WO2009062868A1 - Ensemble amortisseur de vibrations de torsion - Google Patents

Ensemble amortisseur de vibrations de torsion Download PDF

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Publication number
WO2009062868A1
WO2009062868A1 PCT/EP2008/064974 EP2008064974W WO2009062868A1 WO 2009062868 A1 WO2009062868 A1 WO 2009062868A1 EP 2008064974 W EP2008064974 W EP 2008064974W WO 2009062868 A1 WO2009062868 A1 WO 2009062868A1
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WO
WIPO (PCT)
Prior art keywords
fluid
displacement
assembly
damper
chamber
Prior art date
Application number
PCT/EP2008/064974
Other languages
German (de)
English (en)
Inventor
Cora Carlson
Thomas Dögel
Ingrid Hoffelner
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 WO2009062868A1 publication Critical patent/WO2009062868A1/fr

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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
    • F16F15/162—Suppression of vibrations in rotating systems by making use of members moving with the system using a fluid or pasty material with forced fluid circulation

Definitions

  • the present invention relates to a torsional vibration damper assembly comprising a primary side and a secondary side rotatable against the action of a damper fluid assembly about an axis of rotation relative to the primary side, the damper fluid assembly comprising two sets of displacement chambers filled with first damper fluid of lower compressibility, each having at least one displacement chamber and Assignment thereto comprises at least one compensation chamber filled with a second damper fluid of higher compressibility, wherein upon rotation of the primary side with respect to the secondary side, first damper fluid is displaced from the at least one displacement chamber of one of the groups, thereby compressing the second damper fluid in at least one compensation chamber, wherein the displacement chambers are compressed by one primary-side displacement chamber assembly and a secondary-side displacement chamber assembly are limited and wherein one of the displacement chamber a structural unit with a rotating part of a rotary feedthrough forms, through which rotary feedthrough via a first fluid port in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first
  • Such torsional vibration damper arrangements which are also generally known as a gas spring dual mass flywheel, are of comparatively complex construction, in particular, since the possibility must be provided of supplying the displacement chambers with first damper fluid via a rotary feedthrough or of delivering first damper fluid therefrom , It is to Make sure that the structural design is such that the torques to be transmitted can also be transmitted without mechanical overloading of the various components. At the same time, care must be taken to minimize as far as possible operational damage caused by any pressure fluid leakages.
  • a torsional vibration damper assembly comprising a primary side and a secondary side rotatable against the action of a damper fluid assembly about an axis of rotation with respect to the primary side, the damper fluid assembly having at least two groups of positive displacement chambers filled with first damper fluid of lower compressibility a compensation chamber and associated therewith at least one equalization chamber filled with second damper fluid of higher compressibility, upon rotation of the primary side relative to the secondary side first damper fluid is displaced from the at least one displacement chamber of one of the groups and thereby the second damper fluid is compressed in at least one compensation chamber wherein the displacement chambers by a primary-side displacement chamber assembly and a secondary-side displacement chamber assembly be and wherein one of the displacement chamber assemblies forms a structural unit with a rotating part of a rotary feedthrough, through which rotary feedthrough can be conducted via a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of
  • a connection between the fluid channels and the fluid connections provided in the non-rotating part of the rotary union can be realized in a simple manner by providing at least one connection opening between the first fluid connection and the first fluid channel and at least one in the axial region of the fluid connections in the rotating part of the rotary union a connection opening is provided between the second fluid port and the second fluid passage.
  • the second fluid channel may be arranged at least partially surrounding the first fluid channel, wherein then preferably the first fluid channel comprises at least one substantially axially, preferably coaxially to the axis of rotation, in the insert part extending opening.
  • a connection between the first fluid channel and the associated fluid connection possibly via one or more connection openings, can then be realized in a simple manner in that the first fluid channel is open in the axial region of the first fluid connection to the axial opening in the structural unit ,
  • the second fluid channel can in a simple manner between an outer peripheral surface of the insert part and an inner peripheral surface of the structural unit be formed, so an inner peripheral surface which limits the axial opening in the assembly.
  • connection of the displacement chambers to the fluid channels assigned thereto can be realized, for example, by providing at least one connection opening between the latter and the first fluid channel in association with each displacement chamber of the first group and that in association with each displacement chamber of the second group at least one connection opening between the latter and the second fluid channel is provided in the structural unit, it being furthermore advantageously possible to provide at least one opening in the insert part open to the axially extending opening in the insert part and at the end of the insert part located in the axial region of the displacement chambers at least one displacement chamber of the first group associated with at least one connection opening in the assembly communicating connection opening is provided.
  • the insert be attached to the structural unit in its end region located in the region of the displacement chambers is determined by material connection. In this way, not only a fluid density, but especially under the prevailing high pressures of up to 70 bar stable connection is created. The above-mentioned high pressures can lead to a comparatively strong axial load of the insert part when its loaded in the two axial directions surfaces are different.
  • first fluid channel and associated fluid flow areas in the insert part and / or the second fluid channel are bounded in a first axial direction by a first end face of the insert part and in a second axial direction by a second end face of the insert part Insert part are limited and that the size of the first end surface substantially equal to the size of the second end surface.
  • a torsional vibration damper arrangement comprising a primary side and a secondary side rotatable against the action of a damper fluid arrangement about an axis of rotation with respect to the primary side
  • the damper fluid arrangement comprising two groups of compressibility filled with first damper fluid Displacement chambers each having at least one displacement chamber and associated therewith at least one second damper fluid higher compressibility filled compensation chamber comprises, is displaced upon rotation of the primary side relative to the secondary side first damper fluid from the at least one displacement chamber of the groups and thereby the second damper fluid in at least one compensation chamber is compressed, wherein the displacement chambers by a primary-side displacement chamber assembly and a secondary-side displacement wherein one of the displacement chamber assemblies forms a structural unit with a rotating part of a rotary feedthrough through which rotary feedthrough via a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first group of displacement chambers is
  • a sufficient fluid exchange between the displacement chambers and the fluid connections is made possible, namely via a plurality of openings which, as the second fluid channel, realize a connection between displacement chambers of one of the groups and the associated fluid connection.
  • a connection of these openings to the associated fluid connection or the associated displacement chambers can take place in that each opening is open in its lying in the axial region of the second fluid port end region via at least one connection opening to the second fluid port and in its lying in the axial region of the displacement chambers end is open via at least one connection opening to the at least one displacement chamber of the second group.
  • a substantially axially extending fluid channel be provided in the structural unit between the axial region of the displacement chambers and the axial region of the first fluid connection.
  • This fluid channel may be substantially coaxial with the axis of rotation.
  • a plurality of openings is provided, wel che are radially offset to the axis of rotation and have an angular distance from each other and provide the fluid channel.
  • W2 3607n2, where n2 is the number of openings.
  • the arrangement is preferably such that openings of the fluid channel and openings forming the second fluid channel in the circumferential direction alternate with one another, wherein a very stable and imbalance-avoiding arrangement can then be ensured by the angular distances between openings that follow one another in the circumferential direction are the same size.
  • connection to the fluid connection or the associated displacement chambers in that the fluid channel is open in its axial region of the second fluid connection via at least one connection opening to the first fluid connection and its axial region Displacement chambers lying end region via at least one connection opening to at least one connection chamber of the first group is open.
  • a torsional vibration damper arrangement comprising a primary side and a secondary side rotatable against the action of a damper fluid arrangement about an axis of rotation relative to the primary side
  • the damper fluid arrangement comprising two groups of displacement chambers filled with first damper fluid of lower compressibility at least one displacement chamber and in association with at least one second damper fluid higher compressibility filled compensating chamber comprises, wherein upon rotation of the primary side relative to the secondary side first damper fluid from the at least one displacement chamber of one of the groups is displaced and thereby compresses the second damper fluid in at least one compensation chamber becomes, whereby the Displacement chambers are limited by a primary-side displacement chamber assembly and a secondary-side displacement chamber assembly and wherein one of the displacement chamber assemblies forms a unit with a rotating part of a rotary union through which rotary leadthrough via a first fluid port in a non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber the first
  • connection openings there is a circumferential offset between two axially successive connection openings. This makes it possible to keep the axial distance of the connection openings very small, so basically also the rotary feedthrough axially short design, while still providing sufficient stability.
  • a torsional vibration damper arrangement comprising a primary side and a secondary side rotatable against the action of a damper fluid arrangement about an axis of rotation with respect to the primary side
  • the damper fluid arrangement comprising two groups of compressibility filled with first damper fluid Displacement chambers each having at least one displacement chamber and associated therewith at least one second damper fluid higher compressibility filled compensation chamber
  • the displacement chambers are delimited by a primary-side displacement chamber assembly and a secondary-side displacement chamber assembly and wherein one of the displacement chamber assemblies forms a unit with a rotating part of a rotary union through which rotary leadthrough via a first fluid port in a non-rotating part of the rotary union first damper fluid from and to the at least one displacement chamber of a first group of displacement
  • this insert sleeve By providing an insert sleeve in the non-rotating part of the rotary feedthrough, it is possible on the one hand to intercept the mechanical stress occurring due to mutual friction by using very stable, for example hardened, material for the insert sleeve.
  • this insert sleeve to be regarded as part of the non-rotating part of the rotary feedthrough can very easily be provided with a wide variety of surface geometries or structuring in order to provide different flow paths for the first damper fluid in the non-rotating part of the rotary feedthrough.
  • a circumferential groove is provided into which at least one connection opening of a fluid connection or a connection opening opens.
  • a torsional vibration damper arrangement comprising a primary side and a secondary side rotatable against the action of a damper fluid assembly about an axis of rotation relative to the primary side
  • the damper fluid assembly comprising two sets of displacement chambers filled with first damper fluid of lower compressibility each having at least one displacement chamber and associated therewith at least one second damper fluid
  • first damper fluid is displaced from the at least one displacement chamber of one of the groups, thereby compressing the second damper fluid in at least one compensation chamber
  • the displacement chambers are defined by a primary-side displacement chamber assembly and a secondary-side expansion chamber Displacement chamber assembly are limited and wherein one of the displacement chamber assemblies, a structural unit with a rotating part of a rotary union b through which rotary feedthrough via a first fluid connection in a non-rotatable part of the rotary feedthrough first damper fluid from and to the at least one
  • the second bearing assembly is designed as a movable bearing.
  • the bearing assemblies may be axially provided subsequent to the insert sleeve.
  • a torsional vibration damper arrangement comprising a primary side and a secondary side rotatable against the action of a damper fluid arrangement about an axis of rotation relative to the primary side
  • the damper fluid arrangement comprising two groups of displacement chambers filled with first damper fluid of lower compressibility at least one displacement chamber and in association with at least one second damper fluid higher compressibility filled compensating chamber comprises, wherein upon rotation of the primary side relative to the secondary side first damper fluid from the at least one displacement chamber of one of the groups is displaced and thereby compresses the second damper fluid in at least one compensation chamber with the displacement chambers defined by a primary-side displacement chamber assembly and a secondary-side displacement chamber assembly and wherein one of the displacement chamber assemblies forms a structural unit with a rotating part of a rotary feedthrough, through which rotary feedthrough via a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first
  • the bearing assemblies include floating bearings.
  • the end wall closer to the non-rotating part of the rotary feedthrough has a substantially cylindrical projection on which one of the bearing arrangements is radially supported.
  • Protection against undesired fluid leakage can be obtained by a fluid seal acting between the cylindrical projection and the assembly, and a drainage channel opening into the space between the fluid seal and the bearing assembly.
  • a torsional vibration damper arrangement comprising a primary side and a secondary side rotatable against the action of a damper fluid arrangement about an axis of rotation with respect to the primary side
  • the damper fluid arrangement comprising two groups of displacement chambers filled with first damper fluid of lower compressibility, each having at least one Displacement chamber and in association with at least one filled with a second damper fluid higher compressibility compensation chamber comprises, is displaced upon rotation of the primary side relative to the secondary side first damper fluid from the at least one displacement chamber of one of the groups and thereby the second damper fluid is compressed in at least one compensation chamber
  • the displacement chambers are limited by a primary-side displacement chamber assembly and a secondary-side displacement chamber assembly and wherein one of the displacement chamber assemblies forms a structural unit with a rotating part of a rotary feedthrough through which rotary feedthrough via a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of
  • the provision of different drainage channels ensures that fluid leaks that have been passed over seals can be removed in a defined manner and do not escape at an unsuitable location.
  • the first fluid seals pressure seals be, so seals that are designed to withstand very high pressures, while the second fluid seals can be flow seals, so seals that are basically designed to absorb lower pressure loads, but then can provide a very high density ,
  • a torsional vibration damper arrangement comprising a primary side and a secondary side rotatable against the action of a damper fluid arrangement about an axis of rotation with respect to the primary side, the damper fluid arrangement comprising two groups of displacement chambers filled with first damper fluid of lower compressibility, each having at least one Displacement chamber and associated therewith at least one with second damper fluid higher Kompressibili- wherein, upon rotation of the primary side relative to the secondary side, first damper fluid is displaced from the at least one displacement chamber of one of the groups thereby compressing the second damper fluid in at least one compensation chamber, the displacement chambers being delimited by a primary side displacement chamber assembly and a secondary side displacement chamber assembly and wherein one of the displacement chamber assemblies forms a structural unit with a rotating part of a rotary feedthrough, through which rotary feedthrough via a first fluid connection in a non-rotating part of the rotary feedthrough first damper fluid from and to the at least one displacement chamber of a first
  • the one of the displacement chamber assemblies and the rotating part of the rotary leadthrough may be integrally formed to provide the assembly, that is, to be realized on one and the same component, without requiring a further process of assembly. This is particularly advantageous because it avoids connection points that would have to be secured against fluid loss.
  • FIG. 1 shows a part of a known type of embodiment of an anchor string with a gas spring dual mass flywheel and a
  • Fig. 2 is a cross-sectional view of the gas spring dual mass flywheel
  • FIG. 3 shows the displacement chamber assemblies and the rotary feedthrough of an embodiment according to the invention
  • FIG. 4 shows the arrangement of FIG. 3 without the non-rotating part of the rotary leadthrough
  • FIG. 5 shows an enlarged detail view of the arrangement of FIG. 4 in an axial end region of two fluid channels
  • Fig. 7 is a cross-sectional view of the assembly of Fig. 4 taken along a line VII-VII in Fig. 4;
  • Fig. 8 is a cross-sectional view corresponding to Fig. 7, taken along a line VIII-VIII in Fig. 4;
  • FIG. 9 is a sectional view of the view shown in FIG. 3;
  • FIG. 10 shows an assembly formed from a displacement chamber assembly and the rotating part of the rotary union according to an alternative embodiment;
  • Fig. 12 is a perspective longitudinal sectional view of the Aussaysart the
  • FIG. 11 cut in a sectional plane rotated by 90 ° relative to the sectional plane of FIG. 11;
  • Fig. 13 is a cross-sectional view of the central part of the rotary feedthrough of
  • FIG. 14 is a view corresponding to FIG. 12 of an alternative embodiment
  • Fig. 15 is a cross-sectional view of the central part of the rotary feedthrough of
  • Fig. 17 is a partial longitudinal sectional view of an insert sleeve of the non-rotating part of a rotary union shown in Fig. 16;
  • 19 is a radial view of a rotary feedthrough
  • Piston seals formed sealing arrangements Fig. 21 in the representations a) to k) a plurality of seals formed on the type of rod seals.
  • the torsional vibration damper assembly 12 includes a primary side 20 which is coupled or coupleable to the drive shaft 16 via a flexplate assembly 22 or the like for common rotation about the axis of rotation A.
  • This primary side 20 in turn comprises a first displacement chamber assembly 24 which, with two end walls 26, 28 and an outer peripheral wall 30, defines a plurality of circumferentially successive displacement chambers 32, 33 axially and radially outwardly.
  • a star-shaped arrangement of compensating cylinders 34 is provided with respect to the axis A, in each of which a compensation chamber 36 is formed.
  • each displacement chamber 32, 33 is associated with a compensation chamber 36, or that a displacement chamber 32, 33 are associated with a plurality of compensation chambers 36, or that a compensation chamber 36 with a plurality of displacement chambers 32, 33 cooperates.
  • This interaction takes place via a through opening 38 provided in association with each displacement chamber 32, 33 in the outer peripheral wall 30 and a connecting chamber 40 extending in the circumferential direction along the outer peripheral wall 28.
  • a respective separating piston 42 which is movable in the compensating cylinder 34 separates this into the displacement chamber (s) 32, 33 contained first damper fluid, which is substantially non-compressible and may be, for example, oil from the second damper fluid contained in the associated compensation chamber 36 which is compressible, for example, air or other gas may be.
  • first damper fluid which is substantially non-compressible and may be, for example, oil from the second damper fluid contained in the associated compensation chamber 36 which is compressible, for example, air or other gas may be.
  • a secondary side 44 of the torsional vibration damper assembly 12 includes a second displacement chamber assembly 46 rotatably supported by a bearing 48 on the first displacement chamber assembly 24.
  • the second displacement chamber assembly 46 delimits the displacement chambers 32 after dial inside and is guided via corresponding sealing arrangements with respect to the side walls 26, 28 fluid-tight.
  • circumferentially extending projections 60, 62 are provided on the two displacement chamber assemblies 24, 46, respectively, so that each displacement chamber 32 is defined by a peripheral boundary projection 60 of the primary side first displacement chamber assembly 24 is limited and a peripheral limiting projection 62 of the secondary-side second displacement chamber assembly 46 is limited.
  • the two displacement chamber assemblies 24, 46 can limit a plurality, for example four circumferentially successive displacement chambers, of which two act in parallel, so reduced or increased in volume at the same time.
  • first damper fluid in the displacement chambers 32, 33, these can be supplied to or removed from the first damper fluid via channels 49, 50 which can be seen in FIGS.
  • This purpose is further served by a rotary feedthrough, generally designated 52, the rotating part 54 of which is in communication with the second displacement chamber assembly 46 and whose non-rotating part 56 is in communication with a source of pressurized fluid for first damper fluid or a reservoir.
  • the rotating part 54 of the rotary feedthrough 52 is connected to a friction clutch 58, which is shown by way of example here as a separating / starting element, for common rotation.
  • a friction clutch 58 which is shown by way of example here as a separating / starting element, for common rotation.
  • the rotating part 54 and the friction clutch 58 in their axially opposite areas a toothing, for example in the manner of a Hirth toothing.
  • a clamping sleeve 66 which engages radially inwards through the friction clutch 58 together with a fastening bolt 68 screwed into the rotating part 54 of the rotary leadthrough 52 holds the friction clutch 58 in rotationally fixed engagement with the rotating part 54.
  • FIG. 3 shows in enlarged form the rotary leadthrough 52 and the two displacement chamber assemblies 24, 46 of the torsional vibration damper arrangement 12.
  • FIG. 3 clearly shows that the second displacement chamber assembly 46 and the rotating part 54 of the rotary leadthrough are integrally formed, ie an integral structural unit 70 form.
  • a axial opening 72 which is coaxial to the axis of rotation A and is located to one on the left in FIG. 3, that is to say the motor-side end of this structural unit 70, is provided.
  • an insert 74 is inserted in this axial opening 72.
  • This insert member 74 also has a preferably coaxial to the axis of rotation A and axially extending opening 76.
  • An end portion 80 of the insert 74 proximate the closed end portion 78 of the aperture 72 in the assembly 70 terminates axially spaced from a bottom portion 82 of the aperture 72.
  • the axial aperture 76 in the insert member 74 is thus open to the axial aperture 72 in the assembly 70 , with axial distance to the bottom portion 82nd
  • a plurality of connecting openings 84 which follow one another in a circumferential direction, preferably open, which pass through the rotating part 54 or the structural unit 70 substantially radially.
  • connection openings 84 Through these connection openings 84, a connection is created between the opening 72 in the assembly 70 and the axial opening 76 in the insert part 74, which provides a first fluid channel 86.
  • a first fluid connection 88 which in the illustrated example comprises a connection opening 90, is in the non-rotating part 56 of the rotary feedthrough 52 is formed and communicates via the connection openings 84 in communication with the first fluid channel 86th
  • connection openings 94 open into the first fluid channel 86.
  • the insert part 74 is widened like a disk in this axial end region 92 and inserted into a correspondingly enlarged region of the second displacement chamber assembly 46.
  • a radially outwardly open circumferential groove 98 is provided, into which the three connection openings 94 open. As shown in FIG.
  • connection openings 100 are provided, which are open radially inwards to the circumferential groove 98 and via these in communication with the connection openings 94 and thus the first fluid channel 86 , Radially outward, the two connection openings 100 are open to the respectively mutually associated displacement chambers, for example the displacement chambers 32 shown in FIG. 2, which are considered here as a first group 102 of displacement chambers.
  • these two displacement chambers 32 of the first group 102 are via the connection openings 100, the annular groove 98, the connection openings 94, the first fluid channel 86, ie the axial opening 76 in the insert part 74, and the connection openings 84 in the rotating Part 54 of the pressure passage 52 in connection with the connection opening 90 of the first fluid connection 88.
  • this connection with a source of pressurized first damper fluid or a reservoir for this first damper fluid is brought into connection, thus the fluid pressure or The amount of fluid in the displacement chambers 32 of the first group 102 can be increased or reduced accordingly.
  • a second fluid channel 104 is delimited between an outer surface 106 of the insert 74 and an inner peripheral surface 108 of the module 70.
  • the second fluid channel 104 extends close to the axial end region 80 of the insert part 74 up to an axial region of a second fluid connection 110 which can be seen in FIG. 3 in the non-rotating part 56 of the rotary leadthrough 52.
  • this second fluid connection 10 comprises illustrated example, a connection opening 1 12th
  • a pressurized fluid connection between the second fluid channel 104 and the first fluid channel 86 or between the insert 74 and the bottom 82 of the axial opening 72 formed To prevent room area lies in the end region 80 of the insert 74 on the inner surface 108 of the assembly 70 at.
  • the insert part 74 is radially expanded somewhat in comparison to the region in which it also delimits the second fluid channel 104.
  • an example formed as an O-ring sealing element 1 16 is provided in a radially outwardly open groove of the insert part 74.
  • the axial opening 72 in the assembly 70 or its area lying in the rotating part 54 in the region of a slope 1 18 is tapered.
  • This bevel 1 18 allows insertion of the already equipped with the sealing element 1 16 insert part 74 without the sealing element 1 16 is damaged at a sharp-edged step.
  • the second fluid channel 104 is axially delimited by the disk-like widening 96 of the insert part 74.
  • This widening 96 bears on an axial end face 120 in a circumferential groove a sealing element 122 which is located on an opposite end End surface 124 of the second displacement chamber assembly 46, the second fluid channel 104 tightly abuts.
  • connection openings 126 are provided in the region of the axial end of the second fluid channel 104 in the second displacement chamber assembly 46. These lead radially outward from the second fluid channel 104 to the two other displacement chambers 33, which form a second group 128 of displacement chambers here. These two displacement chambers 33 of the second group 128 are thus in fluid communication with the connection opening 12 of the second fluid connection 10 via the two connection openings 26, the second fluid channel 104 and the connection openings 114. Also, depending on whether this second Fluid port 1 10 in conjunction with a source of pressurized first damper fluid or a reservoir for it, the fluid pressure or the amount of fluid in these displacement chambers 33 is increased or decreased.
  • a fixed support of the insert 74 in the assembly 70 is obtained in the region of the disk-like extension 96.
  • a firm connection can be made by welding, which at the same time also produces a fluid-tight seal, in particular for the annular groove 98.
  • This region 130 is accessible from the axially open end of the axial opening 72 which widens stepwise in the structural unit 70.
  • step-like extension 134 is then provided, for example, designed as a Loselager bearing 48 which radi al inside an axial projection 136 on the end wall 26, ie the first displacement chamber assembly 24 leads or centered.
  • This bearing 48 may be inserted before or after the insert 74 is disposed in the axial opening 72, held therein initially under axial pressure, and then secured by welding.
  • the inner diameter of the bearing 48 may be greater than the disk-like extension 96 of the insert 74, but may also be sized smaller, especially if this bearing 48 is introduced after the insert 74 has been fixed to the assembly 70.
  • connection openings 84 and 100 provided in association with the first fluid channel 86 or the connection openings 1 14, 126 provided in association with the second fluid channel 104 may be provided in the structural unit 70 before the insert 74 is inserted into it.
  • Der Fluid pressure acting on these two surfaces 138, 140 loads the insert 74 in the direction of the opening 72.
  • a fluid pressure acting on an end face 142 at the radial extension of the insert 74 loads the insert in the opposite direction.
  • at least a slight compensation takes place, so that the total of the insert member 74 in the direction of the engine, so out of the opening 72 loading force does not lead to an overload of the material connection of the insert 74 with the building unit 74.
  • the connecting openings 84 and 11 are rotating on both sides Part 54 in corresponding radially outwardly open circumferential grooves 144 sealing elements 146 used.
  • These sealing elements 146 which are designed, for example, as pressure seals, lie radially outward against an inner surface of the non-rotating part 56 of the rotary feedthrough, which is provided here by an insert sleeve 148.
  • This insert sleeve 148 points in the axial region of the fluid connections 88, 110 in FIG 16 also visible radially inwardly open circumferential grooves 150, 152, to which the connection openings 84 and 1 14 are radially open. As shown in FIG. 17, these circumferential grooves 150, 152 may be provided in the insert sleeve 148 at its two flanks with inclined surfaces 154, which avoid damage to the sealing elements 146 at sharp-edged steps when inserting the rotating member 54 into the insert sleeve 148.
  • a passage opening 156 or 158 is formed in the insert sleeve 148, which has a connection between the respective connection opening 90 or 1 12 and the associated circumferential groove 150, 152 manufactures.
  • a bearing 158 or 160 is provided in each case.
  • the left in particular in the illustration of FIG. 16, ie motor side recognizable bearing 160 is designed as a floating bearing.
  • the lying on the other axial side bearing 158 is designed as a fixed bearing, so for example conventional ball bearings.
  • this bearing 158 is axially fixed by a securing ring 162 on the one hand and a radial shoulder 164 on the other hand.
  • this bearing is axially fixed by a radial shoulder 166 and a disk-like closing element 168 bolted to the non-rotating part 56.
  • a defined positioning of the non-rotating part 56 of the rotary feedthrough 52 with respect to the rotating part 54 and thus of the assembly 70 is predefined via this bearing 158.
  • bearing 170 is the primary side 20 and the end wall 28 of the same radially supported on the assembly 70.
  • the end wall 28 has an annular axial extension 172, which surrounds the bearing 170 radially on the outside.
  • This bearing 170 which is positioned axially next to the already mentioned bearing 160, is supported on the outer periphery of the assembly 70. Since none of the further bearings 48, 160, 170 is designed as a fixed bearing except for the bearing 158, these other bearings 48, 160, 170 are all designed as floating bearings, for example needle bearings or the like, there is no overdetermination in the axial positioning of the Assembly unit 70 and also the primary side 20 and the non-rotating part 56 of the rotary leadthrough 52.
  • sealing elements 174, 176 are provided at the two axial ends of the non-rotating part 56 of the rotary feedthrough 52.
  • the sealing element 174 is provided substantially between the closing element 168 fixed to the non-rotating part 56 and the outer periphery of the rotating part 54, such that the bearing 158 is arranged between the axially last sealing element 146 and this sealing element 174.
  • the closing element 168 is tightly sealed with respect to the non-rotating part 56 by way of another, for example, 0-shaped sealing element 178.
  • the seal member 176 is held axially between the non-rotating part 56 and a further disk-like launching member 180 fixed thereto and bears radially against the annular cylindrical projection 172 of the end wall 28.
  • the bearing 160 is located between this sealing element 176 and the next axially following the sealing elements 146th
  • the sealing elements 146 are essentially designed as pressure seals
  • the sealing elements 174, 176 are essentially designed as volume flow seals.
  • the pressure seals are designed to absorb the high pressure loads prevailing in the area of the fluid connections 88 and 110, respectively. For this purpose, they put themselves under load of the high fluid pressure against the peripheral walls of the grooves 144 supporting them. These can be provided, for example, by hard turning and subsequent axial grinding and complete firing in order to achieve an excellent sealing effect by means of appropriate surface quality.
  • the sealing elements 146 may be provided with a microstructuring which improves the hydrodynamics in the frictional contact region.
  • a drainage channel 184 also passes through the insert sleeve 148 into the region between the two sealing elements 146, which lie between the two annular grooves 150, 152 in the insert sleeve 148.
  • a drainage channel 186 leads into the axial region between the bearing 160 and the immediately following sealing element 146.
  • a drainage channel 188 leads into the region between the two bearings 160, 170, which is closed in a fluid-tight manner radially outwardly by the sealing element 176 and which further by a between the end wall 28 and the second Displacement chamber assembly 46 acting example two-stage seal assembly 188 is fluid-tight.
  • a corresponding sealing arrangement 188 can also produce a fluid-tight closure between the end wall 26 and the second displacement chamber assembly 46.
  • a drainage channel 190 leads to the axial region between the bearing 158 and the immediately following sealing element 46.
  • a drainage channel 192 leads into the region between the bearing 158 and the closure element 168, which also axially is sealed fluid-tight by the volumetric flow seal designed as a sealing element 174th
  • all of these drainage channels may be provided by bores in the non-rotating part 56 and, if necessary, the insert sleeve 148, which are guided to face between the non-rotating part 56 and a non-rotating part 56 lead the drainage port 182 providing attachment portion 194 formed space portion 196, which in turn is open to the drainage port 182.
  • the drainage port 182 may be brought into communication with a reservoir for the first damper fluid.
  • the groove 98 in the disk-like extension 96 of the insert part 74 can be dispensed with, in which case in association with each of the connection openings 100, for example, a connection opening 94 in the insert part 74 is to be provided.
  • an exact circumferential alignment must be generated, which can be done by a positioning pin is passed through the connection openings 100, 94, the insert 74 is then determined and then this pin is removed again.
  • the setting of this insert 74 can be done in addition to the already mentioned weld also by other material connection types, such as gluing, or by screwing.
  • the insert part can also be formed in several parts and joined in addition to the illustrated one-piece design.
  • the circumferential grooves 150, 152 provided there can also be provided in the outer circumference of the rotating part 54 of the rotary leadthrough 52.
  • the two fluid connections 88, 110 and their connection openings 90, 112, respectively, can be offset in relation to one another in a deviation from the illustrated axially aligned positioning in the circumferential direction. This makes it possible, while maintaining a sufficiently large wall thickness between them to realize a smaller axial distance and consequently also a smaller axial size.
  • the insert sleeve 148 can be inserted into the non-rotating part 56, for example, by pressing, wherein at its insertion preceding the end of the insert sleeve can be tapered, as can be seen for example in FIG. 17 at the left end of this insert sleeve 148.
  • the opening formed in the non-rotating part 56 and receiving sleeve 148 can be designed to widen radially at its end area.
  • the sealing elements 174, 176 provided as volumetric flow seals can be embodied as closed sealing lip geometries which rest under prestress on the rotating part 54 or the end wall 28. They can in particular also be designed as dry-running seals. In particular, where relative movements occur between different bearings or sealing elements of the components rotating with respect to one another, the surfaces involved can be reworked to provide the corresponding surface quality or the roughness requirements by Höhne or in some other way.
  • FIG. 9 shows an alternative embodiment of the mounting of the primary side 20 and the side wall 28 with respect to the assembly 70. It can be seen here that on the end wall 28 in its radially inner end region a ring-like axially engaging in a corresponding recess of the second displacement chamber assembly 46 Approach 198 is provided. Between this and an outer peripheral surface of the second displacement chamber assembly 46 or the Assembly 70 is now the bearing 170. Axially adjacent to this bearing acts between the end wall 28 and the assembly 70, a further sealing element 200 as a flow seal, in particular in order to avoid leakage of fluid from the region of the displacement chambers.
  • a further drainage channel 202 can lead axially from this region of the bearing, that is to say the region of the bearing 170, into the space between the bearing 160 and the sealing element 176, which can then be emptied via the drainage channel 188 which can be seen in FIG.
  • FIG. 1 An alternative embodiment of the insert 74 is shown in FIG.
  • the structural unit 70 with the axial opening 72 formed therein can be seen.
  • the insertion part 74 is now axially closed and this end area 80 lies on the right side of the connection openings 84 in the illustration of FIG
  • corresponding connection openings 204 are formed in the axial region of the connection openings 84 in the insert part 74.
  • sealing element 206 for example O-ring-like, which has the function of allowing essentially no first damper fluid to reach the region between the axial end region 80 and the bottom wall 82 .
  • the sealing element 206 which overcomes the first damper fluid, can be directed out of this volume area via a drainage channel 208 toward one of the drainage channels in the non-rotating part 56, which are clearly visible in FIG. 3 and also in FIG. 16. In this manner, a pressure of the first damper fluid which axially loads the insert 74 is avoided.
  • the first fluid channel 86 can be closed by a closure element 210 terminating the axial opening 76 in the insert part 74.
  • a significant advantage of this embodiment is that the various axially loaded by the first damper fluid surfaces of the insert part 74 in Both axial directions are substantially equal. That is, the end face loaded in an axial direction which is formed of all the faces loaded in this direction, and the end face loaded in the other axial direction which is formed of all the surfaces or faces in FIG are loaded in the other axial direction, compensate each other substantially, so that substantially no forces acting on the insert 74 forces occur, which relieves mainly the area in which the insert member 74 is fixedly connected to the second displacement chamber assembly 46.
  • connection openings 84 and 204 are aligned with each other in the direction of the circumference, it is possible to proceed in such a way that these openings are drilled only after insertion of the insert part 74, wherein drilling residues have to be removed during and after the drilling process.
  • the holes or openings may be previously provided, and by then inserted into these plugs or pins, the correct alignment can be obtained prior to the solid connection of the insert 74 with the assembly 70.
  • the assembly 70 is formed by an integral assembly of the second displacement chamber assembly 46 and the rotating portion 54 of the rotary union 52.
  • the first fluid channel 86 which connects between the fluid connection 88 or the connection opening 90 of the same and the displacement Chambers 32 of the first group 102 is formed here with two substantially parallel and axially extending openings 212 and 214. These extend from a rotating part 54 radially completely passing through the connection opening 84 which radially outward to the circumferential groove 150 in the insert sleeve 148 is open until the other axial end of the assembly 70 and there are sealed by tight closing insert elements 216, 218, for example Königsexpander or the like., Close.
  • connection opening 220, 222 opens out radially from each of the openings 212, 214, which opens into one of the displacement chambers 32.
  • the second connecting channel 104 is, as shown in FIG. 12, also provided by two substantially axially extending openings 224, 226 in the assembly 70. These go out axially from a connection opening 1 14 in the axial region of the second fluid port 1 12, which radially completely passes through the rotating part 54 and opens into the circumferential groove 152 of the insert part 148. In their other axial end region, the openings 224, 226 are again closed fluid-tightly by closing elements 228, 230, for example likewise Königsexpander, or the like.
  • connection openings 232, 234 extend radially outward and thus establish a connection of the openings 224, 226 with the displacement chambers 33 of the second group 128.
  • the four axial openings 212, 214, 224, 226 are distributed uniformly about the axis of rotation A, ie they have substantially the same radial distance to this and have an angular spacing from one another about 90 ° in each case based on their longitudinal center line, on.
  • an axial opening of the first fluid channel 86 follows an axial opening of the second fluid channel 104, so that overall the axial openings forming the same fluid channel have an angular spacing of approximately 180 ° relative to each other.
  • FIGS. 14 and 15 A modification of this design principle is shown in FIGS. 14 and 15. It can be seen in particular in Fig.
  • connection openings 1 14 again in communication with the second fluid port 1 12. All these axial openings In the center, ie, for example, formed coaxially to the axis of rotation, again the axial opening 76, which forms the first fluid channel 86 and is open in its gethebe content axial end via connection openings 84 radially outward to the first fluid port 88. In its motor-side end, the first fluid channel 86 opens into a chamber 240 which is closed by a closure element 242 which is fixed as a screw plug, as a king expander or as a material-fit connection such as welding or gluing.
  • the four axially extending openings 224, 226, 236, 238 of the second fluid channel 104 are again closed at their motor-side axial end by closure elements, for example Königsexpander or the like., Of which in Fig. 14, the elements 228, 230 of the openings 224 , 226 are shown.
  • the openings 224, 226, 236, 238 of the second fluid channel 104 are connected via connecting openings, which are then not visible in FIG. 14, in a substantially radially extending connection in connection with the displacement chambers 33 of the second group 128, wherein, for example, that each two of the axial openings 224, 226, 236, 238 lead to one of the connecting chamber.
  • FIGS. 18 and 19 essentially show the non-rotating part 56 of the rotary leadthrough 52 with the fluid connections 88, 112 and the drainage connection 182 provided thereon.
  • These 12, 182 sensors 244, 246, 248 are associated with these various ports 88, 112, and 182.
  • These sensors can be designed to control the pressure in the various openings or Capture conclusions or alternatively or additionally to detect the flow of the medium flowing through a respective opening. It goes without saying that such sensors do not have to be provided in association with all connections or that different types of sensors can be provided in association with different connections.
  • a pressure sensor can be provided in each case in association with the two fluid connections 88, 112, while a volume flow sensor can be provided in association with the drainage connection 182.
  • FIGS. 20 and 21 Various types of sealing elements are shown in FIGS. 20 and 21 which may act, for example, to establish a tight seal between the rotating part 54 of the rotary union 52 and the insert 74. It should be pointed out that such sealing elements, which may in principle have a multi-part construction, can of course also act in other regions of the torsional vibration damper arrangement 12 described in detail above, for example also as the sealing elements 146.
  • FIG. 20 shows a wide variety of variants of such sealing elements, for example, for the sealing element 1 16, which has already been explained above, which are designed as so-called piston seals. That is to say, the sealing element 16 itself is arranged in the region of the insert part 74 or a circumferential countersink 250 provided therein.
  • these sealing elements act with an elastically effective biasing element 252, which is supported with respect to the insert part 74 and biases a generally ring-like sealing body 254 against the inner surface of the non-rotating part 54.
  • the biasing member 252 may be formed, for example, as a metal or rubber spring, and the sealing body may or the like as a plastic sealing ring. be educated.
  • sealing elements 1 16 may also be constructed so that, as shown for example in FIG. 2Of recognizable, even the prevailing pressure of the fluid generates a load of the sealing body 254 against the surface to be contacted by this.
  • FIG. 21 The design variants shown in FIG. 21 are designed in the manner of so-called rod seals.
  • a circumferential recess 250 is provided in the non-rotating part 54 and thus also the sealing element, for example, the sealing element 1 16, provided on this non-rotating part 54.
  • An elastic biasing element, for example, again metal or rubber spring 252 then loads an annular sealing body 254 against the outer peripheral surface of the insert 74.
  • the same construction variants can be used, as can also be seen in Fig. 20.

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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)
  • Fluid-Damping Devices (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

L'invention concerne un ensemble amortisseur de vibrations de torsion, comprenant un côté primaire (20) et un côté secondaire (44) rotatif autour d'un axe de rotation (A) par rapport au côté primaire (20) contre l'action d'un ensemble à fluide amortisseur. Selon l'invention, l'ensemble à fluide amortisseur comprend deux groupes de chambres de refoulement (32) remplies d'un premier fluide amortisseur de compressibilité inférieure, chaque groupe comprenant au moins une chambre de refoulement (32) et, en association avec cette chambre, au moins une chambre de compensation (36) remplie d'un deuxième fluide amortisseur de compressibilité supérieure; lors de la rotation du côté primaire (20) par rapport au côté secondaire (44), le premier fluide amortisseur est refoulé hors de la ou des chambres de refoulement (32) d'un des groupes, de manière à comprimer le deuxième fluide amortisseur dans au moins une chambre de compensation (36); les chambres de refoulement (32) sont délimitées par un sous-ensemble de chambre de refoulement (24) du côté primaire et un sous-ensemble de chambre de refoulement (46) du côté secondaire; un des sous-ensembles de chambre de refoulement (24, 46) forme une unité de construction avec une partie rotative (54) d'un passage tournant (52), passage tournant (52) par lequel, via un premier branchement de fluide (88) dans une partie non rotative (56) du passage tournant (52), le premier fluide amortisseur peut être dirigé depuis et vers la ou les chambres de refoulement (32) d'un premier groupe de chambres de refoulement, et par lequel, via un deuxième branchement de fluide (110) au moins axialement décalé par rapport au premier branchement de fluide (88) dans la partie non rotative (56) du passage tournant (52), le premier fluide d'amortissement peut être dirigé depuis et vers la ou les chambres de refoulement d'un deuxième groupe de chambres de refoulement. Une ouverture axiale (72) est prévue dans l'unité de construction (70) et une pièce d'insertion (74) est prévue dans cette ouverture (72), la pièce d'insertion (74) délimitant un premier canal de fluide (86) pour relier le premier branchement de fluide (88) à la ou les chambres de refoulement (32) du premier groupe, et un deuxième canal de fluide (104) pour relier le deuxième branchement de fluide (110) à la ou les chambres de refoulement du deuxième groupe.
PCT/EP2008/064974 2007-11-15 2008-11-05 Ensemble amortisseur de vibrations de torsion WO2009062868A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007054570.5 2007-11-15
DE200710054570 DE102007054570A1 (de) 2007-11-15 2007-11-15 Torsionsschwingungsdämpferanordnung

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DE102021100431A1 (de) 2021-01-12 2022-07-14 Hasse & Wrede Gmbh Drehschwingungsdämpfer oder Drehschwingungstilger

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005018954A1 (de) * 2005-04-23 2006-11-02 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
DE102005058531A1 (de) * 2005-12-08 2007-06-14 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
EP1914452A2 (fr) * 2006-10-17 2008-04-23 ZF Friedrichshafen AG Passage tournant, en particulier pour le conducteur de commande d'un véhicule
WO2008074397A1 (fr) * 2006-12-19 2008-06-26 Zf Friedrichshafen Ag Dispositif d'amortissement des vibrations de torsion
WO2008080485A1 (fr) * 2006-12-22 2008-07-10 Zf Friedrichshafen Ag Ensemble amortisseur de vibrations de torsion
EP1975477A1 (fr) * 2007-03-31 2008-10-01 ZF Friedrichshafen AG Passage tournant, en particulier pour un amortisseur d'oscillations de torsion dans un train d'entraînement d'un véhicule
DE102008008508A1 (de) * 2007-04-20 2008-10-23 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer für den Antriebsstrang eines Fahrzeugs
EP1998076A2 (fr) * 2007-06-01 2008-12-03 ZF Friedrichshafen AG Agencement d'amortisseur de vibrations de torsions

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005018954A1 (de) * 2005-04-23 2006-11-02 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
DE102005058531A1 (de) * 2005-12-08 2007-06-14 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer
EP1914452A2 (fr) * 2006-10-17 2008-04-23 ZF Friedrichshafen AG Passage tournant, en particulier pour le conducteur de commande d'un véhicule
WO2008074397A1 (fr) * 2006-12-19 2008-06-26 Zf Friedrichshafen Ag Dispositif d'amortissement des vibrations de torsion
WO2008080485A1 (fr) * 2006-12-22 2008-07-10 Zf Friedrichshafen Ag Ensemble amortisseur de vibrations de torsion
EP1975477A1 (fr) * 2007-03-31 2008-10-01 ZF Friedrichshafen AG Passage tournant, en particulier pour un amortisseur d'oscillations de torsion dans un train d'entraînement d'un véhicule
DE102008008508A1 (de) * 2007-04-20 2008-10-23 Zf Friedrichshafen Ag Torsionsschwingungsdämpfer für den Antriebsstrang eines Fahrzeugs
EP1998076A2 (fr) * 2007-06-01 2008-12-03 ZF Friedrichshafen AG Agencement d'amortisseur de vibrations de torsions

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