DE102008041375A1 - Hydrodynamic coupling device, in particular torque converter - Google Patents

Abstract

A hydrodynamic coupling device, in particular torque converter, comprises a fluid-filled or fillable housing (110) with a pump wheel (112), a turbine wheel (118) arranged in a housing interior (116), which is connected to a drive member (130) for common rotation about one A torque transfer connection between the housing (110) and the output member (130) can be produced, wherein in the torque transmission between the lock-up clutch assembly (134) and the output member (130 ) and / or in the torque transmission path between the turbine wheel (118) and the output member (130) a Torsionsschwingungsdämpferbaugruppe (132) with a Torsionsschwingungsdämpferanordnung (10) is provided, wherein the Torsionsschwingungsdämpferanordnung (10) a primary side (16) and via a damper fluid arrangement with the Primary side (16) for rotation about an axis of rotation (A) and for relative rotation with respect to each other coupled secondary side (24), wherein the damper fluid assembly comprises a fluid pressure accumulator assembly and a fluid conveyor assembly through which upon relative rotation of the primary side relative to the secondary side of the accumulator pressure in the fluid pressure accumulator assembly is variable ,

Description

The The present invention relates to a hydrodynamic coupling device, such as B. a hydrodynamic torque converter, via which in a drive train of a vehicle torque between a drive shaft, for example a crankshaft of an internal combustion engine, and then in the torque flow following transmission, in general Automatic transmission or transmission with continuously variable transmission ratio, transmitted can be.

A Such hydrodynamic coupling device is generally with a housing with an impeller provided thereon and disposed in the housing Turbine wheel built. By fluid circulation between the impeller and the turbine wheel can transmit or amplify a torque, if in the fluid circulation path and a stator is effective. To go in Operating phases in which a torque conversion is not required is to avoid energy losses through the fluid circulation can, via a lock-up clutch assembly optionally a direct torque transmission connection between the housing and an output member, so for example a transmission input shaft, getting produced.

Around dampening occurring in such a system torsional vibrations or to suppress their formation as far as possible, it is known in the torque transmission path to provide to the output member a Torsionsschwingungsdämpferbaugruppe. This can be between the lock-up clutch arrangement and the output drive, basically but also act between the Tubinenrad and the output member. Also, arrangements are known in which the torsional vibration damper assembly two torsional vibration damper assemblies includes, which are connected in series. The turbine wheel is here to an area between the two torsional vibration damper assemblies coupled, so that in the torque transmission path between the Turbine and the output member one of Torsionsschwingungsdämpferanordnungen acts, and in the torque transmission path between the lockup clutch assembly and the output member both torsional vibration damper arrangements serially can.

The used in such Torsionsschwingungsdämpferbaugruppen torsional vibration damper are generally with helical compression springs as damper elements a damper element arrangement educated. These helical compression springs extend approximately in the circumferential direction or tangential thereto and can at torque load be compressed. Although by a comparatively compact Design is feasible, are the elasticity properties and thus the Vibration damping characteristics, which can be achieved with such constructions limited. In particular, it is practically impossible to operate or after constructive design of such a structure changes at the vibration damping behavior make.

It the object of the present invention is a hydrodynamic Coupling device, in particular torque converter to provide, which in the torque flow to an output member an improved vibration damping characteristic having.

According to the invention this Task solved by a hydrodynamic coupling device, in particular a torque converter, comprising a fluid filled or fillable casing with a pump wheel, a turbine wheel arranged in a housing interior, which with a driven member for common rotation around a Rotary axis is coupled or coupled, and a lock-up clutch arrangement, via which optionally a torque transmission connection between the housing and the output member is producible, wherein in the torque transmission path between the lockup clutch assembly and the output member and / or in the torque transmission path between the Turbine and the output member, a torsional vibration damper assembly with a torsional vibration damper assembly is provided, wherein the Torsionsschwingungsdämpferanordnung a primary side and one over a damper fluid assembly with the primary side for rotation about a rotation axis and for relative rotation in terms of comprises mutually coupled secondary side, wherein the damper fluid assembly a fluid pressure accumulator assembly and a fluid delivery assembly comprising, by relative rotation of the primary side relative to the secondary side the storage pressure in the fluid pressure storage arrangement changeable is.

at the structure of the invention So it is in the torque transmission path incorporated in the hydrodynamic coupling means a kind of a gas spring Torsionsschwingungsdämpferanordnung. This allows the extension of the vibration damping spectrum and, if necessary, also the variability of the vibration damping characteristic while the operation, which, as stated above, in conventionally constructed Torsionsschwingungsdämpferanordnungen with damper elements with fixed preset spring characteristic is basically not possible.

there it can be provided that the damper fluid arrangement a torque transmitting between the primary side and the secondary side first damper fluid with lower compressibility in a first damper fluid chamber arrangement includes as well as a pressure increase of the first damper fluid in the first damper fluid chamber assembly loaded second damper fluid with higher compressibility in a second damper fluid chamber arrangement wherein the second damper fluid chamber arrangement at least one chamber unit and in association with this one the first damper fluid separating from the second damper fluid and at pressure change in the chamber unit displaceable separating element, wherein the first damper fluid chamber assembly at least one pressure chamber with relative rotation of the primary side with respect to the secondary side variable Volume and in association with this comprises a connection volume for receiving by reducing the volume of the at least one pressure chamber out of this repressed first damper fluid for acting on the separating element of the at least one chamber unit. In this arrangement, therefore, essentially forms the first damper fluid chamber arrangement with its at least one pressure chamber essentially the fluid conveying arrangement, while the second damper fluid chamber assembly with her at least one chamber unit and the recorded therein second damper fluid with higher compressibility essentially provides the fluid pressure accumulator assembly.

at the structure of the invention a hydrodynamic coupling device can, for example be provided that the primary side of the torsional vibration damper with the lock-up clutch arrangement is coupled and the secondary side the torsional vibration damper assembly coupled to the output member or can be coupled.

Around at the vibration damping To be able to provide a stepped action characteristic will continue suggested that the primary side the torsional vibration damper assembly via a further torsional vibration damper arrangement with the lock-up clutch arrangement coupled, wherein the further Torsionsschwingungsdämpferanordnung a damper element arrangement comprising at least one elastically deformable spring element.

Also then, if the secondary side the torsional vibration damper assembly via another torsional vibration damper coupled to the output member or can be coupled, the other torsional vibration damper a damper element arrangement comprising at least one elastically deformable spring element, can the two torsional vibration damper assemblies be coordinated with each other, that by a stepped action characteristic These are effective in different torque ranges.

The secondary side the torsional vibration damper assembly can over the further torsional vibration damper assembly and the turbine wheel coupled to the output member or coupled be so that the torque flow in series across the two torsional vibration damper assemblies and then the turbine wheel is directed to the output member.

at an alternative variant may be provided that the turbine wheel with the secondary side the torsional vibration damper assembly is coupled. In this case, so the turbine is at a Range of torque transmission path coupled between the two torsional vibration damper assemblies lies.

at A further alternative variant can be provided that the turbine wheel with the primary side the torsional vibration damper assembly coupled, which leads that the turbine wheel massively the primary the torsional vibration damper assembly is to be assigned.

Around in the hydrodynamic invention Coupling device in the area constructed as a gas spring Torsionsschwingungsdämpferanordnung torsional vibration damper an influence on the damping characteristic even while to be able to realize the operation suggested that for at least one pressure chamber of the Torsionsschwingungsdämpferanordnung a pressurized fluid supply channel assembly for supplying pressurized fluid first damper fluid is provided for this.

Further can influence the state of engagement the Oberbrückungskupplungsanordnung provided be that the output member from a drive shaft is from and that in the output shaft, a first flow channel for controlling the lockup clutch arrangement is provided.

at a structurally particularly easy to implement design variant It is further proposed that the pressure fluid supply channel arrangement the first flow channel included in the output shaft.

In order to decouple the lockup clutch assembly on the one hand and the Torsionsschwingungsdämpferanordnung on the other hand functionally can, in an alternative Ausgestaltungsvari Ante be provided, that the pressure fluid supply channel arrangement comprises a second flow channel in the output shaft for supplying first damper fluid to at least one pressure chamber. In this case, for example, the second flow channel may be arranged concentrically surrounding the first flow channel substantially.

Around also in that area of the housing interior, in which the Turbine is arranged to realize a fluid exchange can, is further suggested that in the output shaft, a third flow channel for the supply and / or removal of fluid to or from the housing interior is provided.

The Supply the at least one pressure chamber with the first damper fluid may alternatively or additionally also be realized in that a hollow support shaft, the drive shaft is provided surrounding, and that the pressure fluid supply channel arrangement one between the hollow support shaft and the output shaft formed fourth flow channel for supplying the first damper fluid comprises at least one pressure chamber. In this embodiment can the effective as the output member output shaft then comparatively be simple, because, for example, only a single opening as first flow channel for controlling the lockup clutch arrangement must be provided.

at a further alternative embodiment variant is proposed that a hollow support shaft is provided and that the pressure fluid supply channel arrangement one formed in the hollow support shaft fifth flow channel for supplying first damper fluid comprises at least one pressure chamber. To do so for both Relative directions to provide a fluidic damping effect can, It is further proposed that the pressure fluid supply channel arrangement one in the hollow support shaft formed sixth flow channel to Supply of first damper fluid to at least one pressure chamber, wherein further provided that can be the sixth flow channel the fifth flow channel is arranged substantially concentrically surrounding.

at a further alternative embodiment, which in particular with regard to the fluid supply of the hydrodynamic coupling device in itself no substantive changes required, but nevertheless the supply of the torsional vibration damper assembly with first pressurized fluid, It is proposed that on one of a drive unit facing to be positioned side of the housing a rotary feedthrough with one with the housing connected rotating rotary feedthrough area is provided wherein the pressurized fluid supply channel assembly comprises a seventh flow channel in the rotating rotary feedthrough area for supplying first damper fluid comprises at least one pressure chamber.

According to one In another aspect, the present invention relates to a drive system for a vehicle, comprising a drive unit and a torque between a drive shaft of the drive unit and a hydrodynamic coupling device, in particular hydrodynamic torque converter, transmitting torsional vibration damper, wherein the torsional vibration damper assembly a primary page and one over a damper fluid assembly with the primary side for rotation about a rotation axis and for relative rotation with respect to each other coupled secondary side includes, wherein the damper fluid assembly a fluid pressure accumulator assembly and a fluid delivery assembly comprising, by relative rotation of the primary side relative to the secondary side the storage pressure in the fluid pressure storage arrangement changeable is.

there it can be provided that the damper fluid arrangement a torque transmitting between the primary side and the secondary side first damper fluid with lower compressibility in a first damper fluid chamber arrangement includes as well as a pressure increase of the first damper fluid in the first damper fluid chamber assembly loaded second damper fluid with higher compressibility in a second damper fluid chamber arrangement wherein the second damper fluid chamber arrangement at least one chamber unit and in association with this one the first damper fluid separating from the second damper fluid and at pressure change in the chamber unit displaceable separating element, wherein the first damper fluid chamber assembly at least one pressure chamber with relative rotation of the primary side with respect to the secondary side variable Volume and in association with this comprises a connection volume for receiving by reducing the volume of the at least one pressure chamber out of this repressed first damper fluid for acting on the separating element of the at least one chamber unit.

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

1 a drive system with a gas spring torsional vibration damper assembly and a hydrodynamic torque converter;

2 a cross section through the in 1 recognizable gas spring torsional vibration damper assembly;

3 a hydrodynamic torque converter with an integrated gas spring Torsionsschwingungsdämpferanordnung;

4 a cross-sectional view of in 3 recognizable gas spring torsional vibration damper assembly;

5 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

6 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

7 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

8th one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

9 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

10 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

11 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

12 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

13 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment; and

14 one of the 3 corresponding representation, which basically shows an alternative constructed hydrodynamic torque converter of an alternative embodiment;

15 a further partial longitudinal sectional view of a hydrodynamic torque converter of an alternative embodiment.

The 1 and 2 show a Torsionsschwingungsdämpferanordnung 10 that serves in a propulsion system 11 a torque between a rotating about a rotation axis A drive shaft of a vehicle 12 , So for example, a crankshaft, and a hydrodynamic coupling device 14 represented by a hydrodynamic torque converter. With reference to the following explanations, it should be noted that in the context of the present invention, a tensile state is mentioned when a torque from the drive shaft 12 on the friction clutch 14 is to be transferred, while of a thrust state is then mentioned when the torque from the friction clutch 14 towards the drive shaft 12 is transferred, so for example, a vehicle is in an engine braking state.

The torsional vibration damper assembly 10 includes a general with 16 designated primary side. This is about a Flexplattenanordnung 18 with the drive shaft 12 connected. This is particularly advantageous because it is an elasticity is integrated into the drive train, the conditions Taumelbewe or compensate for axial offsets. Besides, like this in 1 clearly visible, the flexplate assembly 18 be designed such that radially inside the connection to the drive shaft 12 takes place and radially outside the connection to the primary side 16 takes place, so that in the radially inner region of the Torsionsschwingungsdämpferanordnung 10 no action must be taken to there the connection to the drive shaft 12 to enable.

The primary side 16 comprises a substantially ring-like designed first chamber housing 20 , In this coaxial manner is also a ring-like ausgestaltetes second chamber housing 22 a secondary side 24 the torsional vibration damper assembly 10 used. As in 2 clearly visible, is between the two chamber housings 20 . 22 a ring-like gap 26 educated. At the first chamber housing 20 are at an angular distance of 180 °, two radially inward circumferential boundary projections 28 ' and 28 '' intended. At the second chamber housing 22 are in a corresponding manner also at an angular distance of 180 ° two radially outwardly extending circumferential boundary projections 30 ' and 30 '' intended. The on the other chamber housing to be extended perimeter boundary projections 28 ' . 28 '' . 30 ' and 30 '' limit between each first pressure chambers 32 ' and 32 '' or second pressure chambers 34 ' and 34 '' a general with 36 designated first damper fluid chamber assembly. Through to the jewei liger peripheral limitation projections 28 ' . 28 '' . 30 ' and 30 '' provided sealing elements are circumferentially alternately successive pressure chambers 32 ' . 34 '' . 32 '' . 34 ' essentially fluid-tightly separated from each other. The pressure chambers 32 ' . 32 '' . 34 ' and 34 '' are also in the axial direction through the first chamber housing 20 and a permanently attached end plate 42 in connection with the second chamber housing 22 and sealed thereto sealing elements fluid-tight. Due to the relative rotation of the primary side 16 with respect to the secondary side 24 the torsional vibration damper assembly 10 about the axis of rotation A are the volumes of the pressure chambers 32 ' . 32 '' . 34 ' and 34 '' changeable. Turns, for example, in the representation of 2 the inner chamber housing 22 with respect to the outer chamber housing 20 in the counterclockwise direction, so does the volume of the second pressure chambers 34 ' and 34 '' to, while the volume of the first pressure chambers 32 ' and 32 '' decreases.

To enable this relative rotational movement in a defined manner is, as in 1 recognizable, a radial bearing 38 provided, between the inner periphery of the second chamber housing 22 and a radially inward cross-approach 40 of the first chamber housing 20 is arranged. This camp 38 can be designed as Wälzkörperlager or as a plain bearing. Next, this camp can also serve the Axialabstützung.

Radially outside is the first chamber housing 20 surrounded by a chamber unit assembly 44 , This chamber unit assembly, for example, made in one piece 44 comprises a plurality of circumferentially about the rotational axis A successive, pot-like chamber units 46 , Radially outside is on the chamber unit assembly 44 as a separate component with the various chamber units 46 in the radial outer region, for example, by welding firmly connected starter ring gear 45 intended. The chamber units 46 are thus arranged with respect to the axis of rotation A in radially outwardly extending star-like configuration and are open radially inward.

In each of these chamber units 46 is a separating piston 48 used, the z. B. by an O-ring-like sealing element with respect to the respective chamber unit 46 is sealed fluid-tight and is displaced in this substantially in the radial direction. Radially inside are the chamber units 46 to an annulus 50 open. This is divided in the circumferential direction by a plurality of partitions 52 . 54 . 56 . 58 , Through these partitions 52 . 54 . 56 . 58 becomes the annulus 50 divided into four connecting chambers 60 . 62 . 64 . 66 , Each of these connecting chambers 60 . 62 . 64 . 66 is one of the pressure chambers 32 ' . 34 . 32 '' respectively. 34 ' assigned.

It can be seen that in the chamber housing 20 radially outside each openings 68 . 70 . 72 . 74 available. It represents the opening 68 a connection between the first pressure chamber 32 ' and the connecting chamber arranged radially outside thereof 60 ago. The opening 70 provides a connection between the second pressure chamber 34 '' and the connecting chamber arranged radially outside thereof 62 ago. The opening 72 provides a connection between the first pressure chamber 32 '' and the connecting chamber arranged radially outside thereof 64 ago, and the opening 74 provides a connection between the second pressure chamber 34 ' and the connecting chamber arranged radially outside thereof 66 ago.

About these connection chambers 60 . 62 . 64 . 66 are the different pressure chambers 32 ' . 32 '' respectively. 34 ' . 34 '' in conjunction with these respectively associated with the chamber units 46 a general with 76 designated second damper fluid chamber assembly. One recognizes that by the positioning of the partitions 58 and 52 the first pressure chamber 32 ' over the connection chamber 60 three circumferentially immediately successive chamber units 46 assigned. The first pressure chamber 32 '' are about the connection chamber 64 four of the chamber units 46 assigned. The second pressure chamber 34 ' are about the connection chamber 66 two chamber units 46 assigned, and the second pressure chamber 34 '' are about the connection chamber 62 also two of the chamber units 46 assigned.

The radially inward toward the annulus 50 or the connection chambers 60 . 62 . 64 . 66 through the separating pistons 48 fluid-tight sealed volumes 78 the chamber units 46 are with a compressible damper fluid, so for example a gas such. As air filled. The pressure chambers 32 ' . 32 '' . 34 ' and 34 '' are, as well as the connecting chambers 60 . 62 . 64 . 66 , with a substantially incompressible damper fluid, so a liquid such. As oil or the like filled.

To the pressure chambers 32 ' . 32 '' . 34 ' and 34 '' or the connection chambers 60 . 62 . 64 . 66 to fill with the incompressible damper fluid is the secondary side 24 a general with 80 assigned rotary feedthrough assigned. This includes an axial extension 82 of the chamber housing 22 surrounding and by two storage units 84 . 86 with respect to this rotary rotary feedthrough ring 88 , In the chamber housing 22 are through holes channels 90 respectively. 92 formed, of which, for example, the channel 90 to the second pressure chambers 34 ' respectively. 34 '' leads, while the channel 92 to the first pressure chambers 32 ' . 32 '' leads. To keep flow losses as low as possible, it is of course possible to lead to each of the pressure chambers own channel. In association with each of these channels is in the rotary feedthrough ring 80 then a stationary in rotary operation channel 94 respectively. 96 provided over which channels 94 . 96 the channels 90 . 92 in connection with a source of the incompressible damper fluid or a reservoir for it can be brought. In this way, the fluid pressure of the incompressible damper fluid in the pressure chambers 32 ' . 32 '' . 34 ' and 34 '' be adjusted according to the required damping characteristics.

One recognizes in 1 continue that between or on both sides of the channels 94 . 96 in the rotary union ring 88 sealing elements 98 . 100 respectively. 102 are present, which are essentially pressure seals. Axially out of stock 84 and 86 are still volumetric flow seals 104 . 106 arranged. Between the seals 100 and 106 on the one hand and 102 . 104 On the other hand, volumes formed may be via respective leakage channels 108 . 110 be emptied, so that possibly still passed through the pressure seals incompressible damper fluid can also be returned to the reservoir.

The Indian 1 shown hydrodynamic torque converter 14 may be of conventional construction with a housing 110 to which a pump wheel 112 with his impeller blades 114 is realized. One in a housing interior 116 arranged turbine wheel 118 makes with its turbine wheel blades 120 and accordingly also the impeller 112 or the impeller blades 114 a fluid circulation that under the action of a stator 122 or the stator blades 124 can also be used for torque amplification. The stator 122 is via a hollow support shaft 126 on a transmission indicated only schematically 128 or a transmission housing worn. The hollow support shaft 126 surrounds as a driven member or output shaft 130 effective transmission input shaft, with which the turbine wheel 118 via a torsional vibration damper assembly 138 is coupled for common rotation. Also, via a lockup clutch arrangement 134 the housing 110 over the torsional vibration damper assembly 138 with the transmission input shaft 130 be coupled.

A torsional vibration damper assembly 132 can, as shown here, be formed in one stage, so essentially comprise only a set of example designed as helical compression springs damper springs, but may also be formed multi-stage, wherein a first stage, the Torsionsschwingungsdämpferanordnung 138 then also between the lock-up clutch assembly 134 and the Tubinenrad 118 can act, and a second stage, a torsional vibration damper assembly 10 includes, as in the 1 also recognizable.

Hereinafter, the function of the above with respect to the 1 and 2 in terms of their structural design described Torsinnsschwingungsdämpferanordnung 10 explained.

In the tensile state, ie a state in which a torque from the primary side 12 on the secondary side 24 is transmitted, so at first detained secondary side 24 and in the 2 also held chamber housing 22 the primary side 12 , in the 2 So the chamber housing 20 , turned counterclockwise. This means that in the second pressure chambers 34 ' and 34 '' contained essentially non-compressible damper fluid from these pressure chambers through the openings 74 respectively. 70 through into the associated connection chambers 66 . 62 is displaced. Through the in the connecting chambers 66 . 62 increasing pressure are the separating pistons 48 the connecting chambers 60 . 62 associated chamber units 46 the second damper fluid chamber assembly 76 loaded so that they under compression and corresponding pressure increase in the volumes 78 existing compressible damper fluids are moved radially outward. With increasing compression, the counterforce increases, so that here a spring characteristic is achieved. If the load in the other direction occurs, the first pressure chambers become 32 ' and 32 '' reduced in volume so that the incompressible damper fluid contained therein through the openings 68 respectively. 72 in the associated connection chambers 60 . 64 is displaced and according to the radially outside of these connecting chambers 60 . 64 arranged chamber units 46 be charged. The separating pistons 48 of these chamber units 46 will move under compression of the compressible damper fluid radially outward and now provide in the thrust direction for the desired damping characteristic.

As in the in the 2 shown embodiment, the separating piston 48 in the neutral relative rotational position between the primary side 16 and secondary side 24 are in their maximum radially inwardly displaced positioning, it is necessary to those pressure chambers 32 ' . 32 '' . 34 ' . 34 '' , whose volume during relative rotation between the primary side 16 and secondary side 24 increases in this state with a reservoir for unpressurized first damper fluid to connect in this relative rotation and also in the reverse rotation in the neutral relative rotational position, a corresponding change in volume of this pressure chambers. However, are the separating pistons 48 in the state of neutral relative rotational position, for example, radially in the center of each receiving chamber units 46 , They can shift when decompressed, so volume increase of a respective associated pressure chamber, radially inward, under the biasing effect of in a respective chamber unit 46 existing second damper fluid so as to supply the required for an increase in volume first damper fluid from a connecting chamber into a respective pressure chamber. In such a configuration, such a Torsionsschwingungsdämpferanordnung 10 operate as a self-sufficient, closed to the outside, so not supplied with first damping fluid system. The connection with a pressure fluid source via the rotary union 88 However, it is therefore advantageous because in this way by appropriate variation or influencing the fluid pressure in respective pressure chambers 32 ' . 34 ' . 32 '' . 34 '' an influence on the vibration damping behavior can be taken.

From the foregoing description, it can be seen that by displacing the incompressible damper fluid in the first damper fluid chamber assembly 36 and the corresponding admission of the separating piston 48 in the chamber units 46 the second damper fluid chamber assembly 76 Damping functionality can be obtained both in the thrust direction and in the tension direction. The damping characteristic will differ in the direction of pull and in the direction of thrust since there are four chamber units in the pulling direction 46 are effective, while this in thrust a total of seven chamber units 46 are. It can therefore be seen that solely by the positioning of the partitions 52 . 54 . 56 . 58 a choice can be made as to how many of the chamber units 46 the second damper fluid chamber assembly 76 in overrun mode or in train operation are effective. Furthermore, an influence on the damping characteristic can be taken by the fact that the different first and possibly also the different second pressure chambers 32 ' . 32 '' respectively. 34 ' . 34 '' also different numbers of chamber units 46 are assigned, as in the first pressure chambers 32 ' . 32 '' is recognizable. In order to avoid the occurrence of imbalances during rotation, it is advantageous to obtain the most uniform possible distribution about the axis of rotation A. Of course, the size or the number of chamber units 46 be tailored to the given requirements. In the Darge presented example with a total 11 chamber units 46 is due to the existing separation of the individual chamber units 46 forcibly provided an uneven action characteristic in the pulling direction and in the thrust direction. With even number of chamber units 46 In the direction of pull and in the direction of thrust, it is possible for a number of them to be effective, and thus a uniform action characteristic can be provided in both loading directions.

In this case with reference to the 1 and 2 Torsional vibration damper assembly described in terms of their construction and their functionality 10 form the primary side 16 with its chamber housing 20 or the peripheral limiting projections provided thereon 28 '' and the secondary side 24 with its chamber housing 22 or the peripheral limiting projections provided thereon 30 ' . 30 '' and the thus defined pressure chambers 32 ' . 32 '' . 34 ' . 34 '' a general with 35 designated fluid conveying arrangement, which displaces fluid upon relative rotation between the primary side and the secondary side, namely the incompressible damper fluid contained therein, and thus promotes. The here primary side, so on the chamber housing 20 provided chamber unit assembly 44 forms with their chamber units 46 and the compressible damper fluid contained therein, substantially a fluid pressure accumulator assembly 47 in which the accumulator pressure is variable, depending on the fluid displacement or fluid delivery of the fluid conveyor assembly 35 ,

The following will be with reference to the 3 to 14 various embodiments of hydrodynamic coupling devices described in which a Torsionsschwingungsdämpferbaugruppe comprises at least one Torsionsschwingungsdämpferanordnung, as described in principle above with reference to the 1 and 2 has been described. The hydrodynamic coupling devices described below, all designed as hydrodynamic torque converters, can be used in a drive system between a drive unit, for example an internal combustion engine, and the following area of a drive train, in particular an automatic transmission, for torque transmission and also for torsional vibration damping.

The 3 shows a hydrodynamic torque converter 14 of basically conventional construction with an impeller 112 , a turbine wheel 118 and a stator 122 , Further, a lockup clutch arrangement 134 provided, which is constructed in the manner of a multi-plate clutch and a clutch piston 136 , which the housing interior 116 separates into two spatial areas, is engageable. In the torque transmission path between the lockup clutch assembly 134 and the output shaft 130 lies a torsional vibration damper assembly 132 , which is a torsional vibration damper assembly 10 comprises, as described above with reference to the 2 was also explained in detail. Some of the design of the 2 existing differences are discussed below with reference to the 4 still described.

First, it should be noted that the Torsionsschwingungsdämpferbaugruppe 132 in addition to the Torsionsschwingungsdämpferanordnung 10 , which is constructed in the manner of a gas spring damper, another torsional vibration damper assembly 138 having. This is to the torsional vibration damper assembly 10 connected in series and lies in the torque transmission path between the primary side 16 the same and the lock-up clutch arrangement 134 , The further torsional vibration damper arrangement 138 comprises a friction element carrier as input area or primary side 140 , which the output-side friction elements or lamellae of the lock-up clutch assembly 134 carries and with trained as helical compression springs damper springs 142 the further torsional vibration damper assembly 138 cooperates for torque transmission. At the primary side 16 or the chamber housing 20 it is a cover disk element 144 for example, by welding, screwing or otherwise defined, so that between the chamber housing 20 and this cover disk element 144 an area is formed in which the damper springs 142 are included. Both on the chamber housing 20 as well as on the cover disk element 144 are, as well as the Reibelemententräger 140 , Circumferential support areas for the damper springs 142 provided so that they can be compressed in torque introduction in the circumferential direction and thus a relative rotation between the Reibelemententräger 140 , So the primary side of the further torsional vibration damper assembly 138 , and the cover disk element 144 or the chamber housing 20 , So allow the secondary side of the further torsional vibration damper assembly. It should be noted here that this further torsional vibration damper assembly can be constructed in principle, as a conventional, designed as a sliding cup Torsionsschwingungsdämpfer two-mass flywheel. The embodiment in the manner of a clutch disc torsion damper or a sliding shoe torsion damper is possible.

In the torque flow on the further torsional vibration damper assembly 138 following torsional vibration damper assembly 10 is the secondary side 24 , So their chamber housing 22 , now for example by a toothed area 146 with the output shaft 130 connected for common rotation. Furthermore, to the primary side 16 So, for example, the end plate 42 , the turbine wheel 118 or a turbine shell of the same connected, for example by welding, screwing or otherwise. This means that the Torsionsschwingungsdämpferanordnung 10 in the torque flow also between the turbine wheel 118 and the output shaft 130 is, therefore, so the turbine wheel 118 in the torque flow between the further torsional vibration damper assembly 138 and the torsional vibration damper assembly 10 to the torsional vibration damper assembly 132 is coupled. The primary side 16 the torsional vibration damper assembly 10 and the turbine wheel 118 thus essentially form the primary-side mass of the torsional vibration damper assembly 10 or the secondary-side mass of the further torsional vibration damper arrangement 138 while the secondary side 24 the torsional vibration damper assembly 10 together with the output shaft 130 essentially the secondary side mass of the Torsionsschwingungsdämpferanordnung 10 forms. The housing arrangement 110 forms with all non-rotatable components substantially the primary-side mass of the further torsional vibration damper assembly 138 when the lock-up clutch assembly 134 is in the engaged state.

In 4 can be seen in cross section the basic structure of the torsional vibration damper assembly 10 as they are in 3 is used. In essential areas, this corresponds, as already stated above, in 2 Described. It can be seen, however, that the annulus 50 is not interrupted in the circumferential direction and thus all chamber units 46 the two example Zugseitig effective pressure chambers 32 ' . 32 '' assigned. Only these have openings 68 respectively. 72 to which a connection volume between the pressure chambers 32 ' . 32 '' and the chamber units 46 producing annulus 50 on. This means that under tensile load and corresponding relative rotation between the primary side and the secondary side, the volume of the two pressure chambers is reduced 32 ' . 32 '' and it will thereby by appropriate pressure increase in the annulus 50 all chamber units 46 loaded on increased pressure.

The two push-side pressure chambers 34 ' . 34 '' have respective openings 150 respectively. 152 on which, for example, through the end wall 42 through to the interior of the housing 116 are open.

Will the torsional vibration damper assembly 10 loaded on thrust, so a torque passed from the drive train towards the drive unit, so reduces the volume of the pressure chambers 34 ' . 34 '' , In this case, first damper fluid is displaced out of these into the housing interior which then provides a receiving volume 116 , Since this compared to the torque at load occurring pressures will have a comparatively low fluid pressure is the outflowing fluid from the pressure chambers 34 ' . 34 '' no substantial resistance opposite, so that the Torsionsschwingungsdämpferanordnung 10 Here is essentially effective only in the tensile direction vibration damping. Because of the openings 150 . 152 is a permanent connection between the pressure chambers 34 ' . 34 '' and the housing interior 116 provided, so of course, these pressure chambers 34 . 34 '' be filled with the same fluid, as well as the housing interior 116 , Also, as explained below, in the pressure chambers 32 ' . 32 '' In principle, the first damper fluid to be introduced and pressurized may be of the same consistency, but has its own flow path or flow circuit. The advantage is that possibly occurring leaks then in the area of the housing interior 116 and can be removed from there with the normal fluid circulation.

To the two pressure chambers 32 ' . 32 '' To be filled with pressurized first damper fluid or to be able to supply first damper fluid is in the secondary side 24 So the chamber housing 22 , for example in association with each of the pressure chambers 32 ' . 32 '' a radially outwardly leading channel 154 intended.

In the output shaft 130 a central bore is provided, which in the area in which also the chamber housing 22 is located, is graded, so expanded. In the output shaft 130 is a tubular insert 156 used, which is formed in the bore or opening in a central first flow channel 158 and a second flow channel surrounding it substantially coaxially 160 divides. The insert part 156 can with the output shaft 130 For example, by friction welding or the like to produce a tight separation of the two flow channels 158 . 160 be connected. About the first flow channel 158 can fluid in a room area 162 be directed, so that by increasing the pressure in this room area 162 the clutch piston 136 is applied and the Oberbrückungskupplungsanordnung 134 can be indented. The second flow channel 160 is over one or more openings 164 radially outwardly open, specifically to the inner periphery of the chamber housing 22 where the channels 154 open into a circumferential groove. Thus, regardless of the relative rotational positioning of the output shaft 130 with respect to the chamber housing 22 a fluid exchange connection of the second flow channel 160 with the channels 154 be ensured. The channels 154 form with the second flow channel 160 in this embodiment, essentially a pressurized fluid supply channel arrangement 168 via which first damper fluid under high pressure from a source, for example in a transmission, of pressurized first damper fluid into the pressure chambers 32 ' . 32 '' can be fed. Due to the design of the second flow path in the output shaft 130 For example, the rotary feedthrough provided for this within a transmission can equally be used to apply first damper fluid into the pressure chambers 32 ' . 32 '' initiate.

To between the chamber housing 22 and the output shaft 130 to provide a fluid-tight transition, both sides of the openings 164 Sealing elements act, such as O-rings or other ring-like sealing elements. To continue doing a uniform sealing gap between the chamber housing 22 and the output shaft 130 ensure is the output shaft 130 via a radial bearing 170 , For example, a roller bearing or a sliding bearing, with respect to the housing 110 or a housing hub provided thereon 172 radially mounted. As a general rule, the torsional vibration damper assembly 10 in defined radial positioning with respect to the housing 110 is maintained in this way ensures that over the entire circumference, the two sealing elements experience a uniform load and thus can also fulfill a uniform sealing function.

In the axial direction, the Torsionsschwingungsdämpferanordnung between the housing 110 and the stator 122 held defined by respective thrust bearings. The stator 122 again, with respect to the housing 110 also axially mounted on its other axial side. The supply and removal of fluid in a space area 174 of the housing interior 116 can, similar to a conventional three-wire converter by a between the output shaft 130 and the hollow support shaft 126 formed flow path and one between the hollow support shaft 126 and a pump hub 176 made flow path.

It can be further seen that in the area of the stator 122 an example induction-like working sensor 178 integrated, which is the rotation of the torsional vibration damper assembly 10 detected. In this way it becomes possible to obtain information about the state of rotation, in particular the primary side 16 the torsional vibration damper assembly 10 , to get. In the transmission, not shown, a corresponding arrangement may be provided to the rotational position of the output shaft 130 to capture, so that the relative rotational position between the primary side 16 and the secondary side 24 can be determined and thus the need for a possible pressure increase in the pressure chambers 32 ' . 32 '' can be determined.

It should be noted that in this embodiment, for example, by two radial bearings 180 . 182 the primary side 16 with respect to the secondary side 24 the torsional vibration damper assembly 10 can be mounted radially.

The design of the torsional vibration damper assembly 10 and the further torsional vibration damper assembly 138 may be such that in principle a stepped operation occurs, so for example, the Torsionsschwingungsdämpferanordnung 10 is biased and at smaller torques, as they are to be expected in the thrust state, only the further torsional vibration damper assembly 138 is effective. If major torque fluctuations or spontaneous torque increases occur, as is to be expected in the tension state, the torsional vibration damper arrangement also becomes 10 effective, wherein the effective characteristic then by the variation of the pressure of the first damper fluid in the two pressure chambers 32 ' . 32 '' can be adjusted.

The 5 shows an alternative embodiment of a hydrodynamic torque converter 14 , wherein here only a schematic diagram is shown, in comparison to the embodiment of the 3 existing differences in principle.

One recognizes at the in 5 illustrated embodiment variant that the Torsionsschwingungsdämpferbaugruppe 132 again the two torsional vibration damper assemblies 10 and 138 includes, which act serially to each other. However, it is the primary page here 16 the torsional vibration damper assembly 10 directly to the lockup clutch assembly 134 coupled. The secondary side 24 the torsional vibration damper assembly 10 is about the further torsional vibration damper assembly 138 to the output shaft 130 coupled. That is, the secondary side 24 is here about the two bearings 170 . 170 ' radially with respect to the output shaft 130 stored, but not fundamentally rotatably coupled with this. The turbine wheel 118 is on the primary side 16 the torsional vibration damper assembly 10 coupled so that with disengaged lockup clutch assembly 134 both serially effective torsional vibration damper assemblies 10 . 138 between the turbine wheel 118 and the output shaft 130 Act.

Basically, the secondary side could 24 Here also by toothing rotatably to the output shaft 130 be coupled, so that on the further torsional vibration damper assembly 138 could be waived.

The structure of the further torsional vibration damper assembly 138 may again be as described above. The secondary side of the same can by gearing in rotary coupling engagement with the output shaft 130 stand. The mounting of the torsional vibration damper assembly 10 in particular with respect to the output shaft 30 For example, could be done by the secondary side 24 or even the primary side 16 the same with respect to the hollow support shaft 126 is supported radially, so that by the defined position assignment of the hollow support shaft 126 to the output shaft 130 also a defined relative positioning of the secondary side 24 with respect to this output shaft 130 would be ensured. In this case, for example, the further torsional vibration damper arrangement 138 also on the engine side axial side of the torsional vibration damper assembly 10 lie.

In this embodiment variant, the further Torsionsschwingungsdämpferanordnung 138 Basically be designed so that it is effective even in the range comparatively small torque to be transmitted or torque fluctuations, which still under the biasing pressure or biasing torque of the torsional vibration damper assembly 10 or the friction occurring there is also there. Only then, when the torques to be transmitted or occurring in the drive train torque fluctuations this biasing torque and the existing friction torque exceeds, is also the Torsionsschwingungsdämpferanordnung 10 effectively, if necessary, then in series with the further torsional vibration damper arrangement which is also effective in such higher torque ranges 138 , In principle, however, this could also be designed so that when the torques reach this higher range, they have already reached their maximum relative rotation between the input and the output region and are no longer effective in damping vibrations.

Another variant is in 6 shown. Again, the two Torsionsschwingungsdämpferanordnungen 10 . 138 connected in series with each other, wherein in the torque flow of the lock-up clutch assembly 134 to the output shaft 30 first, the torsional vibration damper assembly 10 lies and their secondary side 24 then to the further torsional vibration damper assembly 138 is coupled, namely their primary side. The secondary side of the further torsional vibration damper assembly 138 is to the turbine wheel 118 coupled, which in turn rotatably connected to the output shaft 130 For example, by gearing Gekop gelt is. To increase the secondary side mass of the further torsional vibration damper assembly 138 which essentially only the output shaft 130 and the turbine wheel 118 around can, on this turbine wheel 118 an additional flywheel 184 be provided.

In this embodiment variant, the secondary side could 24 the torsional vibration damper assembly 10 omitting the further torsional vibration damper arrangement 138 directly to the turbine wheel 118 and via this to the output shaft 130 be coupled.

It can be seen that the Torsionsschwingungsdämpferanordnung 10 here axially between the housing 110 and the turbine wheel 118 is supported by respective thrust bearing assemblies. The turbine wheel 118 itself is in turn axially on the stator 126 mounted, which at its other axial side with respect to the housing 110 is stored. Again, respective Wälzkörperlager or sliding bearings can be used.

In a modification of this embodiment, the further torsional vibration damper arrangement 138 on the other axial side of the torsional vibration damper assembly 10 be arranged and the input side to the lock-up clutch assembly 134 be coupled. The torque flow would then be from the lockup clutch arrangement 134 over the further torsional vibration damper assembly 138 on the secondary side 24 the torsional vibration damper assembly 10 , Their primary side 16 would be with the turbine wheel 118 firmly connected, which in turn to the output shaft 130 is coupled. Because in this case the turbine wheel 118 together with the primary page 16 the torsional vibration damper assembly 10 a very large mass can, on the additional mass 184 be waived.

Another embodiment of a hydrodynamic torque converter 14 is in 7 recognizable. In this embodiment, the further Torsionsschwingungsdämpferanordnung 138 in the torque transmission path between the secondary side 24 the torsional vibration damper assembly 10 and the output shaft 130 arranged. The turbine wheel 118 is to the secondary side 24 the torsional vibration damper assembly 10 and the primary side of the further torsional vibration damper assembly 138 coupled. Again, an additional mass to increase the mass 184 at the turbine wheel 118 to be available.

With the lock-up clutch disengaged 134 acts in torque conversion mode or torque transmission between the impeller 112 and the turbine wheel 118 via the fluid circulation, the further torsional vibration damper assembly 138 in the torque transmission path to the output shaft 130 , The torsional vibration damper assembly 10 as such is effective only when the lock-up clutch assembly 134 in the engagement state, otherwise increases the primary side mass of the further torsional vibration damper assembly 138 ,

Here could also in the Torsionsschwingungsdämpferanordnung 10 the torque flow be reversed. So it could be the secondary side 24 to the lockup clutch assembly 134 be coupled or docked while the primary side 16 with the turbine wheel 118 coupled, resulting in a significant increase in mass in this area and thus the possibility of adding to the additional mass 184 to renounce leads. Next, it would be possible the extra mass 184 if it should be provided for reasons of improved vibration damping characteristic, also in the torque flow before the Torsionsschwingungsdämpferanordnung 10 So, for example, to arrange at the motor-facing side.

In 8th a variant embodiment is shown, with regard to the design of the torsional vibration damper assembly 132 the in 5 shown variant corresponds. It should be noted that here, of course, the other variants explained above are conceivable. One recognizes in the 8th in that the pressurized fluid supply channel arrangement 168 here the first flow channel 158 includes, over which itself the lockup clutch assembly 134 is to be controlled. That is, in the output shaft 130 provided and the first flow channel 158 essentially providing opening or bore is via an opening 164 radially outward and thus to the secondary side 24 the torsional vibration damper assembly 10 open, which can be designed as in 3 shown. As a result, in the pressure chambers 32 ' . 32 '' on the one hand and the room area 162 on the other hand, essentially always the same pressure of the first damper fluid will be present. The consequence of this is that with the lock-up clutch disengaged 134 and correspondingly low pressure of the first damper fluid, the Torsionsschwingungsdämpferanordnung 10 is set soft, essentially a torque through direct contact between the primary side 16 and secondary side 24 transfers. In this state, then, essentially only the further torsional vibration damper arrangement 138 vibration damping effective. Will the lock-up clutch arrangement 134 engaged and thereby increases the fluid pressure, also the torsional vibration damper assembly 10 brought into a state in which the in the pressure chambers 32 . 32 ' existing pressure of the first damper fluid of the relative rotation between the primary side 16 and secondary side 24 then increasingly counteracts. By varying the fluid pressure, the vibration damping characteristic can then be influenced.

In this embodiment variant, the output shaft 130 about a camp 190 , For example, plain bearings or rolling element bearings, with respect to the housing 110 be stored. The secondary side 24 the torsional vibration damper assembly 10 is about the bearings 170 . 170 ' on the output shaft 130 stored. As with the previously described embodiments, the fluid leakage, which in the region of the sealing of the opening or the openings 164 with respect to the secondary side 24 the torsional vibration damper assembly 10 arises, in the axial direction in the housing interior 116 arrive, so that the so escaping first damper fluid with the fluid in the housing interior 116 can mix. It should be emphasized once again that the first damper fluid and the interior of the housing 116 existing fluid are preferably removed from the same reservoir and thus have the same consistency, so that mixing does not lead to problems.

With regard to the introduction of fluid into the housing interior 116 It should be noted that here too the hydrodynamic torque converter 14 basically of the three-wire type, as explained above.

In 9 is an embodiment of the hydrodynamic torque converter 14 shown in which to the lock-up clutch assembly 134 the primary side 16 the torsional vibration damper assembly 10 followed. With this is also the turbine wheel 118 coupled. The secondary side 24 the torsional vibration damper assembly 10 is about the further torsional vibration damper assembly 138 to the output shaft 130 coupled. The primary side 16 is axial with respect to the housing 110 on the one hand and on the turbine wheel 118 with respect to the stator 122 supported on the other hand. Radial is the primary side 16 about a camp 192 which alternative or in addition to the bearings 180 . 182 ( 3 ) may be provided with respect to the turbine wheel 118 stored. The secondary side of the torsional vibration damper assembly 10 is on the axial end portion of the hollow shaft support over the bearings 170 . 170 ' stored.

One for the supply of the pressure chambers 32 ' . 32 '' serving fourth flow channel 194 the pressure fluid supply channel arrangement 168 is here between the outer circumference of the output shaft 30 and the inner circumference of the hollow support shaft 126 educated. In the axial area of the secondary side 24 has these openings 196 which ones to those in the secondary side 24 provided channels are open. Between the secondary side 24 and the outer periphery of the hollow support shaft 126 creates a seal arrangement 203 with sealing elements on both axial sides of the openings 196 a substantially fluid-tight transition between the fourth flow channel 194 and the secondary side 24 , Between the output shaft 130 and the hollow support shaft 126 are dynamic seals 198 . 200 provided, which in the axial direction the fourth flow channel 194 limit. Within a transmission, the latter can then be open to a source of pressurized fluid without the need to provide a rotary union for the supply of first damper fluid.

In the output shaft 130 is the first flow channel 158 surrounding a third flow channel 202 intended. This can be realized in a way like this 3 is shown, and surrounds the first flow channel 158 coaxial. The third flow channel 202 is to the room area 174 of the housing interior 116 open and can be used to initiate fluid in these. The fluid can then in a between the hollow support shaft 126 and a pump hub 176 be withdrawn flow path formed again. Of course, the flow direction can also be reversed.

In this embodiment variant, any leaks that occur in the region of the guidance of the first damper fluid which is under very high pressure can be detected in the interior of the housing 116 be caught.

The 10 shows a modification of the in 9 shown embodiment. It should be noted that here and of course in the embodiment according to 9 the embodiment of the torsional vibration damper assembly 132 can also be chosen as shown in other embodiments.

One recognizes in 10 in that the output shaft 130 has three coaxially arranged flow channels, namely the first flow channel 158 for controlling the lockup clutch arrangement 134 , the third flow channel 202 for fluid supply or fluid discharge into or out of the housing interior 116 , as well as a second flow channel 160 , Also the fourth flow channel 194 is provided so that here now two flow channels 160 . 194 are provided, which the torsional vibration damper assembly 10 to lead. This can be designed here as in principle with respect to the 2 described, so be effective both zugseitig and thrust side by respective pressure fluid damping. This means that, for example, the fourth flow channel 194 this is done, under high pressure first damper fluid to the zugseitig effective pressure chambers 32 ' . 32 '' to deliver, or to couple these at thrust load with a fluid reservoir, while the second flow channel 160 this is the purpose of the thrust-side pressure chambers 34 ' . 34 '' with a source for un To couple ter pressurized first damper fluid or to couple with a non-pressurized fluid reservoir. In order to create a possibly induced by fluid leakage overpressure in a space area 206 between the two flow channels 160 . 194 sealing gasket assemblies 205 . 207 to avoid is in the secondary side 24 a leakage channel 208 provided this space area 206 with the housing interior 116 combines. A flow path through which then fluid into the housing interior 116 can be initiated or withdrawn from this is between the hollow support shaft 126 and the impeller hub 176 educated.

The 11 shows an embodiment variant in which the pressure fluid supply channel arrangement 168 a fifth flow channel 210 in the hollow support shaft 126 includes. The secondary side 24 the torsional vibration damper assembly 10 is for example about the bearings 170 . 170 ' on the support hollow shaft 126 stored. In this axial region is associated with the flow channel 210 one or more openings 212 provided so that the channel 210 in conjunction with the pressure chambers 32 . 32 ' can be brought. The fluid-tight transition realized the seal assembly 203 with sealing elements on both axial sides of the openings 212 ,

The supply of fluid into the housing interior 116 can have one between the output shaft 130 and the hollow support shaft 126 flow path formed while the discharge of fluid via a flow path between the hollow support shaft 126 and the impeller hub 176 can be done.

The 12 shows a variant in which in the hollow support shaft 126 the fifth flow path 210 radially surrounding a sixth flow path 214 is provided, with one or more openings 216 to the secondary side 24 the torsional vibration damper assembly 10 is open. Again, so can the zugseitig effective pressure chambers 32 ' . 32 '' for example via the flow path 210 and the thrust-side effective pressure chambers 34 ' . 34 '' over the flow path 214 be supplied.

It should be noted that in the embodiments of the 11 and 12 hollow shafts shown the flow paths formed therein 210 respectively. 214 similar as with respect to the 3 and the output shaft 130 can be generated described, so as can be provided as the axis of rotation A circulating substantially cylindrical cavities. In principle, it is also conceivable to introduce axial bores here, for example also at different circumferential regions, which are then open radially outward via radial branch bores.

In 13 a variant embodiment is shown in which the supply of the torsional vibration damper assembly 10 with pressurized first damper fluid through one between the hydrodynamic torque converter 14 and a drive unit indicated only schematically 218 arranged rotary feedthrough 220 he follows. A non-rotating rotary feedthrough area 222 may be connected to a source or a reservoir for first damper fluid. The rotating rotary feedthrough area 224 is with the case 110 connected and engages axially in this. The output shaft 130 can have a bearing in this rotating rotary feedthrough area 224 be stored. A connection approach 226 extends from the housing 110 axially on the drive shaft 12 to and can be centered in this. A flexible coupling arrangement 228 can be a non-rotatable coupling between the housing 110 and the drive shaft 12 realize.

On the rotating rotary feedthrough area 224 is in the case 110 the secondary side 24 the torsional vibration damper assembly 10 rotatably mounted, for example via two bearings 170 . 170 ' , The rotating rotary feedthrough area 224 is therefore not in the torque flow.

The pressurized fluid supply channel arrangement 168 includes a sixth flow channel 230 , The sixth flow channel 230 can have one or more axial bores or openings in the rotating rotary feedthrough area 224 include radially outward through openings 232 are open. By appropriate termination elements these holes can then be completed in the axial direction. On both sides of the opening or openings 232 are arranged dynamic seals, which provide a fluid-tight transition between the rotating rotary feedthrough area 224 and the torsional vibration damper assembly 10 realize.

In this embodiment, the lock-up clutch 134 to be able to control, ie in the room area 162 Being able to introduce fluid is in the axial region of this spatial area 162 preferably a plurality of the rotary rotary leadthrough area 224 provided by passing openings which establish a connection between the space area 162 and the first flow path 158 ,

It should be noted that of course in this embodiment also in association with the pressure fluid chambers 34 ' . 34 '' in the rotating rotary feedthrough area 224 a flow channel, for example in the form of several boh ments can be provided in order here to a two-way effective operation of the torsional vibration damper assembly 10 to be able to ensure.

A modification to this is also in 14 shown. It can be seen that, for example, the pressure fluid chambers 32 ' . 32 '' over the rotating rotary feedthrough area 224 and the sixth flow channel formed therein 230 be supplied. The unrecognizable thrust chambers effective 34 ' . 34 '' be via a second flow channel 160 supplied in the output shaft 130 is formed. Of course, here could also be a hollow shaft in the support 126 or one between the hollow support shaft 126 and the output shaft 130 formed flow channel can be used.

Another type of design is in 15 shown. In this embodiment variant, the two Torsionsschwingungsdämpferanordnungen work 10 and 138 again in series with each other, via the lock-up clutch arrangement 134 a torque first in the Torsionsschwingungsdämpferanordnung 10 is introduced, and, as set out below, in the previously assigned to the secondary side chamber housing 22 the same, and then on the previously assigned to the primary side chamber housing 20 on the further torsional vibration damper assembly 138 is transmitted. This is the output side rotatably with the output shaft 130 , So the transmission input shaft to couple.

One recognizes in 15 in that the chamber housing 22 over the up to radially inwardly extended Reibelemententräger 140 the lockup clutch arrangement 134 attached to them. The chamber housing 20 carries in the radially outer region a connecting element 300 which is a central disk element 302 the further torsional vibration damper assembly 138 radially overlaps externally and with the cover disk element 144 for example, by a Axialsteckverzahnungsformation 304 rotatably connected. Similar to the in 3 shown embodiment variant form the chamber housing 20 and the cover disk element 144 Circumferential support areas for the steam springs 142 , as well as the central disk element lying between them 302 in its radially inner area with a hub area 306 connected or integrally formed by the spline or the like with the output shaft 130 is coupled for common rotation.

In this embodiment variant forms the secondary side 16 the torsional vibration damper assembly 10 to the entrance of the further torsional vibration damper assembly 138 , essentially the connecting element 300 and the cover disk element 144 a comparatively large intermediate mass range, with which also the turbine wheel 118 is firmly connected, namely by the fact that it to the cover disk element 144 for example, by riveting is connected. For further increase in mass, for example, on the connecting element 300 an additional mass 308 be provided in the radially outer region, so that this additional mass 308 contribute significantly to the mass moment of inertia of this Zwischenmassse.

The supply of the torsional vibration damper assembly 10 with the pressure fluid required for its functionality takes place through the transmission input shaft 30 therethrough. The output shaft 130 points to provided by two inserts 156 and 310 three mutually coaxial flow channels 158 . 160 such as 312 on. Through to the axial end of the two insert parts 156 . 310 built-up output shaft 130 leading flow channel 148 this can be used to operate the lock-up clutch assembly 134 required pressure fluid to be supplied or removed, with which also the clutch piston 136 can be acted upon. Through the radial then following flow channel 160 through can pressure fluid to a pair of the pressure chambers, so for example the pressure chambers 32 ' . 32 '' be directed to vary the pressure of the incompressible damper fluid therein. For this purpose, the insert part 310 , the output shaft 130 , one on the inner peripheral side of the chamber housing 22 the secondary side 24 firmly provided sleeve 314 and the chamber housing 22 radially inwardly or radially outwardly leading, mutually associated openings. At relative rotation between the secondary side 24 the torsional vibration damper assembly 10 and the output shaft 130 However, to have a connection ready, for example, on the outer circumference of the output shaft 130 an annular groove 316 be provided. This could of course also on the inner circumference of the sleeve 314 be arranged. On both sides of this annular groove are two sealing rings, such as rectangular sealing rings, which ensure a fluid-tight seal.

The between the insert part 310 and the actual output shaft 130 limited, radially outermost flow channel 312 is also over in the output shaft 130 , the sleeve 314 and the chamber housing 22 the secondary side 24 formed openings in connection with the other pair of pressure chambers 34 . 34 '' so as to be able to vary the fluid pressure therein. Here is, for example, on the inner peripheral surface of the sleeve 314 a circumferential groove 318 provided in order to maintain this fluid connection regardless of the relative rotational state. On both sides of this circumferential groove 318 are two sealing elements, for example, law corner sealing rings, provided, which again ensure a fluid-tight seal. You can see that between the two grooves 316 and 318 lying sealing element for both flow channels 312 and 116 is equally effective, so this seals with respect to each other. Of course, could also be the groove 318 on the outer circumference of the output shaft 130 be provided.

One recognizes in 15 in that all of the fluid feedthrough serve radially outward openings and grooves on the output shaft 130 are provided in an end region thereof, beyond the coupling of the output shaft 130 at the hub area 306 is located, so not in the torque flow of a drive train. This ensures that even at comparatively high torques, which are to be transmitted via a drive train, a forcibly occurring by the introduction of openings or grooves weakening of the output shaft 130 their torque transfer capacity is not affected.

The chamber housing 20 . 22 the torsional vibration damper assembly 10 are over two between the two chamber housings 20 and 22 effective bearings 320 . 322 , In particular needle roller bearings or the like, mounted on two in axially with respect to each other at a distance from each other positions. These are radially within that range in which the two chamber housing 20 . 22 also sealed with respect to each other. The transmission input shaft 130 is about two more camps 324 . 326 , For example, also designed as a needle bearing, with respect to the secondary side 24 the torsional vibration damper assembly 10 radially mounted. It can be seen that the bearing 324 between the hardened sleeve, for example 314 and the insert part 310 the output shaft 30 is arranged while the warehouse 322 directly between the chamber housing 22 and the output shaft 130 is effective.

The axial bearing takes place via two Axialwälzkörperlager known to be located on both sides of a freewheel arrangement of the stator, as well as between the radially inner region of the cover disk element 144 and the central disk element 302 effective axial bearing 328 , For example in the form of a thrust washer. Furthermore, the hub area 306 , So the output range of the further torsional vibration damper assembly 138 through an axial rolling element bearing 330 at the chamber housing 22 axially stored. This in turn is over the sleeve firmly connected to it 314 and another Axialwälzkörperlager 332 on a ring-like component 334 axially supported, which via another Axialwälzkörperlager 336 on the housing 110 is supported. The component 334 is radially inward on the output shaft 130 , in particular the insert 110 , Centered to produce a fluid-tight seal and leads on its outside the clutch piston 136 during its axial movement. Of course, this component could 334 also on the housing 110 be set.

The bearing of the output shaft 130 with respect to the chamber housing 22 could alternatively or additionally also in an area between the two grooves 316 and 318 respectively. In this case, for the fluid-tight separation of these two areas then two axially on both sides of a bearing to be arranged there bearing to be positioned sealing elements required. Fluid leaks that occur in the area of these seals get into the housing 110 formed wet space and can be recirculated in a conventional manner with the fluid used for torque transmission or conversion.

To when inserting the output shaft 130 To avoid damage to the various sealing elements or to simplify this process, is the output shaft 130 with their inserts, especially the insert 310 , designed with the outer end decreasing towards the free end region. The existing transition stages can be formed by bevels. Of course it is also possible, the output shaft 130 over its entire length with a substantially uniform outer dimension.

In the torque transmitting operation with the lock-up clutch arrangement engaged, therefore, a torque from the housing 110 via the lockup clutch arrangement 134 or the Reibelemententräger 140 the same first on the chamber housing 22 the torsional vibration damper assembly 10 passed and over the chamber housing 20 on the entrance of the further torsional vibration damper assembly 138 , essentially provided by the connecting element 300 , the cover disk element 144 directed. The circumferentially at this input area supporting damper springs 142 give the torque to the central disc element 302 or the hub area 306 the same and thus on the output shaft 300 with open lockup clutch arrangement 134 , so in torque conversion mode, the torque on the housing 110 in the turbine wheel 118 which is connected to the input region of the further torsional vibration damper arrangement 138 namely the cover disk element 144 , is firmly connected. Thus, the further torsional vibration damper assembly 138 also in the torque conversion mode with disengaged lock-up clutch assembly 134 effective for vibration damping and has with the Torsionsschwingungsdämpferan order 10 a very high input-side mass.

To operate the lock-up clutch assembly 134 can, as already stated, via the flow channel 158 the output shaft 130 Pressure fluid are supplied, thereby the clutch piston 136 to act on. The supply or removal of fluid, so for example oil in the interior of the housing 110 , In particular for cooling the entire assembly and to establish the fluid circulation between the impeller and the turbine can be done in a conventional manner on both axial sides of the stator, for example via between a support shaft of the stator and the output shaft on the one hand and the support shaft and a pump hub on the other formed flow channels. Here, in the interior of the housing 110 a bias pressure to be built, which the provision, ie the disengagement of the clutch piston 136 , supports or effects.

It should be noted in addition to this embodiment that, of course, also here various constructive variations are possible. For example, this could already be the primary side of the torsional vibration damper arrangement 10 assigned chamber housing 20 over the friction element carrier 140 to the lockup clutch assembly 134 be tethered while the chamber housing 22 then with the output shaft 130 either rigid or can be connected via another, damper springs using Torsionsschwingungsdämpferanordnung. This further torsional vibration damper arrangement could then also be designed such that it is effective in a torque range which is still below the pretensioning torque range of the torsional vibration damper arrangement 10 is located, so that even for small torque fluctuations to be transmitted a damping functionality can be provided.

In the embodiment variants described above with reference to the figures, the fluid conveying arrangement comprises 35 in each case the assemblies also described, in particular those assemblies that define the pressure chambers. In this embodiment, a limit is set by the pressure chambers in the circumferential direction bounding walls of the relative rotation between the primary side and the secondary side of the Torsionsschwingungsdämpferanordnung. In an alternative embodiment variant with regard to the fluid conveying arrangement, this could comprise a gear pump or the like which is driven for rotation by the relative rotation between the primary side and the secondary side and fluid in the direction of a fluid pressure accumulator arrangement, for example the chamber subassembly described above, by intermeshing intermeshing tooth areas. leads or dissipates from there. This also substantially supports the torque to be transmitted between the primary side and the secondary side via the essentially incompressible damper fluid, which in turn loads the compressible damper fluid via the separating elements or separating pistons. An advantage of the embodiment with such a gear pump is that it can operate without a rotation angle limit for the rotation between the primary side and the secondary side.

It be final noted that, of course, in the preceding described embodiments, the various variants shown the torsional vibration damper assembly on the one hand and the fluid supply of the various pressure chambers On the other hand, are arbitrarily combined with each other. Next is noted that the various flow channels described, of course, respectively comprise a plurality of circumferentially discretely arranged channel sections can, For example, each pressure chamber is a separate channel section a respective flow channel can be assigned. Next it should be noted that to share or shut off respective flow channels for supply or removal of first damper fluid To or from the pressure chambers valve arrangements may be provided which for example, be positioned in a transmission.

Claims (21)

Hydrodynamic coupling device, in particular torque converter, comprising a fluid-filled or fillable housing ( 110 ) with a pump wheel ( 112 ), one in a housing interior ( 116 ) arranged turbine wheel ( 118 ), which with an output member ( 130 ) for common rotation about a rotation axis (A) is coupled or coupled, and a lock-up clutch assembly ( 134 ), via which optionally a torque transmission connection between the housing ( 110 ) and the output member ( 130 ), wherein in the torque transmission path between the lock-up clutch arrangement ( 134 ) and the output member ( 130 ) and / or in the torque transmission path between the turbine wheel ( 118 ) and the output member ( 130 ) a torsional vibration damper assembly ( 132 ) with a torsional vibration damper arrangement ( 10 ), wherein the torsional vibration damper arrangement ( 10 ) a primary page ( 16 ) and one via a damper fluid arrangement with the primary side ( 16 ) for rotation about an axis of rotation (A) and for relative rotation with respect to each other coupled secondary side ( 24 ) wherein the damper fluid arrangement comprises a fluid pressure storage arrangement ( 47 ) as well as a fluid conveying arrangement ( 35 ), by which during relative rotation of the primary side with respect to the secondary side of the accumulator pressure in the fluid pressure accumulator arrangement ( 47 ) is changeable. Hydrodynamic coupling device according to claim 1, characterized in that the damper fluid arrangement a torque between the primary side ( 16 ) and the secondary side ( 24 ) transmitting first damper fluid having a lower compressibility in a first damper fluid chamber arrangement ( 36 ) as well as pressure increase of the first damper fluid in the first damper fluid chamber arrangement ( 36 ) loaded second damper fluid with higher compressibility in a second damper fluid chamber assembly ( 76 ), wherein the second damper fluid chamber arrangement ( 76 ) at least one chamber unit ( 46 ) and in association therewith a separating the first damper fluid from the second damper fluid and when changing pressure in the chamber unit ( 46 ) displaceable separating element ( 48 ), wherein the first damper fluid chamber arrangement ( 36 ) at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ) with relative rotation of the primary side ( 16 ) with respect to the secondary side ( 24 ) variable volume and in association with this a connection volume ( 60 . 62 . 64 . 66 ) includes for receiving by reducing the volume of the at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ) from this displaced first damper fluid for acting on the separating element ( 48 ) of the at least one chamber unit ( 46 ). Hydrodynamic coupling device according to claim 1 or 2, characterized in that the primary side ( 16 ) of the torsional vibration damper arrangement ( 10 ) with the lock-up clutch arrangement ( 134 ) and the secondary side ( 24 ) of the torsional vibration damper arrangement ( 10 ) with the output member ( 130 ) is coupled or can be coupled. Hydrodynamic coupling device according to claim 3, characterized in that the primary side ( 16 ) of the torsional vibration damper arrangement ( 10 ) via a further torsional vibration damper arrangement ( 138 ) with the lock-up clutch arrangement ( 134 ), wherein the further torsional vibration damper arrangement ( 138 ) a damper element arrangement with at least one elastically deformable spring element ( 142 ). Hydrodynamic coupling device according to claim 3 or 4, characterized in that the secondary side ( 24 ) of the torsional vibration damper arrangement ( 10 ) via a further torsional vibration damper arrangement ( 138 ) with the output member ( 136 ) is coupled or can be coupled, wherein the further torsional vibration damper arrangement ( 138 ) a damper element arrangement with at least one elastically deformable spring element ( 142 ). Hydrodynamic coupling device according to claim 5, characterized in that the secondary side ( 24 ) of the torsional vibration damper arrangement ( 10 ) via the further torsional vibration damper arrangement ( 138 ) and the turbine wheel ( 118 ) with the output member ( 130 ) is coupled or can be coupled. Hydrodynamic coupling device according to claim 5, characterized in that the turbine wheel ( 118 ) with the secondary side ( 24 ) of the torsional vibration damper arrangement ( 10 ) is coupled. Hydrodynamic coupling device according to one of claims 3 to 5, characterized in that the turbine wheel ( 118 ) with the primary side ( 16 ) of the torsional vibration damper arrangement ( 10 ) is coupled. Hydrodynamic coupling device according to one of claims 2 to 8, characterized in that for at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ) of the torsional vibration damper arrangement ( 10 ) a pressurized fluid supply channel arrangement ( 168 ) is provided for supplying pressurized first damper fluid thereto. Hydrodynamic coupling device according to claim 9, characterized in that the output member ( 130 ) an output shaft ( 130 ) and that in the output shaft ( 130 ) a first flow channel ( 158 ) for controlling the lock-up clutch arrangement ( 134 ) is provided. Hydrodynamic coupling device according to claim 10, characterized in that the pressurized fluid supply channel arrangement ( 168 ) the first flow channel ( 158 ) in the output shaft ( 130 ). Hydrodynamic coupling device according to claim 10, characterized in that the pressurized fluid supply channel arrangement ( 168 ) a second flow channel ( 160 ) in the output shaft ( 130 ) for supplying first damper fluid to at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ). Hydrodynamic coupling device according to claim 12, characterized in that the second flow channel ( 160 ) the first flow channel ( 158 ) concentrically surrounds substantially. Hydrodynamic coupling device according to one of claims 10 to 13, characterized in that in the output shaft ( 130 ) a third flow channel ( 202 ) for the supply and / or removal of fluid to or from the housing interior ( 116 ) is provided. Hydrodynamic coupling device according to one of claims 10 to 14, characterized in that a hollow support shaft ( 126 ) the output shaft ( 130 ) and that the pressure fluid supply channel arrangement ( 168 ) one between the hollow support shaft ( 126 ) and the output shaft ( 130 ) formed fourth flow channel ( 194 ) for supplying first damper fluid to at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ). Hydrodynamic coupling device according to one of claims 10 to 15, characterized in that a hollow support shaft ( 126 ) and that the pressure fluid supply channel arrangement ( 168 ) one in the hollow support shaft ( 126 ) formed fifth flow channel ( 210 ) for supplying first damper fluid to at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ). Hydrodynamic coupling device according to claim 16, characterized in that the pressure fluid supply channel arrangement ( 168 ) one in the hollow support shaft ( 126 ) formed sixth flow channel ( 214 ) for supplying first damper fluid to at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ). Hydrodynamic coupling device according to claim 17, characterized in that the sixth flow channel ( 214 ) the fifth flow channel ( 210 ) is arranged substantially concentrically surrounding. Hydrodynamic coupling device according to one of claims 2 to 18, characterized in that on a drive unit ( 218 ) facing side of the housing ( 110 ) a rotary union ( 220 ) with one with the housing ( 110 ) associated rotary rotary feedthrough area ( 224 ), the pressure fluid supply channel arrangement ( 168 ) a seventh flow channel ( 230 ) in the rotating rotary feedthrough area ( 224 ) for supplying first damper fluid to at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ). Drive system for a vehicle, comprising a drive unit and a torque between a drive shaft ( 12 ) of the drive unit and a hydrodynamic coupling device ( 14 ), in particular hydrodynamic torque converter, transmitting Torsionsschwingungsdämpferanordnung ( 10 ), wherein the Torsionsschwingungsdämpferanordnung ( 10 ) a primary page ( 16 ) and one via a damper fluid arrangement with the primary side ( 16 ) for rotation about an axis of rotation (A) and for relative rotation with respect to each other coupled secondary side ( 24 ), wherein the damper fluid arrangement comprises a fluid pressure storage arrangement ( 47 ) as well as a fluid conveying arrangement ( 35 ), by which during relative rotation of the primary side with respect to the secondary side of the accumulator pressure in the fluid pressure accumulator arrangement ( 47 ) is changeable. Hydrodynamic coupling device according to claim 20, characterized in that the damper fluid arrangement has a torque between the primary side ( 16 ) and the secondary side ( 24 ) transmitting first damper fluid having a lower compressibility in a first damper fluid chamber arrangement ( 36 ) as well as pressure increase of the first damper fluid in the first damper fluid chamber arrangement ( 36 ) loaded second damper fluid with higher compressibility in a second damper fluid chamber assembly ( 76 ), wherein the second damper fluid chamber arrangement ( 76 ) at least one chamber unit ( 46 ) and in association therewith a separating the first damper fluid from the second damper fluid and when changing pressure in the chamber unit ( 46 ) displaceable separating element ( 48 ), wherein the first damper fluid chamber arrangement ( 36 ) at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ) with relative rotation of the primary side ( 16 ) with respect to the secondary side ( 24 ) variable volume and in association with this a connection volume ( 60 . 62 . 64 . 66 ) includes for receiving by reducing the volume of the at least one pressure chamber ( 32 ' . 32 '' . 34 ' . 34 '' ) from this displaced first damper fluid for acting on the separating element ( 48 ) of the at least one chamber unit ( 46 ).