, for example in the form of a helical compression spring, indicated in FIG effective. This biasing spring member 150a biases the valve spool 76a toward the cam member 130a so that relative rotation of the primary side 12a with respect to the secondary side 14a in a first relative rotational direction causes displacement of the spool 76a in a first displacement direction with respect to the valve cylinder 74a and relative rotation in the opposite direction Relative direction of rotation also causes a shift in the opposite direction of displacement.

In the valve spool 76a, a substantially axially extending feed section 98a is formed in the central region. This is open via radial openings 100a to a circumferential groove 152a, so that the corresponding openings in the valve cylinder 74a are opposite and thus allow a fluid supply via the rotary leadthrough 38a. It can be seen in Fig. 10 that the valve cylinder 74 a with its outer peripheral portion of a part of Drehdurchfϋhrung, in particular the feed area 68a, provides.

Axially offset from the openings 110a, the valve spool 76a has radially outwardly open first supply openings 106a, which are open radially outwards in a circumferential groove 154a provided on the outer circumference of the valve spool 76a.

On the valve cylinder 74a, second feed openings 108a and 108a ^{1 are} provided at an axial distance from one another and distributed over the circumference. In the case of a neutral relative rotational position that can be recognized in FIG. 11, the first feed openings 106a and the circumferential groove 154a are positioned such that substantially no overlaps exist with the second feed openings 108a or 108a ¹ lying on either side thereof.

The second feed openings 108a and 108a ', respectively, are open radially outward to annular spaces 156a and 156a' extending circumferentially about the axis of rotation A, respectively. The pressure fluid displacement chambers 22a and 22a 'respectively associated with the first gas spring arrangement 18a are in each case connected to the annular space 156a via a connection channel, of which FIG. 10 shows the connection channel 158a assigned to the pressure fluid displacement chamber 22a. Likewise, the pressure fluid displacement chambers 24a, 24a ^{1 of} the second gas spring assembly 20a, of which only the pressure fluid displacement chamber 24a is seen in FIG. 10, are coupled to the other annulus 156a ¹ via respective communication channels 160a (associated with the pressure fluid displacement chamber 24a). Each of these communication passages 158a respectively forms one of the pressure fluid displacement chambers 22a, 22a 'of the first gas spring assembly 18a, 160a for each of the pressure fluid displacement chambers 24a, 24a ^{1 of} the second gas spring assembly 20a, as set forth below, both a pressurized fluid supply channel and a channel for the removal of pressurized fluid.

In each case axially outside the second supply openings 108a and 108a ', first discharge openings 162a and 162a' are provided in the valve cylinder 74a. These are also open to the spaces 156a and 156a ¹ and thus also in connection with the connecting channels 158a, 160a. Further axially removed with respect to the second supply opening 108 or 108a ¹ , second discharge openings 164a or 164a 'are formed in the valve cylinder 74a, wherein the second discharge opening 164a ¹ on the left in FIG. 11 can also be seen substantially through the axial end of the valve cylinder 74a. the disk part 80a of the primary side 12a and the cylindrical part 88a of the secondary side 14a are limited. The two second discharge openings or respectively groups of discharge openings 164a, 164a ¹ are provided via discharge sections 170a, of which several can be provided circumferentially around the axis of rotation, in conjunction with another part of the rotary feedthrough 38a which provides the discharge area 70a and which now is cylindrical Component 88 a of the secondary side 14 a and is formed with a larger diameter than the formed on the valve cylinder 74 a portion of the rotary leadthrough 38 a.

In association with each pair, comprising in each case one or more first discharge openings 162a, 162a ¹ and axially offset therefrom one or more second discharge openings 164a, 164a ¹ , a bypass channel 166a or 166a ¹ open radially outward is formed in the valve slide 76a. Here, in particular, the bridging channel 166a ^{1, which can be seen} on the left in FIG. 11, is essentially also formed in the region of the axial end of the valve slide 76a, that is to say in the region in which the extension 140a is located. Further, in the locking member 142a, two openings 168a are formed, which allow the passage of fluid through this bypass channel 166a ¹ .

The configuration is such that when the primary side 12a and the secondary side 14a are in the neutral relative rotational position with respect to each other, on the one hand the first supply ports 106a are out of registration with the second supply ports 108a and also out of register with the other second supply ports 108a ¹ are. This means that the feed area 68a of the rotary leadthrough 38a is not connected to any of the connection channels 158a, 160a leading to the different pressure fluid displacement chambers. In the same way, the two are axially offset from each other Bridging channels 166a, 166a ¹ are arranged in this situation so as to be in register with the second discharge openings 164a and 164a ¹ , respectively, but are not in register with the first discharge openings 162a, 162a '. Thus, also, the discharge portion 70a of the rotary leadthrough 38a is not in communication with any of the pressure fluid displacement chambers.

If a rotation of the primary side 12a with respect to the secondary side 14a in a first direction of relative rotation takes place starting from the neutral relative rotational position, this results from the interaction of the cam element 130a with the extension 140a on the valve slide 76a, as can be seen in FIG , the valve spool 76a is displaced with respect to the valve cylinder 74a, for example, so as to be moved to the left in the illustration of FIG. This means that the first supply openings 106a overlap with the second supply openings 108a ¹ via the annular groove 154a surrounding them. It is thus made via the annular space 156a 'a connection with the connecting channels 160a, which in turn connect to the pressure fluid displacement chambers 24a, 24a' produce. The first discharge openings 162a 'remain closed in this state or in this phase by the valve spool 76a. By the displacement of the valve spool 76a, however, the bypass passage 166a now also coincides with the first discharge openings 162a on the other axial side of the first supply openings 108a and 108a ', while the second supply openings 108a continue to be closed by the valve spool 76a. Thus, via the annular space 156a now leading to the pressure fluid displacement chambers 22 and 22a connecting channels 158a in connection with the recognizable in Fig. 11 Abführabschnitten 170a and thus the discharge region 70a of the rotary feedthrough 38a. This means that the fluid pressure in the pressure fluid displacement chambers 24a, 24a 'reduced in volume in this state is increased by the connection to the pressure fluid line 62 recognizable in FIG. 2 and thus the pressure fluid source 50, while the enlarged in volume pressure fluid displacement chambers 22a, 22a 'in conjunction with the recognizable in Fig. 2 and leading to the fluid reservoir 48 fluid line 66 are brought or stand. By the extent of the overlap, so also the extent of the axial displacement of the valve spool 76a, which corresponds to the extent of the relative rotation between the primary side 12a and the secondary side 14a, the flow or connection cross-section is influenced.

In the case of the relative rotation illustrated in FIG. 17 in the other direction of relative rotation, the pressure fluid displacement chambers 22a, 22a ¹ recognizable in FIG. 17 are reduced in their volume. At the same time, by the cooperation of the cam member 130a with the projection 140a of the valve spool 76a, this valve spool 76a is now displaced in the opposite axial direction against the biasing action of the above-mentioned spring 150a. As a result, the first supply openings 106a are now brought into registry with the second supply openings 108a via the surrounding annular groove 154a, while the second supply openings 108a 'located on the other axial side remain closed. Thus, there is a connection between the feed section 98a and the annular space 156a, in which the connecting channels 158a leading to the pressure fluid displacement chambers 22a, 22a 'open. The first discharge openings 162a remain closed in this state by the valve spool 76a. However, the further first discharge openings 162a ¹ located on the other axial side are now connected via the bypass channel 166a 'formed at the axial end region of the valve slide 76a to the further second discharge opening 164a ¹ located at the axial end of the valve cylinder 74a and thus also in the Fig. 11 recognizable Abführabschnitten 170a. This means that in this relative rotational state, the two pressure fluid displacement chambers 22a, 22a ^{1 are} in communication with the pressure fluid source 50, while the other pressure fluid displacement chambers 24a, 24a ^{1 are} in communication with the fluid reservoir 48.

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 also present or associated therewith are more compressed, while the gas volumes assigned to the other gas spring arrangement are expanded. By increasing the fluid pressure also via the position control valve 72a, it is possible to bring the primary side 12a accelerated in the neutral relative rotational position with respect to the secondary side 14a and to keep in this.

Again, it is possible to ensure that in the neutral relative rotational position all Druckfluidverdrängungskammern are completely completed or by

Providing a slight overlap of the annular groove 154a with both the second supply ports 108a and the other second supply ports

108 a ^{1 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 and the second

Feed openings 108a, 108a 'possible to achieve a progressive increase of the connection cross-section in the production of an overlap.

A further embodiment variant of a torsional vibration damper 10a is shown in FIG. This embodiment variant corresponds in many areas to the embodiment shown with reference to FIGS. 10 to 17, so that the essential differences are discussed below.

First of all, it should be noted that in FIG. 18, not only the rotary part of the rotary feedthrough provided substantially by the valve cylinder 74a

38a is recognizable, but also the stationary, non-rotating part 200a. This surrounds the rotating part, ie the valve cylinder 74a. About a example designed as a ball bearing fixed bearing 202a and a example as a Loselager

(Needle bearing o. The like.) Formed bearing 204 a, the valve cylinder 74 a and the stationary part 200 a of the rotary leadthrough 38 a are mounted radially with respect to each other.

It can be seen further in FIG. 18 that this provides an end wall Disk part 82a, which together with the one further end wall providing disk part 80a and the cylindrical wall 84a provides a primary-side displacement chamber 206a has an axially projecting, annular projection 208a, which surrounds the rotating part of the rotary feedthrough 38a, so the valve cylinder 74a, radially outward. Between this projection 208a and the rotating part, a loose bearing 210a designed, for example, as a needle bearing is provided, which supports a radial guidance of the primary-side displacement chamber assembly 206a with respect to a fluid displacement chambers radially inwardly delimiting secondary-side displacement chamber assembly 212a. This secondary-side displacement chamber assembly 212a, in which also the various connection channels 158a, 160a, which are not visible in FIG. 18, extend to the pressure fluid displacement chambers, is non-rotatable with the valve cylinder 74a. This is further supported at its left in Fig. 18 axial end via another loose bearing 214a, for example, also needle bearing, radially on the other disc part 80a. Thus, the primary-side displacement chamber assembly 206a via the two bearings 214a, 210 with respect to the valve cylinder 74a, so the rotating part of the rotary leadthrough 38a stored, while on the two bearings 204a and 202a, this rotating part of the rotary feedthrough 38a is mounted relative to the stationary part 200a. The defined Axialrelativpositionierung of the rotating assemblies with respect to the stationary part 200a of the rotary feedthrough 38a via the fixed bearing 202a.

In the stationary part 200a of the rotary leadthrough 38a, there is provided a supply port 216a for the pressurized fluid supplied from a source of pressurized fluid.

Over at least one opening 218a formed in the valve cylinder 74a is this

Feed port 216 a to the radial openings 100 a in the valve spool 76 a open. The pressurized fluid thus passes independently of the axial positioning of the

Valve spool 76a via the radial openings 100a in the axially extending feed section 98a and thus to the radially outwardly open first feed openings 106a. In the neutral position shown in Fig. 18, these first supply ports 106a are closed. Shifts the valve spool 76a starting from the positioning shown in FIG. 18 to the left, the first supply ports 106a are associated with the second supply ports 108a ¹ formed in the valve cylinder 74a and thus with the associated pressure fluid displacement chambers via the communication channels communicating therewith and not shown. The second supply openings 108a are then in this state via the bridging channel 166a formed on the valve spool 76a and opening radially outward in connection with a discharge port 220a in the stationary part 200a of the rotary union 38a, which in this embodiment is at the same radial level as the supply port 216a. While in this state the pressurized fluid supplied via the supply port 216a to the pressure fluid displacement chambers connected to the second supply ports 108a 'may be discharged, pressurized fluid may be discharged from the pressurized fluid displacement chambers communicating with the second supply ports 108a and the bypass passage 166a and the drain port 220a, respectively.

When displaced in the opposite direction, the first supply ports 106a are then in communication with the second supply ports 108a, and thus the pressure fluid displacement chambers associated therewith. The second feed openings 108a ¹ and thus also the associated Druckfluidverdrängungskammem are no longer covered by the axial end portion of the valve spool 76a, so that over a substantially of the axial end of the valve spool 76a and the valve cylinder 74a limited bridging channel 166a ¹ and an adjoining Outlet opening 164a 'fluid can be passed through a channel not visible in FIG. 18 in the region of the two bearings 210a, 204a. This volume region can be emptied via a drainage channel 222a formed in the non-rotating part 200a of the rotary union 38a. This drainage passage 222a leads to a drainage port 224a in the non-rotating part of the rotary feedthrough 200a.

One recognizes further that in the transition area between the non-rotating Part 200a and the rotating part 74a of the rotary feedthrough 78a on both sides of the feed port 216a pressure seals 226a, 228a are provided. Also on both sides of the discharge port 220a such pressure seals 230a, 232a are provided. 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, two mass flow seals 234a, 236a continue to be provided. A drainage channel 238 opens into the region between the two groups of pressure seals 226a, 228a or 230a or 232a. A drainage channel 240 opens into the region between the pressure seal 226a and the mass flow seal 234a, and a further drainage channel 242a opens into the region between the pressure seal 232a and the mass flow seal 236a in addition to the already described leakage channel 222a. All of these drainage channels lead to the leakage connection 224a.

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

When integrating such a torsional vibration damper 10a in a drive system of the valve cylinder 74a, including the rotating part of the rotary feedthrough 38a, for torque transmission from the secondary side to a subsequent assembly, such as a clutch o. The like .. For this purpose, the front end 252a of the valve cylinder 74a with an engagement formation, for example, be designed in the manner of a Hirth toothing, which then in Drehkopplungseingriff brought with a corresponding formation on the following module and the like by a clamping element. can be held.

In Fig. 19, a further embodiment of an inventively constructed torsional vibration damper is shown in principle representation. This corresponds in terms of structural design, in particular the primary side

12, the secondary side 14, the position control valve 72 and various associated with this system areas, for example, the embodiment variants described above in detail. In this respect, the same components or system areas are also designated by reference symbols, as they were previously used, in particular also in FIG. 2.

19, the pressure fluid pump, generally designated by the reference numeral 46, can be seen in the lower region with a pressure fluid pump drive 300 and a pressure fluid pump delivery region 302. In the example shown, the pressure fluid pump drive 300 is provided by a drive unit, for example an internal combustion engine 304 of a vehicle. This engine 304 drives the pressure fluid pump delivery area 302 in a permanently coupled manner to deliver pressurized fluid from the fluid reservoir 48 into the conduit 62 leading to the rotary union 38 in which a check valve, generally designated 306, is located. The pressurized fluid delivery region 302 can be designed in various ways, that is to say with different delivery elements, which contribute to the conveyance 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 region 302 thereof is assigned a pressure-dependent effective adjustment arrangement 308. This accesses the pressure of the pressure fluid prevailing in the line 62, that is to say on the output side of the pressure fluid pump 46, and adjusts the conveying capacity of the pressure fluid conveying area 302 in accordance with this tapped pressure. For this purpose, a delivery device 302 acting on the pressurized fluid conveying region, for example a conveying element acting therein, acting, depending on the pressure fluid displaceable adjusting plunger 310 may be provided which contributes directly or indirectly with such a conveying member for varying the conveying effect. For example, in the case of a lifting piston designed as a delivery member, it is possible to vary by an eccentric the stroke of the reciprocating piston and thus also the amount delivered per stroke. In their conveying capacity variable fluid pumps are known in the art and therefore need not be further described here. It is important here, however, that the size acting on such a variable pressure fluid pump is itself the pressure fluid pressure that is also essentially provided by this pump and tapped in the supply area to the rotary feedthrough 38. It is thus ensured that, despite the permanently existing drive connection with the pressure fluid pump drive 300, when the pressure fluid pressure in the supply region 68 is sufficiently high, the conveying capacity is reduced and therefore virtually no further pressure increase is generated by the pressure fluid pump 46 and thus by the drive unit 304 worn drive energy share can be reduced.

The pressure fluid pump 46 is further associated with a pressure accumulator 312, which stores pressure fluid or energy. Occur spontaneous relative rotation between the

Primary side 12 and the secondary side 14 on, the pressure accumulator 312 can spontaneously deliver pressurized pressurized fluid, so that correspondingly spontaneously occurring relative rotations can be counteracted. For this purpose, it is for example advantageous to design the pressure accumulator so that the pressure fluid volume required in such spontaneous changes in the

Essentially completely by this can be provided. For example, it is advantageous for a maximum required volume flow of

35 l / min form the pressure accumulator with a storage volume of about 250 ml. This makes it possible to dimension the pressure fluid pump 46 correspondingly smaller, so to design with a lower maximum delivery rate.

The pressure fluid pump 46 is further associated with a pressure limiting valve 314, which discharges pressure fluid in the direction of the fluid reservoir 48 when the pressure in the line 62 rises above a preset value and thus provides a pressure limitation. The further provided pressure sensor 66 detects the pressure fluid pressure present on the output side of the pressure fluid pump 46 and, if an unexpected or excessively high rise occurs, can provide a corresponding signal which can lead, for example, to an emergency shutdown or a corresponding diagnosis.

FIG. 19 shows a torsional vibration damper 10, which is essentially completely self-sufficient, that is to say without any control technology

Interaction with other system components of a vehicle can work.

Both the position control valve 72, as well as the pressure fluid source 50 work alone triggered by respective occurring in the system itself variables, in particular

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 manually to be shifted transmission. Unlike

In the case of transmissions to be manually shifted, automatic transmissions do not have any system states or size-defining signal values or control variables which can also be used in the torsional vibration damper 10. However, this is basically not necessary in the structure shown in FIG. 19.

A modification of this system is shown in FIG. In the following, only the differences to the embodiment according to FIG. 19 will be explained. It can be seen in Fig. 20 that the pressure fluid source 50 again the

Pressure fluid pump 46 with the example provided by an internal combustion engine 304 pressure fluid pump drive 300 comprises. the

Druckfluidpumpenförderbereich 302, however, no adjustment arrangement is assigned, so that when the drive unit, so the internal combustion engine 304, in

Operation is set, according to the pressure fluid pumping region 302 operates and promotes pressurized fluid. Because of this permanent mode of action comes to the pressure relief valve 314, which is arranged in this embodiment with respect to the check valve 306 pump side, of particular importance, since due to the permanently present conveying effect of the pressure fluid pump 46, even if no relative rotation between the primary side 12 and the secondary side 14 occurred over a long time This means that if such a situation exists without consumption of pressurized fluid, permanent fluid is circulated permanently via the pressure limiting valve 314. Although this entails a greater expenditure of energy because of an increase in pressure However, a larger proportion of the drive energy is tapped from the internal combustion engine 304, but simplifies the structure compared to the embodiment variant shown in Figure 19. The variant shown in Fig. 20 is therefore particularly in systems into consideration, in which a more or less cont Inuierlicher consumption of pressurized fluid is present, as for example in very large-sized vehicle drives, such. B. in marine propulsion, the case.

FIG. 21 shows a further modification of the embodiment variant shown in FIG. 19. The pressurized fluid source as the pressurized fluid pump drive 300 here includes an electric drive motor 316 that drives the pressurized fluid pump delivery area 302. A pressure switch 318 engages the existing on the line 62

Pressure fluid pressure and leads to a corresponding activation or deactivation of the electric drive motor 316. So exceeds the pressure in the line 62 and in the pressure accumulator 312 an upper limit, the electric drive motor 316 is turned off. If the pressure falls below a lower limit, the electric drive motor 316 is switched on again. This also makes it possible to ensure that in the region of the line 62 and also of the pressure accumulator 312 with a completely self-sufficient operation of the system permanently for a sufficiently high pressure can be provided. It should be noted here that, of course, the electric drive motor 316 may also be associated with a drive device which receives, for example, the pressure signal of the pressure sensor 66 and accordingly affects the drive behavior of the electric drive motor 16, thus increasing or decreasing the drive speed to one maintain a relatively constant pressure fluid pressure in line 62. However, a completely autonomous mode of operation is also ensured in this case, since no control-technology connection to 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 even in a start phase of a drive system by prior activation of the pressure fluid pump 46 are ensured can that sufficient pressure is present when the rotational speed of a drive train is moving up in the direction of idling speed while a resonant frequency range of the torsional vibration damper 10 is traversed.

Claims

claims

A torsional vibration damper comprising a primary side (12; 12a) and a secondary side (14; 14a) rotatable against the action of a damper assembly with respect to the primary side (12; 12a) about an axis of rotation (A);

Damper arrangement comprises at least one gas spring arrangement (18, 20, 18a, 20a) comprising a pressurized gas volume (98) and at least one pressure fluid displacement chamber (22, 22 ', 24, 24 "; 22a, 22a ¹ , 24a, 24a ¹ ) Volume with 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 supplying / removing pressurized fluid characterized by a position control valve assembly (72; 72a) in the pressurized fluid flow path between the rotary union (38; 38a) and the at least one pressurized fluid displacement chamber (22,22 ', 24,24'; 22a, 22a ¹ , 24a, 24a '), wherein in dependence 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 ¹ , 24a, 24a ¹ ) having a supply region (68; 68a ) of the rotary feedthrough (38; 38a) or with a discharge region (70; 70a) of the rotary feedthrough (38; 38a) is connectable.

A torsional vibration damper according to claim 1, characterized in that the damper assembly comprises at least one first gas spring assembly (18; 18a) and associated therewith at least one pressure fluid displacement chamber (22,22 "; 22a, 22a ¹ )

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 ¹ ). and at least one second gas spring assembly (20; 20a) and associated therewith at least one pressure fluid displacement chamber (24,24 '; 24a, 24a ¹ ), the first gas spring assembly (18; 18a) being compressed; 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 from the first relative direction of rotation by the at least one pressure fluid displacement chamber (24, 24 '; 24a, 24a ¹ ) of the second

Gas spring assembly (20; 20a) displaced compressed fluid is compressed.

Torsional vibration damper according to claim 2, characterized in that the position control valve arrangement (72; 72a), when the at least one pressure fluid displacement chamber (22, 22 ';

22a ¹ ) of the first gas spring arrangement (18; 18a) with the discharge region (70;

70a) of the rotary union (38; 38a) connecting at least one

Pressure fluid displacement chamber (24, 24 "; 24a, 24a ¹ ) of the second

Gas spring assembly (20; 20a ¹ ) with the supply area (70; 70a) of the rotary feedthrough (38; 38a) connects, and if they at least one pressure fluid displacement chamber (24,24 '; 24a, 24a ¹ ) of the second

Gas spring arrangement (20; 20a) with the discharge region (70; 70a) of

Rotary union (38, 38a) connects, the at least one

Pressure fluid displacement chamber (22, 22 ', 22a, 22a ¹ ) of the first gas spring assembly (18; 18a) with the supply region (68; 68a) of the

Rotary union (38, 38a) connects.

4. Torsionsschwingungsdämpfer 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

The position control valve arrangement (72, 72a) completely closes all pressure fluid displacement chambers (22, 22 ¹ , 24, 24 '; 22a, 22a ¹ , 24a, 24a ¹ ).

5. 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 Druckfluidverdrängungskammern (22, 22 ', 24, 24'; 22a, 22a ¹ , 24a, 24a ¹ ) connects to the supply area (68; 68a) of the rotary leadthrough (38; 38a).

6. torsional vibration damper according to one of claims 1 to 5, characterized in that in 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) a connection flow cross-section provided in the position control valve assembly (72; 72a) for supplying / removing pressurized fluid to / from the at least one pressure fluid displacement chamber (22,22 ', 24,24'; 22a);

22a ¹ , 24a, 24a ¹ ) increases progressively.

7. Torsional vibration damper according to one of claims 1 to 6, characterized in that the position control valve arrangement (72; 72a) with one of the primary side (12; 12a) or the secondary side (14; 14a) rotatable

Valve cylinder (74, 74a) and in the valve cylinder upon relative rotation of the primary side (12; 12a) with respect to the secondary side (14; 14a) movable valve spool (76, 76a) comprises.

8. Torsional vibration damper according to claim 7, characterized in that the valve cylinder (74a) or the valve slide (76) forms a rotatable part of the rotary feedthrough (38, 38a).

9. 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 spool (76) with the secondary side (12) rotatable rotary valve.

10. Torsional vibration damper according to claim 9, characterized in that in the rotary valve (76) at least part of the supply line region (68) and the discharge region (70) of the rotary feedthrough (38) is formed.

11. 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 of the

Rotary slide (76) receiving cylinder opening (114) open second feed opening (108, 108 ', 108 ", 108'") is formed, further in the secondary side (14) of the at least one pressure fluid displacement chamber (22, 22 ', 24, 24 ') away leading feed channel (110, 110', 110 ", 110 '") is formed, which is dependent 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.

12. Torsionsschwingungsdämpfer 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 ') limited by an end profile is, with relative rotation of the primary side (12) with respect to the secondary side (14) starting from the

Neutral relative rotational position produces a progressive increase in the coverage of the at least one first feed opening (106, 106 ') with the at least one second feed opening (108, 108 ", 108", 108' ").

13. 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 discharge region (70) is formed and in the Valve cylinder (74) at least one open to the rotary valve receiving cylinder opening (114) open second discharge opening (118, 118 ') is formed, further in the secondary side (14) of the at least one pressure fluid displacement chamber (22, 22', 24, 24 ') leading away discharge channel (120, 120 ', 120 ", 120"') is formed, in dependence 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 conjunction with the at least a first discharge opening (116, 116 ', 116 ", 116'") can be brought.

14. Torsional vibration damper according to claim 11 and claim 13, characterized in that in the rotary valve (76) is provided a substantially axially extending supply line section (98) which is radially open via the at least one first supply opening (106, 106 '), in that in the rotary valve (76) has a substantially axially extending

Ableitungsabschnitt (99) is provided, which on the at least one first discharge opening (116, 116 ', 116 ", 116'") is radially open, and that the supply line section (98) and the discharge section (99) are not in communication with each other.

15. Torsional vibration damper according to claim 2 and one of claims 11 to 14, characterized in that in the valve cylinder (76) in association with each Druckfluidverdrängungskammer (22, 22 ') of the first gas spring assembly (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.

16. Torsional vibration damper according to claim 2 and one of claims 13 to 15, characterized in that in the valve cylinder (74) in association with each Druckfluidverdrängungskammer (22, 22 ', 24, 24') of the first gas spring assembly and the second gas spring assembly (20) a second discharge opening (118, 118 ') is provided.

17. Torsionsschwingungsdämpfer according to claim 16, characterized in that in the valve cylinder (76) one of the number Pressure fluid displacement chambers (22, 22 ') of the first gas spring assembly (18) or the number of pressure fluid displacement chambers (24, 24') of the second gas spring assembly (20) corresponding number of second discharge openings (118, 118 ') is provided and that Relative rotational position of the primary side (12) with respect to the secondary side (14)

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 conjunction with the first discharge openings (116, 116') 116 ", 116" ') can be brought.

18. 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 spool (76a) in a cylinder opening (114a) of the valve cylinder (74a) in the direction of the axis of rotation (A ) is slidable and against rotation with respect to the valve cylinder (74 a) locked valve piston.

19. Torsional vibration damper according to claim 20, characterized in that on the primary side (12 a) a cam element

(130a) is provided, which cooperates with the valve piston (76a) for displacement thereof during relative rotation of the primary side (12a) with respect to the secondary side (14a).

20. A torsional vibration damper according to claim 19, characterized in that the valve piston (76a) is biased by a biasing member (150a) in a first axial direction and displaceable by the cam member (130a) in a second axial direction against the biasing action of the biasing member (150a) is.

21. Torsional vibration damper according to claim 20, characterized in that the biasing element (150 a) in a through the valve piston (76a) and the valve cylinder (74a) limited chamber (250a) is arranged and that in the chamber (250a) accumulated fluid via a drainage channel (244a) can be discharged.

22. Torsional vibration damper according to one of claims 18 to 21, characterized in that in the valve piston (76 a) at least part of the supply line region (68 a) and the discharge region (70 a) of the rotary feedthrough (38 a) is formed.

23. Torsional vibration damper according to claim 22, characterized in that in the valve piston (76a) at least one radially open first supply port (106a) is formed in that in the valve cylinder (74a) at least one second feed opening (108a, 108a ¹ ) is formed, which via a connecting channel (158a, 160a) in connection with the at least one pressure fluid displacement chamber (22a,

22a ¹ , 24a, 24a '), and in dependence 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 supply port (106a) with the at least one second supply port (180a, 108a ¹ ) is changeable.

24. Torsional vibration damper according to claim 23, characterized in that in the valve cylinder (74a) at least one first discharge opening (162a, 162a ¹ ) is provided, which via the connecting channel (158, 160) in conjunction with the at least one pressure fluid displacement chamber (22, 22a ', 24a, 24a ¹ ) is that in the

Valve cylinder (74a) at least one second discharge opening (164a, 164a ') is provided, which is in connection with a discharge section (170a) of the rotary feedthrough (38a), and in that in the valve piston (76a) at least one bypass channel (166a, 166a') is provided, which in dependence on the relative rotational position of the primary side (12a) with respect to

Secondary side (14 a) a connection between the at least one first discharge opening (162 a, 162 a ¹ ) and the at least one second discharge opening (164a, 164a ¹ ).

25. Torsional vibration damper according to claim 24, characterized in that upon relative rotation of the primary side (12a) with respect to the secondary side (14a) either a connection between the at least one first supply port (106a) and the at least one second supply port (108, 108a ¹ ) can be produced or about the

Bridging channel (166a, 166a ¹ ), a connection between the at least one first discharge opening (162a, 162a ¹ ) and the at least one second discharge opening (164a, 164a ¹ ) can be produced.

26. Torsional vibration damper according to claim 6 and 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 ¹ ) is formed with such end profile that when relative rotation of primary

(12a) with respect to the secondary side (14a) starting from a neutral

Relative rotational position, the extent of overlap of the at least one first

Feed opening (106 a) with the at least one second feed opening (108 a, 108 a ¹ ) increases progressively.

27. Torsional vibration damper according to claim 2 and one of claims 24 to 26, characterized in that the at least one Druckfluidverdrän- supply chamber (22a, 22a ') of the first gas spring assembly (18a) via a

Connecting channel (158a) in conjunction with at least a second

Feed port (108a ¹ ) and the at least one Druckfluid- displacement chamber (24a, 24a ¹ ) of the second gas spring assembly (20a) via a connecting channel (160a) in conjunction with at least one further second feed opening (108a), and in that

Relative rotational position of the primary side (12a) with respect to the secondary side (14a) by moving the valve piston (76a) at least a first Supply opening (106a) in overlap with the at least one second feed opening (108a) or the at least one further second feed opening (108a ¹ ) can be brought.

28. Torsional vibration damper according to claim 27, characterized in that the at least one Druckfluidverdrän- supply chamber (22a, 22a ') of the first gas spring assembly (18a) via the connecting 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 assembly (20a) via the connecting channel (160) in conjunction 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) are associated and the at least one further first discharge opening (162a, 162a ') at least one further second

Abführöffnung (164a ¹ ) and another connecting channel (166a ¹ ) are assigned.

29. 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 supply port (106a) in conjunction with the at least one second feed opening (108a) occurs and the at least one further first discharge opening (162a ¹ ) passes via the further bridging channel (166a ¹ ) in conjunction with the at least one further second discharge opening (164a ¹ ), and in that when the valve piston is displaced ( 76a) in a direction of the neutral relative rotational position of the primary side (12a) with respect to the secondary side (14a), the at least one first supply port (106a) in connection with the at least one further second supply port (108a ¹ ) occurs in a first shift direction opposite the second shift direction and the at least one first Abführöffnu ng (162a) via the bridging channel (166a) in Connection with the at least one second discharge opening (164a) occurs.

30. Torsional vibration damper according to claim 27, characterized in that when the at least one first feed opening (106a) is in communication with the at least one further second feed opening (108a ¹ ), the at least one second feed opening

(108a ¹ ) via a bypass channel (166a) in conjunction with a

Abführöffnung (164a), and if the at least one first

Feed opening (106a) in registration with the at least one second feed opening (108a), the at least one further second feed opening

(108a) via a further discharge opening (164a ¹ ) with a drainage channel

(222a) is in communication.

31. Torsional vibration damper according to one of the preceding claims, characterized by a in connection with the supply line (68) of

Rotary feedthrough (38) standing or bringable pressurized fluid source (50).

32. Torsional vibration damper according to claim 31, characterized in that the pressure fluid source (50) comprises a pressure fluid pump (46) with a pressure fluid pump drive (300).

33. Torsional vibration damper according to claim 32, characterized in that the pressure fluid pump (46) is associated with a pressure accumulator (312).

34. Torsional vibration damper according to claim 32 or 33, characterized in that the pressure fluid pump (46) is associated with a pressure limiting valve arrangement (314) for limiting the on an output side of the pressure fluid pump (46) existing pressure fluid pressure to a default value.

35. Torsional vibration damper 32 to 34, characterized in that the conveying capacity of the pressure fluid pump (46) is variable as a function of the pressure fluid pressure present on an outlet side of the pressure fluid pump (46).

36. 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.

37. The torsional vibration damper according to claim 32, wherein the pressure fluid pump drive comprises a vehicle drive unit.

38. Torsional vibration damper according to claim 35 or 36, characterized in that the pressure fluid pump drive (300) in

Depending on the pressure fluid pressure can be activated and deactivated and / or varied in its drive effect.

39. Torsional vibration damper according to claim 38, characterized in that the pressure fluid pump drive (300) has a

Electric drive motor (316) includes.

40. 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 ¹ , 24a, 24a ¹ ) is defined by a primary side displacement chamber assembly (206a) and a secondary side displacement chamber assembly (212a). is limited, wherein the primary-side displacement chamber assembly (206a) comprises two end walls (80a, 82a) and a peripheral wall (84a), and wherein the secondary-side

Displacement chamber assembly (212 a) or a subsequent thereto rotating part (74 a) of the rotary feedthrough (38 a) one of the end walls (80a, 82a), said end wall (82a) having an annular axial extension (208a), with a bearing (210a) radially supported on the axial extension (208a), over which the primary side either with respect to a non-rotating part (200a) 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 mounted.

41. Torsional vibration damper according to claim 40, characterized in that the bearing (210a) is a floating bearing.

42. Torsionsschwingungsdämpfer 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 Hirthverzahnnung, for torque-transmitting coupling with a following assembly.