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WO2008080484A1 - Ensemble amortisseur de vibrations de torsion - Google Patents

Ensemble amortisseur de vibrations de torsion Download PDF

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Publication number
WO2008080484A1
WO2008080484A1 PCT/EP2007/010504 EP2007010504W WO2008080484A1 WO 2008080484 A1 WO2008080484 A1 WO 2008080484A1 EP 2007010504 W EP2007010504 W EP 2007010504W WO 2008080484 A1 WO2008080484 A1 WO 2008080484A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
damper fluid
damper
assembly
arrangement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2007/010504
Other languages
German (de)
English (en)
Inventor
Cora Carlson
Andreas Orlamünder
Thomas Dögel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of WO2008080484A1 publication Critical patent/WO2008080484A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/16—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material
    • F16F15/161—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material characterised by the fluid damping devices, e.g. passages, orifices

Definitions

  • the present invention relates to a torsional vibration damper arrangement, in particular for the drive train of a vehicle, comprising a primary side and a secondary side coupled via a damper fluid arrangement with the primary side for rotation about an axis of rotation and for relative rotation with respect to each other.
  • a torsional vibration damper arrangement in which the elasticity required for vibration damping is provided by a damper fluid arrangement comprising a substantially incompressible first damper fluid, ie a liquid, and a compressible second damper fluid, ie a gaseous medium , includes.
  • the first, non-compressible damper fluid is arranged in pressure chambers, which change their volume during relative rotation between the primary side and the secondary side. When the volume is reduced, first damper fluid is displaced out of these pressure chambers into connection chambers arranged radially outside it.
  • Each connecting chamber is separated by a separating piston displaceable in the circumferential direction from a compensation chamber located radially outside a respective pressure chamber and extending substantially in the circumferential direction, in which second damper fluid is arranged.
  • the separating piston is displaced by the volume fraction of the first pressure fluid which is increased in the connecting chamber, namely by compression of the second damper fluid.
  • a torsional vibration damper arrangement in particular for the driveline of a vehicle, comprising a primary side and a secondary side coupled via a damper fluid arrangement with the primary side for rotation about a rotation axis and for relative rotation with respect to each other
  • a damper fluid assembly comprising a first damper fluid having a lower compressibility in a first damper fluid chamber assembly and transmitting a second damper fluid having a higher compressibility in a second damper fluid chamber assembly loaded upon pressure increase of the first damper fluid in the first damper fluid chamber assembly, the second damper fluid chamber assembly comprising at least one damper fluid chamber assembly Chamber unit, with respect to the first damper fluid chamber arrangement ange ⁇ radially outside and / or radially inside rdnet, wherein in association with each chamber unit, a first damper fluid from the second damper fluid separating and displaceable in the chamber unit in the direction of the axis of rotation displaceable pressure change is provided.
  • the at least one chamber unit of the second damper fluid chamber arrangement is arranged radially outside with respect to the first damper fluid chamber arrangement.
  • the second damper fluid chamber arrangement comprises at least one chamber unit surrounding the first damper fluid chamber arrangement, wherein the separating element separating the first damper fluid from the second damper fluid of the at least one chamber unit is designed like a ring.
  • the at least one chamber unit of the second damper fluid chamber arrangement is arranged radially inward with respect to the first damper fluid chamber arrangement.
  • the second damper fluid chamber assembly has at least one concentric to the axis of rotation concentrically arranged chamber unit, said separating the first damper fluid from the second damper fluid separating element of the at least one chamber unit substantially circular disc-like is trained.
  • the torsional vibration damper arrangement according to the invention can be constructed, for example, such that the first damper fluid chamber arrangement at least one during relative rotation of the primary side with respect to the secondary side in a first relative rotational direction in volume reducible first pressure chamber, which communicates via a connecting chamber in operative connection with at least one of these associated chamber unit of the second damper fluid chamber arrangement.
  • the first damper fluid chamber arrangement has at least one second pressure chamber which can be reduced in volume in a volume which can be reduced in volume relative to the secondary side relative to the secondary side in a second relative direction of rotation opposite the first relative direction of rotation, which second chamber is reducible via a connecting chamber An operative connection with at least one of these associated chamber unit of the second damper fluid chamber arrangement is.
  • the at least one first pressure chamber and / or the at least one second pressure chamber may be circumferentially extending so that generally the first damper fluid chamber assembly has an annular structure about the axis of rotation.
  • one side of the primary side and the secondary side comprises a first substantially cylindrical chamber housing and that the other side of the primary side and secondary side inserted into the first cylindrical chamber housing and with this an annular space limiting second cylindrical chamber housing, wherein on the first chamber housing at least one on the second chamber housing to be extended occidentallycksbegrenzungsvorsprung is provided and on the second chamber housing at least one to the first chamber housing to be extended second circumferential limiting projection is provided and wherein between each of a first peripheral limiting projection and a second circumferential boundary projection is a pressure chamber in the circumferential direction is limited and the volume of the pressure chamber by relative circumferential movement of the limiting this limiting boundary is changeable.
  • At least one chamber unit of the second damper fluid chamber arrangement assigned to a first pressure chamber of the first damper fluid chamber arrangement be in pressure compensation connection with at least one further chamber unit of the second damper fluid chamber arrangement which is associated with a second pressure chamber of the first damper fluid chamber arrangement.
  • a torsional vibration damper arrangement in particular for the drive train of a vehicle, comprising a primary side and via a damper fluid arrangement with the primary side for rotation about a rotation axis and for relative rotation with respect to each other coupled secondary side
  • the damper fluid arrangement a Torque between the primary side and the secondary side comprises first damper fluid having lower compressibility in a first damper fluid chamber assembly and comprises a second damper fluid with higher compressibility in a second damper fluid chamber assembly loaded upon pressure increase of the first damper fluid in the first damper fluid chamber assembly
  • the second Damper fluid chamber assembly comprises a plurality of chamber units, wherein in association with each chamber unit a first damper fluid from the second damper fluid separating and displaceable in pressure change in the chamber unit separating element is provided, wherein at least two chamber units of the second damper fluid chamber assembly, a composite chamber unit with a common volume for the form second damper fluid and the second damper fluid of each composite chamber unit is compressible
  • a larger gas volume can then be utilized in different load states.
  • the first damper fluid chamber arrangement has at least one first pressure chamber which can be reduced in volume relative to the secondary side relative to the secondary side in a first relative direction of rotation, which is operatively connected via a connection chamber with at least one of these associated chamber unit of a composite chamber unit of the second
  • Dämpferfluidhuntanssen is, and at least one in relative rotation of the primary side relative to the secondary side in a first relative direction opposite second relative rotational direction reducible in its volume second pressure chamber, which communicates via a connecting chamber in operative connection with at least one of these associated chamber unit of the same composite chamber unit of the second damper fluid chamber assembly ,
  • the at least one first pressure chamber and / or the at least one second pressure chamber may be designed to extend in the circumferential direction, so that here too a substantially annular structure of the first Damper fluid chamber arrangement is obtained.
  • one side of the primary side and the secondary side comprises a first substantially cylindrical chamber housing and that the other side of the primary side and secondary side comprises a second cylindrical chamber housing inserted into the first cylindrical chamber housing and defining an annular space therewith
  • Chamber housing is provided at least one to the second chamber housing to be extended Lease chiefsbegrenzungsvorsprung and on the second chamber housing at least one extending on the first chamber housing second circumferential limiting projection and wherein between each of a first peripheral boundary projection and a second peripheral limiting projection a pressure chamber is limited in the circumferential direction and the volume of the pressure chamber is variable by relative circumferential movement of these limiting peripheral boundary projections.
  • the separating element can be displaced substantially in the direction of the axis of rotation, so that, as stated above, neither centrifugal forces nor circumferentially acting mass inertia forces can influence the positioning of such a separating element.
  • such a separating element it is possible for such a separating element to be displaceable substantially in the circumferential direction with respect to the axis of rotation or else to be displaced substantially radially with respect to the axis of rotation.
  • the separating element may be formed as a separating piston.
  • a separating membrane which is fixed in its peripheral region and can then move with its central region in the particular intended direction.
  • the first damper fluid chamber arrangement is in connection with a source or / and a reservoir for the first damper fluid via a rotary feedthrough or can be brought.
  • Fig. 1 is a longitudinal sectional view of a Torsionsschwingungsdämpferanaku
  • FIG. 2 is a partial cross-sectional view of the torsional vibration damper assembly shown in FIG. 1; FIG.
  • FIG. 3 is a view corresponding to FIG. 1 of an alternative torsional vibration damper arrangement
  • FIG. 4 is a partial cross-sectional view of the torsional vibration damper assembly shown in FIG. 3; FIG.
  • FIG. 5 shows a further longitudinal sectional view of an alternative constructed torsional vibration damper assembly
  • FIG. 6 is a cross-sectional view of the torsional vibration damper assembly shown in FIG. 5; FIG.
  • FIG. 7 is a view corresponding to FIG. 5 of an alternative torsional vibration damper arrangement
  • FIG. 8 is a cross-sectional view of the torsional vibration damper assembly shown in FIG. 7.
  • a torsional vibration damper assembly is generally designated 10.
  • This torsional vibration damper arrangement 10 described in detail below comprises a primary side 12, which is to be fixed, for example, in its radially inner region with a plurality of threaded bolts 14 on a drive shaft, for example a crankshaft of an internal combustion engine.
  • a friction clutch 20 which may be of conventional design.
  • the portion of a driveline of a vehicle following the torsional vibration damper assembly 10 may be implemented in a variety of ways and may include, for example, an electric machine, a hydrodynamic torque converter, a fluid coupling, or the like.
  • the primary side 12 comprises a first substantially ring-like chamber housing 22, in which a second substantially ring-like chamber housing 24 of the secondary side 18 is positioned radially inwardly.
  • the two chamber housings 22, 24 form a first damper fluid chamber arrangement, generally designated 26.
  • these pressure chambers 30, 32 bounded by respective peripheral boundary projections 34 on the first chamber housing 22 and peripheral boundary projections 36 on the second Chamber housing 24.
  • the provided on one of the chamber housing 22 and 24 perimeter limiting projections 34 and 36 each extend radially to the other chamber housing and lie there to provide a tight completion of circumferentially through these limited pressure chambers 30, 32 at the other chamber housing , It should be noted that in Fig.
  • the first damper chamber assembly 26 includes four circumferentially successive pressure chambers 30 and 32, wherein the pressure chamber 30 and the latter at an angular distance of 180 ° opposite and not visible in Fig. 2 pressure chamber is referred to as the first pressure chamber, while the Pressure chamber 32 and the pressure chamber, not shown, and this also with a circumferential distance of approximately 180 ° opposite pressure chamber is hereinafter referred to as a second pressure chamber.
  • the chamber housing 22 engages with a cylindrical projection 36, the second chamber housing 24 radially inward.
  • a sleeve-like sliding bearing element 38 provides both a radial and an axial bearing function of these two chamber housing 22, 24 ready.
  • the first damper fluid chamber assembly 26, the pressure chambers 30, 32 are also limited in the axial direction by the first chamber housing 22 and a cover plate 40, radially outwardly surrounding a second damper fluid chamber assembly 42 is provided.
  • this comprises two chamber units 44, 46, which are concentrically arranged about the axis of rotation A of the torsional vibration damper arrangement and preferably extend annularly about the axis of rotation A.
  • the two chamber units 44, 46 are substantially cylindrical in one or by a common axis in the axial direction Circumferentially provided toroidally shaped housing portion 48. In this housing portion 48, two annular disk-like separating piston 50 and 52 are provided.
  • these separating pistons 50 and 52 are displaceable in the axial direction, wherein they respectively at their outer circumference or on its inner circumference, respectively providing a fluid-tight seal on an inner peripheral wall 54 and an external abut circumference wall 56 of the housing portion 48 and are guided there in the axial direction.
  • a connecting chamber 58, 60 is formed in each case.
  • a respective annular stop member 62 and 64 of the axial travel of the piston 50, 52 is limited, so that during the movement of the separating piston 50, 52, the volumes of the connecting chambers 58, 60 can not fall below a certain minimum value.
  • the connecting chambers 58, 60 in communication with the pressure chambers 30, 32.
  • each of the pressure chambers 30, by a connection opening 68 associated therewith in communication with the connecting chamber 60, while each pressure chamber 32 through its associated connection opening 66 in communication with the connecting chamber 58.
  • the separating piston 50 cooperate.
  • a volume 70 which is variable in size as a function of the axial position of these separating pistons 50, 52 is formed.
  • a compressible damper fluid such as gas, such as air, included.
  • the gas contained in the volume 70 is thus loaded by different ones of the separating pistons 50, 52. That is, this volume 70, with the compressible damper fluid contained therein, is associated with both chamber units 44, 46 to form a composite chamber unit 72.
  • Their function in Vibration damping operation will be explained below.
  • channels 76, 78 are provided in particular also in an axial extension 74, wherein the channel 76 leads to the pressure chambers 30, while the channel 78 leads to the pressure chambers 32.
  • a ring-type rotary feedthrough element 82 is provided for providing a rotary feedthrough, generally designated 80.
  • This includes respective radial channels 84, 86 provided in association with channels 76, 78 and may be through a valve assembly in communication with a source of pressurized incompressible damper fluid. In this way, the pressure of the incompressible damper fluid fed via the channels 84, 86 or 76, 78 into the pressure chambers 30, 32 and the associated connection chambers 60, 58 can be changed.
  • pressure seals 88, 90, 82 are respectively provided between and also axially outside the radial channels 84, 86.
  • Bearings 94, 96 are provided on the axial outer sides of the pressure seals 90, 92, via which the rotary leadthrough element 80 is rotatably mounted axially and radially on the extension 74 of the second chamber housing 24. Axially outside of these bearings 94, 96 are then flow seals 98, 100 are arranged. The existing between the pressure seal 90 and the flow seal 98 and the bearing 94 receiving space area can be emptied via a formed in the rotary feedthrough element 82 radial passage 102.
  • the space area formed between the pressure seal 92 and the volume flow seal 100 and containing the bearing 96 can be emptied via a radial passage 104.
  • a drainage functionality for the pressure seals 90 and 92 overcoming damper fluid can be provided.
  • the pressure conditions be adjusted so that are biased by the prevailing in the volume 70 pressure of the compressible damper fluid, the two separating pistons 50, 52 in their maximum remote positioning, in which they the respective associated stop elements 62 and 64 abut. In this way it is ensured that the leading to the connecting chambers 58, 60 channels 66, 68 are not covered.
  • the two chamber housings 22, 24 can assume the relative circumferential positioning recognizable in FIG. 2 with respect to each other, in which their peripheral limiting projections 34 and 36 have a mutual circumferential distance of approximately 90 °, so that for the first pressure chambers 30 and the second pressure chambers 32 respectively same volume is provided.
  • a torque is transmitted, for example, from the primary side 12 to the secondary side 18, which means that the drive system is in a tensile state, and this torque is introduced in such a way that in the illustration of FIG Chamber housing 24, the first chamber housing 22 is rotated counterclockwise, this means a load of existing in the pressure chambers 30 incompressible damper fluid. Due to the increase in pressure in the pressure chambers 30, the pressure in the connecting chamber 60 assigned to these pressure chambers 30 will also increase. If this pressure then exceeds the prestressing pressure which is exerted by the compressible damper fluid on the separating piston 52, then the separating piston 52 will shift out of its basic position in the direction of the other separating piston 50.
  • the compressible damper fluid is compressed in the volume range 70 and increases its pressure accordingly.
  • This axial displacement of the separating piston 52 in the case of an axially stationary separating piston 50 is accompanied by the relative rotation of the two chamber housings 22, 24 which is now possible due to the displacement of the incompressible damping fluid out of the pressure chambers 22 with respect to each other.
  • the volumes of the two first pressure chambers 30 decrease accordingly.
  • the torsional vibration damper arrangement 10 shown in FIGS. 1 and 2 has significant advantages due to its structural design with efficient space utilization.
  • the separating pistons 50, 52 are arranged so that they are axially displaceable to fulfill their functionality. That is, neither the centrifugal forces occurring during rotational operation nor the circumferential accelerations occurring during torsional oscillations influence the positioning of the separating pistons 50, 52, so that they can actually fulfill their functionality in the vibration damping without significant influence by external circumstances. In principle, this would also be possible if the two chamber units 44, 46 were not combined to form a composite chamber unit 72, but if, for example, between the two separating pistons 50, 52 a volume region 70 is separated into two Chamber dividing partition would be present. It would also be possible to provide only one of the separating pistons 50 and 52, in which case a connection chamber and correspondingly also a vibration damping functionality would then also be provided only in association with the first pressure chambers 30 or the second pressure chambers 32.
  • a second principle which can also be seen in the illustration of FIG. 1, relates to connecting the two chamber units 44, 46 to a composite chamber unit 72.
  • a further advantage of the design shown in FIG. 1 is that a comparatively large volume, filled only with the gaseous, incompressible fluid, is present radially on the outside of the primary side 12, so that better spin acceleration values can be achieved due to the comparatively low moment of inertia.
  • FIGS. 3 and 4 A modified embodiment of a structure of a torsional vibration damper arrangement which utilizes the above-described functional principles or design principles is shown in FIGS. 3 and 4.
  • components that correspond to components described above in terms of structure and function are denoted by the same reference numeral with the addition of an appendix "a".
  • the second damper fluid chamber arrangement with respect to the first damper fluid chamber arrangement was arranged radially outward, is in the in FIGS. 3 and 4 shown variant, a reversal of the radial assignment.
  • the first damper fluid chamber assembly 26a is disposed radially outward of the second damper fluid chamber assembly 42a. It can be seen for this purpose that the now completely radially outer first chamber housing 22a with the radially likewise enlarged second chamber housing 24a again delimits the annular space region 28a, in which the pressure chambers 30a and 32a, respectively bounded in the circumferential direction by the peripheral boundary projections 34a and 36a, follow one another.
  • the radial mounting of the two chamber housings 22a and 24a can take place via a bearing 38a which acts between the second chamber housing 24a and the plate 40a firmly connected to the first chamber housing 22a. Furthermore, the channels 76a and 78a leading to the pressure chambers 30a and 32a are again provided in the second chamber housing 24a.
  • the structure of the rotary feedthrough 80a corresponds to the above-described, so that in this regard and also with respect to the coupling of the friction clutch 20a to the axial extension 74a of the second chamber housing 24a to the above statements.
  • the two separating pistons 50a, 52a of the chamber units 44a, 46a forming a composite chamber unit 72a are now provided radially inward in a housing region 48a provided essentially by the second chamber housing 24a.
  • this housing portion 48a is formed with respect to the axis of rotation A is substantially cylindrical and concentric with the axis of rotation A, axially closed space in which the circular disk-like designed here separating piston 50a, 52a are received axially displaceable. Again, they rest against an inner peripheral surface 54a of this common housing portion 48a to form a tight seal.
  • the volume region 70a is formed, which contains the compressible damper fluid.
  • the connecting chambers 58a and 60a are formed, in which again the channel-like openings 66a and 68a open, which connect to the pressure chambers 32a and 30a.
  • the separating piston 50a, 52a in the direction of each other To provide an Axialroisanschlag, are now provided in the radially inner region by these loaded or their Axialhub limiting stop elements 62a, 64a, so as to ensure that the separating piston 50a, 52a, the openings 66a, 68a can not close.
  • the primary side 12a is coupled to the drive shaft 112a shown here via a flex plate arrangement 114a or the like, which is radially inward through the threaded bolts 14a to the drive shaft 12a is connected and is connected radially outwardly by bolt 116a or the like to the chamber housing 22a of the primary side 12a.
  • FIGS. 3 and 4 The embodiment variant shown in FIGS. 3 and 4 is characterized by a particularly simple construction.
  • the principle of utilizing an axial displacement of a separating piston or other separating element can also be used if only one chamber unit is provided or if the volume area 70a by a partition or the like into two separate and the respective Chamber units 44a and 46a associated subvolume areas is divided.
  • FIGS. 5 and 6 show a further embodiment of a torsional vibration damper arrangement.
  • parts or assemblies which previously described with regard to structure or function, with the same reference numeral with the addition of the appendix "b".
  • Damper fluid chamber assembly 26b is arranged.
  • a housing portion 48b providing or containing substantially the second damper fluid chamber arrangement 42b is arranged with a substantially ring-like shape radially inside the second chamber housing 24b and is also non-rotatably connected thereto.
  • the housing portion 48b now contains four chamber units 44b, 46b, 44b 1 , 46b 'with these respectively associated separating piston 50b, 52b, 50b 1 , 52b'. These separating pistons move in the circumferential direction along the annular formed in the housing portion 48b, so in the circumferential direction extending recesses with a corresponding pressure load. Again, two of the chamber units 44b, 46b, 44b ', 46b 1 form a composite chamber unit 72b or 72b'.
  • the chamber unit 46b interacting with the pressure chamber 30b forms with its separating piston 52b and the chamber unit 44b cooperating with the pressure chamber 32b with its separating piston 50b the composite chamber unit 72b extending approximately over a circumferential extension of 180 ° with the volume area 70b.
  • the cooperating with the pressure chamber 30b 1 chamber unit 46b 1 form with their separating piston 52b 1 and cooperating with the pressure chamber 32b 1 chamber unit 44b 1 with its separating piston 50b 1, the composite chamber unit 72b '.
  • Each of the chamber units 44b, 46b, 44b ', 46b 1 interacts with the associated pressure chamber via a respective connecting chamber 60b, 58b, 60b 1 , 58b 1 and via the openings 68b, 66b, 68b formed in the housing area 48b or also in the second chamber housing 24b ', 66b 1 together.
  • These connecting chambers are again in the housing area 48b and close in the circumferential direction of the volume 70b or 70b 'closed off by the respective separating pistons 52b, 50b, 52b', 50b '.
  • stop elements 64b, 62b, 64b 1 , 62b' designed for the separating pistons 52b, 50b, 52b ', 50b 1, for example in the form of securing rings, are provided.
  • Connecting chambers 60b, 58b, 60b ', 58b 1 are filled with incompressible damper fluid and move the associated two separating piston 52b, 52b' or 50b, 50 'under compression of the contained in the volume areas 70b, 70b' compressible, such as gaseous damper fluid.
  • the effect can be used that for both relative directions of rotation, the total volume of two chamber units represented by the volume portions 70b, 70b 1, can be used for the performance of the attenuation function, which due to the relatively large volume available a much larger Variability in the adjustment of the damping characteristic, for example, by specifying the biasing pressure or the degree of filling of the volume areas 70b, 70b 1 allows with the compressible damper fluid.
  • FIGS. 7 and 8 show a further embodiment of a torsional vibration damper arrangement with separating pistons which are movable in the circumferential direction.
  • components which correspond to components described above in terms of structure and function are denoted by the same reference numeral with the addition of an appendix "c".
  • the second damper fluid chamber arrangement 42c is now arranged radially outside the first damper fluid chamber arrangement 26c.
  • the housing region 48c now lies radially outside the first chamber housing 22c and is firmly connected thereto, for example.
  • the housing portion 48c is here assembled, for example, of two halves, with the left half shown in Fig. 8 containing the two chamber units 46c and 44c 1 , which together also provide the composite chamber unit 72c.
  • the other half of the housing portion 48c contains the two chamber portions 44c and 46c ', which together form the composite chamber unit 72c'.
  • the functionality corresponds to that described above.
  • the advantage of this embodiment is that especially the radially inner space for a larger volume of the pressure chambers 30c, 32c, 30c 1 and 32c 1 can be used. Also, due to the arrangement further radially outward for the second damper fluid chamber assembly 42c, a larger overall volume can be provided.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un ensemble amortisseur de vibrations de torsion, notamment pour la chaîne cinématique d'un véhicule, cet ensemble comprenant un côté primaire (12) et un côté secondaire (18) couplé au côté primaire (12) par un ensemble de fluides amortisseurs (16) pour tourner autour d'un axe de rotation (A) et l'un par rapport à l'autre. L'ensemble de fluides amortisseurs (16) comprend un premier fluide amortisseur qui transmet un couple de rotation entre le côté primaire (12) et le côté secondaire (18) et présente une faible compressibilité dans un premier dispositif de chambre (26) de fluide amortisseur, ainsi qu'un deuxième fluide amortisseur qui présente une forte compressibilité dans un deuxième dispositif de chambre (42) de fluide amortisseur et est sollicité lorsque la pression du premier fluide amortisseur augmente dans le premier dispositif de chambre (26) de fluide amortisseur. Le deuxième dispositif de chambre (42) de fluide amortisseur comporte au moins une unité de cavité (44,46) disposée de manière radiale externe et/ou interne relativement au premier dispositif de chambre (26;26a) de fluide amortisseur. Un élément de séparation (50,52) est associé à chaque unité de cavité (44,46), cet élément séparant le premier fluide amortisseur du deuxième fluide amortisseur et pouvant se déplacer sensiblement dans le sens de l'axe de rotation (A) lorsque la pression de l'unité de cavité (44,46) varie.
PCT/EP2007/010504 2006-12-22 2007-12-04 Ensemble amortisseur de vibrations de torsion Ceased WO2008080484A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610061343 DE102006061343A1 (de) 2006-12-22 2006-12-22 Torsionsschwingungsdämpferanordnung
DE102006061343.0 2006-12-22

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WO2008080484A1 true WO2008080484A1 (fr) 2008-07-10

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CN113586665A (zh) * 2020-04-30 2021-11-02 采埃孚股份公司 用于机动车辆动力传动系的减振器组件和变速器

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DE102008047302A1 (de) * 2008-09-16 2010-04-15 Zf Friedrichshafen Ag Torsionsschwingungsdämpferanordnung
DE102008050054A1 (de) * 2008-10-01 2010-04-08 Zf Friedrichshafen Ag Hybridantriebssystem
US10843558B2 (en) * 2016-01-28 2020-11-24 Parker-Hannifin Corporation Viscous coupling and power take off assembly for a drive train system

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DE19626729A1 (de) * 1996-07-03 1998-01-15 Mtu Friedrichshafen Gmbh Rotierende drehschwingungsdämpfende Kraftübertragungseinrichtung
DE10057822A1 (de) * 2000-11-21 2002-06-06 Freudenberg Carl Kg Drehelastische Kupplung
DE10059226C1 (de) * 2000-11-29 2002-03-07 Freudenberg Carl Kg Dämpfungseinrichtung für eine drehelastische Kupplung
DE10064332C1 (de) * 2000-12-21 2002-03-14 Freudenberg Carl Kg Dämpfungseinrichtung für eine drehelastische Kupplung
EP1715216A2 (fr) * 2005-04-23 2006-10-25 Zf Friedrichshafen Ag Amortisseur de vibrations torsionelles
EP1734279A2 (fr) * 2005-06-16 2006-12-20 MAN Nutzfahrzeuge Aktiengesellschaft Amortisseur d'oscillations de torsion
DE102005058531A1 (de) 2005-12-08 2007-06-14 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
WO2007065569A1 (fr) * 2005-12-08 2007-06-14 Zf Friedrichshafen Ag Amortisseur d'oscillations de torsion

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CN113586665A (zh) * 2020-04-30 2021-11-02 采埃孚股份公司 用于机动车辆动力传动系的减振器组件和变速器

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