EP3137787A1 - Unité d'amortissement de vibrations - Google Patents

Unité d'amortissement de vibrations

Info

Publication number
EP3137787A1
EP3137787A1 EP15712641.8A EP15712641A EP3137787A1 EP 3137787 A1 EP3137787 A1 EP 3137787A1 EP 15712641 A EP15712641 A EP 15712641A EP 3137787 A1 EP3137787 A1 EP 3137787A1
Authority
EP
European Patent Office
Prior art keywords
vibration damper
damper unit
sealing membrane
guide structure
membrane
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.)
Withdrawn
Application number
EP15712641.8A
Other languages
German (de)
English (en)
Inventor
Alexander Manger
Bernhard Schierling
Christoph Fauss
Michael Traut
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 EP3137787A1 publication Critical patent/EP3137787A1/fr
Withdrawn legal-status Critical Current

Links

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
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range
    • 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
    • F16F15/165—Sealing arrangements

Definitions

  • Embodiments relate to a vibration damper unit, which can be used for example in the context of a drive train of a motor vehicle, for example a motor vehicle with an internal combustion engine.
  • damper assemblies or vibration damper units are used, which are used for damping at least one vibration component of a rotational movement and optionally for transmitting a torque of the rotary motion.
  • corresponding damper arrangements are used for example in the field of vehicle construction in the context of powertrains of motor vehicles, in which it may come to deviations from a uniform or uniform rotational movement, for example, conceptually.
  • damper assemblies are used there.
  • vibration damper units are described, for example, in DE 10 201 1 086 927 A1, which comprise a torsion damper and also a damper vibration damper which has at least one damper mass and at least one guide structure. About at least one sealing device, the spring elements and the at least one absorber mass are sealed on an output side of the torsion damper to a clutch and to a transmission.
  • the fundamental challenge of realizing an attenuation of at least one oscillation component of a rotary movement is often accompanied by a multiplicity of further boundary conditions with regard to construction, function and other parameters. For example, there is a need to improve a trade-off between packaging space, friction that occurs, ease of manufacture, and improved performance in an operation of a vibration damper unit.
  • a vibration damper unit for example for a drive train of a motor vehicle, comprises a torsion damper having at least one primary side and at least one secondary side, between which at least one spring element is coupled in such a way that torque is transmitted from the primary side to the secondary side via the at least one spring element ,
  • the at least one spring element is arranged in a spring region, which comprises a lubricant during the operation of the vibration damper unit.
  • the vibration damper unit further comprises a damper vibration damper comprising at least one damper mass and at least one guide structure, wherein the guide structure is adapted to movably guide the at least one damper mass to damp a vibration component of a rotary motion.
  • a lubricant may be a medium that may enhance a function of the torsion damper or spring elements, such as a liquid, paste, grease, lubricating fluid, or other lubricating medium.
  • the lubricant may in some cases only be introduced during assembly or during operation in the vibration damper unit.
  • the sealing membrane is supported on the guide structure and the cover member in an axial direction. In some embodiments, it can thus be made possible that an axial force curve from the guide structure to the cover component takes place at least partially over the sealing membrane. Thus, if necessary, other components for transmitting the axial force can be reduced or even completely eliminated.
  • the cover member is part of a housing of the vibration damper unit.
  • the spring region in which the spring element is received can thus be formed or limited in a simple manner. If necessary, the cover component can be fastened to another housing component, for example welded to it.
  • the sealing membrane is additionally or alternatively attached to the guide structure of the Tilgerschwingungsdämpfers. In some embodiments, positioning of the sealing membrane, at least in a circumferential direction and / or a radial direction, can thus be made possible in a simple manner.
  • the sealing membrane may comprise at least a first partial membrane and a second partial membrane. In some embodiments, such a simple assembly of the sealing membrane can be made possible.
  • the first partial membrane may be arranged on an axially opposite side to the second partial membrane.
  • the guide structure and the absorber masses are arranged in the axial direction between the two partial membranes.
  • the second sub-membrane may have a support area which is supported against the cover component.
  • such an Axialkraftverlauf can be effected by the guide structure on the second part of the membrane to the cover member.
  • the support region can also be formed on the first part membrane.
  • the second sub-membrane has an overlap portion that overlaps with an overlap portion of the first sub-membrane.
  • the sealing membrane is indeed formed in several parts, but nevertheless in a region in which the two sub-membranes adjoin one another, form a closed or even tight envelope.
  • at least one of the overlap sections extends at least partially or substantially in an axial direction.
  • the overlapping sections may then overlap in the axial direction.
  • the overlapping sections can also extend at an angle to the axial direction, that is to say be conical, for example.
  • the sealing membrane can be supported radially within the at least one absorber mass on the guide structure.
  • the sealing membrane is arranged and / or fixed with a sufficient distance in the axial direction to the absorber masses.
  • touching, grinding and / or contact of the absorber masses on the sealing membrane can at least be reduced or even prevented.
  • the at least one absorber mass is arranged in the axial direction between at least a first and a second guide structure.
  • the sealing membrane may be secured to at least one of the guide structures with a fastener interconnecting the first and second guide structures. In some embodiments, so further components or fasteners for fixing or securing the sealing membrane may be reduced or even completely eliminated.
  • Exemplary embodiments according to a further aspect relate to a vibration damper unit, for example for a drive train of a motor vehicle, having a torsion damper which has at least one primary side and at least one secondary side, between which at least one spring element is coupled such that a torque transmission from the primary side to the Secondary side via the at least one spring element.
  • the vibration damper unit comprises a damper vibration damper comprising at least one damper mass and at least one guide structure, wherein the guide structure is adapted to movably guide the at least one damper mass to damp a vibration component of the rotational movement.
  • the vibration damper unit also includes a seal diaphragm that at least partially separates the damper unit from a space outside the damper unit to at least reduce lubricant penetration to the space portion outside the damper unit, or intrusion into the damper unit.
  • the sealing membrane is supported on the guide structure via a wear-reducing structure against a cover component of the vibration damper unit.
  • a material of the wear reduction structure differs from a material of the cover component.
  • the sealing membrane is supported by a wear reduction structure against a cover component of the vibration damper unit, in some embodiments it may be possible to at least reduce wear and / or noise during a relative movement between the sealing membrane and the cover component.
  • a function of the vibration damper unit can be improved and, under certain circumstances, a lifetime of the vibration damper unit can also be increased.
  • the wear reduction structure may be, for example, a separate component that is not connected to either the cover component or the sealing membrane.
  • the wear reduction structure is arranged in some embodiments in the circumferential direction movable between the sealing membrane and the cover component. In some embodiments, such an ability of the wear reduction structure to reduce wear can be increased.
  • means for fixing the wear-reducing structure can thus be dispensed with.
  • the vibration damper unit includes a Belleville spring or a Belleville spring package that is configured and arranged to effect an axial force progression from a primary side of the vibration damper unit via the guide structure, seal membrane, and wear reduction structure to the cover component.
  • a Belleville spring or a Belleville spring package that is configured and arranged to effect an axial force progression from a primary side of the vibration damper unit via the guide structure, seal membrane, and wear reduction structure to the cover component.
  • an axial securing of the wear reduction structure can be made possible.
  • Fig. 1 is a schematic cross-sectional view of a vibration damper unit according to an embodiment
  • FIG. 2 shows a further schematic cross-sectional view of the vibration dampenings according to the exemplary embodiment of FIG. 1;
  • FIG. 2 shows a further schematic cross-sectional view of the vibration dampenings according to the exemplary embodiment of FIG. 1;
  • FIG. 3 is a schematic cross-sectional view of a vibration damping according to a further embodiment
  • FIG. 4 shows a further schematic cross-sectional representation of the vibration damping according to the embodiment of FIG. 3;
  • Fig. 5 is a schematic representation of a partial elevation of a view of a
  • Vibration damper unit according to another embodiment
  • FIG. 6 shows a schematic cross-sectional view through the vibration damper unit shown in FIG. 5 along a section C;
  • Vibration damper unit according to another embodiment
  • FIG. 8 shows a schematic cross-sectional view through the vibration damper unit shown in FIG. 7 along a section A.
  • FIG. 1 and 2 show schematic cross-sectional views of a vibration damper unit 1 according to an embodiment.
  • the vibration damper unit 1 for example for a drive train of a motor vehicle, comprises a torsion damper 3, which has at least one primary side 5 and at least one secondary side 7 between which at least one spring element 9 is coupled, so that a torque transmission from the primary side 5 to the secondary side 7 via the at least one spring element 9 takes place.
  • the primary side 5 can also be used as a primary flywheel or as part of a housing of the vibration be formed damper unit.
  • the at least one spring element 9 is arranged in a spring region 11.
  • the spring portion 1 1 comprises during operation of the vibration damper unit 1, not shown in FIGS. 1 and 2 lubricant.
  • the primary side 5 or the housing has an opening 82. For example, the lubricant can be introduced into the spring region 11 via the opening 82.
  • the cover component 21 is connected to the primary side 5 via an axial section 23 extending substantially in an axial direction, for example by welding.
  • the axial section 23 has a directed in an axial direction shoulder 25, against which a correspondingly formed shoulder 27 of the cover member 21 is applied.
  • the connection between the cover member and the housing or the primary side can also be done in other ways.
  • the cover component may be formed integrally with the housing.
  • the cover member 21 extends substantially in a radial direction parallel to the primary side 5 and extends further radially inwardly as the spring member 9 extends radially inwardly.
  • a torque is transmitted from a crankshaft, not shown, via a crankshaft screw 29 to the primary side 5.
  • a ring gear 84 is connected to the primary side 5 and the housing.
  • the means for torque introduction may also be designed differently.
  • the spring element 9 of the torsion damper 3 is driven. Additionally or alternatively, the control of the spring element 9 via spring element control shoes 32, as they can be seen for example in Fig. 2 done.
  • the primary side 5 serves to drive the spring element control shoes 32.
  • the spring element 9 transmits the torque to the secondary side 7, which adjoins in the circumferential direction adjacent to the spring element 8 and may be formed, for example, as Federan Kunststoffsteg.
  • the torque can be transmitted to an output shaft, not shown, which rotates about a rotation axis M.
  • a radially inner through hole 33 is introduced. This can serve, for example, for assembly purposes. In some other, not shown embodiments, this through hole can also be omitted.
  • the component comprising the secondary side 7 may also be referred to as a hub or hub disc.
  • the absorber mass 15 is guided via a roller body 37, as can be seen in FIG. 2, on the first guide component 17-a and the second guide component 17-b.
  • the guide components 17-a and 17-b each have a raceway 39-a and 39-b for the rolling element 37.
  • absorber masses can be performed on other rolling elements on the guide structure 17.
  • the damper mass 15 essentially has a plurality of plate-shaped individual filter masses 41a, 41b and 41c, which are arranged substantially parallel to one another. These are connected to each other via a non-illustrated fastener.
  • the absorber mass 15 has a passage opening 43, which passes through the rolling element 37.
  • the passage opening in the outer Einzeletilgermassen 41 -a and 41 -b has a larger diameter than in the inner Einzeletilgermasse 41-c. Accordingly, the rolling element 37 has different diameters, with which it is located in the passage opening 43 of the absorber mass 15. With its axially outermost rolling surfaces 45, and 47, which represent the smallest diameter of the rolling element 37 in the present embodiment, the rolling element 37 rolls along raceways 39-a and 39-b, which are located on or in the guide structures 17 -a and 17-b are off.
  • the absorber masses can be designed differently.
  • these may comprise a greater or lesser number of Einzeletilgermassen or be integrally formed.
  • the rolling elements may be formed in other ways, for example not as a step roller. So he may for example have a uniform diameter.
  • the Tilgerschwingungsdämpfer 13 further comprises a support body 49.
  • This may for example be annular and is arranged via a shoulder 51 on the secondary side 7 radially within the absorber mass 15.
  • the support body 49 can serve, for example, as a radial stop for the absorber mass 15.
  • a vibration damper unit which may also be referred to as a two-mass flywheel with a speed-adaptive absorber, a chambering of the torsion damper and the Tilgerschwingungsdämpfers via at least one sealing membrane or a plurality of sealing membranes, as well as the support body, which may also be formed as a support ring can be reached.
  • the sealing membrane 19 is likewise fastened to the guide structures 17-a and 17-b by means of the connecting structure 34, which connects the two guide structures 17-a and 17-b.
  • the connecting structure 34 By the connecting structure 34, the sealing membrane in the axial, radial and circumferential direction is fixed to the guide structure 17.
  • a montage or production-related game may be allowed between the sealing membrane and the guide structure.
  • the side portion 64-b of the first sub-membrane 59 extends at least to a radial height on which the connecting structure 34 is arranged.
  • the sealing membrane 19 only just extends to over half the radial extent of the guide structures 17-a and 17-b .
  • the sealing membrane may also extend further radially inward.
  • the sealing membrane may also be formed as a one-piece component.
  • the side portion 64-b has an indentation 66, with which the side portion 64-b conforms to a corresponding recess of the guide member 17-a.
  • a space can be reduced in the axial direction.
  • the sub-membrane 59 or the side portion 64-b has a shoulder, so that the sub-membrane 59 is substantially flush with an inner side 68 of the guide structure 17-a expands in a radial direction.
  • the sub-membrane 60 has a side portion 64-a that is substantially analogous to the side portion 64-b.
  • To the side portion 64-a of the partial membrane 60 includes an overlap portion 74 at.
  • the overlapping portion 74 extends substantially in an axial direction.
  • the overlapping section 74 is arranged at a greater radial height than the separating section 70 of the sub-membrane 59.
  • the first sub-membrane 59 and the second sub-membrane 60 overlap in the axial direction.
  • the overlapping section 74 of the sub-membrane 60 overlaps with an overlapping section 76 which adjoins the separating section 70 of the sub-membrane 59 in the axial direction.
  • the overlapping section 76 rests with its radially outwardly directed side against a radially inwardly directed side of the overlapping section 74.
  • the overlapping sections may also be spaced or overlapped in opposite ways. Further, the ends of the sub-membranes may also abut each other in the axial direction or be spaced from each other. The overlapping sections te may for example be connected or not connected to each other.
  • the overlapping section 74 of the second partial membrane 60 is adjoined by a supporting region 62 on a side of the overlapping section 74 opposite the lateral section 64-a, that is to say on a side of the overlapping section 74 facing the spring element 9.
  • the supporting region 62 extends essentially radially outwards from the overlap portion 74.
  • the support portion 62 overlaps in the radial direction with the cover member 21st
  • the cover component 21 has a shoulder 78 on its inner side facing the spring element 9, so that the cover component 21 has a smaller axial extent at a radial end which points towards the sealing membrane 19.
  • the cover member may be formed without this paragraph.
  • the sealing membrane 19 or the second partial membrane 60 is supported with the support region 62 against the cover component 21 on the inside of the cover component 21.
  • a wear reduction structure 80 is arranged between the cover component 21 and the support region 62.
  • the wear reduction structure 80 is a friction ring. This may include as a material, for example, a plastic or Teflon.
  • the wear reduction structure 80 may be attached to either the support portion 62 or the cover member 21.
  • the wear-reducing structure 80 may also be arranged floating between the cover component and the support region, that is to say in the circumferential direction.
  • the wear reduction structure which may also be referred to as a stop ring, may be disposed axially floating between the hub and the absorber carrier.
  • the sealing membrane can be supported directly on the cover component.
  • the wear reduction structure may also be a coating, a gating and / or a coating on the support region and / or the cover component.
  • the cup spring package 53 is supported in the axial direction between the primary side 5 and the first guide structure 17-a. In other words, in the embodiment of Figs. 1 and 2, a seal with the sealing membrane 19 via the cup spring assembly 53 and a stop ring causes.
  • the cup spring package 53 is centered on the angle ring 55, which may also be designed as a pressure ring.
  • FIGS. 3 and 4 show schematic cross-sectional views of a further embodiment of a vibration damper unit 90.
  • the vibration damper unit 90 shown in FIGS. 3 and 4 differs from the vibration damper unit 1 shown in FIGS. 1 and 2 substantially by a Tilgerschwin- vibration damper 92 with external absorber masses 94-a and 94-b, which may also be referred to as a speed-adaptive absorber with a central hub disc. Therefore only differences will be described.
  • Substantially identical or similar components are designated by the same reference numerals as in FIGS. 1 and 2.
  • a sealing membrane 102 of the vibration damper unit 90 also comprises a first part membrane 104 and a second part membrane 106.
  • the first part membrane 104 is between the primary side 5 and the single-piece mass 94-a and the second part membrane 106 arranged on a side facing away from the primary side 5 of the individual piece of adhesive 94-b.
  • the two partial membranes 104 and 106 have an extent in the radial direction which is greater than a radial extent of the absorber mass 94 or of a spatial region in which the absorber mass 94 moves in the radial direction.
  • the sealing diaphragm 102 or the partial diaphragms 104 and 106 are connected to the guide structure 98 radially within a maximum spatial area in which the damper mass 94 moves, via a fastening means 108, as can be seen in FIG. 4.
  • the sealing membrane 102 forms a completely closed envelope or encapsulation for the absorber masses 94.
  • the two sub-membranes 104 and 106 each have a side portion 110 and 112 which extends substantially in a radial direction and is arranged and aligned parallel to an outer edge of the absorber mass.
  • the side sections may also have heels and / or indentations, for example for stabilization.
  • the separating portion 70 analogous to the embodiment of FIGS. 1 and 2 at.
  • the overlapping section 76 which overlaps with the overlapping section 74 of the partial membrane 106, adjoins this.
  • a Beilagwinkelefficiency 1 14 attached to the primary side 5.
  • On this Beilagwinkelification 1 14 is supported in the radial direction from a plastic ring 1 1 6.
  • the plastic ring 1 16 has on its primary side 5 side facing a paragraph 1 18.
  • a similar component made of a different material or with a different shape.
  • At the shoulder 1 18 of the plastic ring 1 1 6 is supported radially inwardly from a plate spring 120. In the axial direction, the plate spring 120 is supported between the primary side 5 and the plastic ring 1 1 6.
  • the plastic ring is supported in an axial direction on the sealing membrane 102 and the partial membrane 104.
  • the first sub-membrane 104 may be supported with the separation portion 70 and its overlap portion 76 in the axial direction on the side portion 1 12 of the second sub-membrane 102.
  • the plate spring and a plate spring assembly may be arranged analogously or similar to the embodiment of FIGS. 1 and 2.
  • an Axialkraftverlauf in the embodiment of FIGS. 1 and 2 similar to the arrangement of Figs. 3 and 4 are effected.
  • the sealing membrane 19 or 102 may be a thin material, for example a sheet metal.
  • the support of the sealing membrane 19 or 102 takes place on the cover plate 21 and the guide structure 17 and 98, which can also be referred to as Tilgeritati.
  • vibration damper units for example, for sealing a fat space or a spring region of a two-mass flywheel or a torsional vibration damper radially or externally between the cover member and the guide structure, which can also be referred to as a track-carrying Tilgerbauteil, medium or directly attached a resilient sheet metal component. This may possibly only create a seal to the outside become.
  • the radially inside of the spring elements which can also be referred to as a spring set, arranged Tilgerschwingungsdämpfer, which can also be referred to as naviereadapti- ver absorber is either not at all or only by a very complex guide structure, which can also be referred to as a track plate, against spray grease protected.
  • FIGS. 5 and 6 are schematic representations of another embodiment of a vibration damper unit 130. This differs from the prior art
  • Vibration damper units 1 and 90 of the preceding embodiments substantially in the formation of a sealing membrane 132. Therefore, only differences will be described below. Identical or substantially similar components are designated by the same reference numerals as in the preceding embodiments.
  • the vibration damper unit 130 also includes a torsion damper 3, which has at least one primary side 5 and at least one secondary side 7, between which at least one spring element 9 is coupled in such a way that a torque transmission from the primary side 5, which may also be formed as a primary flywheel, to the secondary side 7 takes place via the at least one spring element.
  • a plurality of spring elements 9 can be arranged in the circumferential direction, as can be seen for example in FIG. 5. The spring elements 9 are supported in the circumferential direction relative to the secondary side 7.
  • the vibration damper unit 130 also includes a damper vibration damper 13 that includes at least one damper mass 15 and at least one guide structure 17, the guide structure 17 being configured to movably guide the at least one damper mass 15 to dampen a vibrational component of rotational motion. Further, the vibration damper unit 130 includes the seal diaphragm 132 that at least partially separates the vibration damper unit 130 from a space portion 134 located outside the vibration damper unit 130, advances a lubricant to the space portion 134 located outside the vibration damper unit 130, or infiltrates or dirt particles into the vibration damper unit 130 at least reduce.
  • the sealing membrane 132 is supported on the guide structure 17 via the wear reduction structure 80 against a cover component 21 of the vibration damper unit 130. A material of the wear-reduction structure 80 differs from a material of the cover component 21 and of a material of the sealing membrane 132.
  • the wear reduction structure 80 is a separate component in the embodiment of FIGS. 5 and 6.
  • the wear reduction structure 80 may be formed as a friction ring.
  • the wear reduction structure 80 may be circumferentially movably disposed between the sealing membrane 132 and the cover member 21 in some embodiments. In these cases, the wear reduction structure 80, which may also be a stop ring, not connected to the sealing membrane 132 or the cover member 21 and / or fixed thereto.
  • the sealing membrane 132 is substantially similar or similar to the partial membrane 60 of the embodiment of FIGS. 1 and 2 formed. In the embodiment of FIGS. 5 and 6, the sealing membrane 132 has no part which is arranged in the axial direction between the Tilgerschwingungsdämpfer 13 and the primary side 5. Furthermore, the sealing membrane 132 also does not comprise a section in order at least in sections to effect a sealing action between the torsion damper 3 and the absorber vibration damper 13.
  • the sealing membrane 132 extends further than to a radial height on which the connection structures 34 for connecting the guide structures 17-a, which in some embodiments may also be formed as a motor-side track plate, and 17-b are arranged, as shown in FIG 5 recognizable.
  • the sealing membrane 132 is also connected to the connection structure 34 with the guide structure 17-b.
  • a radially inner edge 156 of the sealing membrane 132 is substantially circular, but has at least one recess 157 for assembly reasons.
  • Reference numeral 158 denotes a radially inner end of the guide structure 17-b, which extends almost as far as a radially outer region 136 of an output hub 138.
  • the output hub 138 has an internal toothing.
  • the secondary side 7 is connected via a fastening structure 140 to a flange 142 of an output hub 138.
  • the attachment structure 140 may be formed, for example, as a rivet or rivet bolt. In some embodiments, the secondary side may also be encompassed by the hub.
  • the sealing membrane 132 which can also be referred to as a sealing plate or membrane, has, as can be seen in FIG. 5, because the covering component 21 is not shown, likewise the supporting region 62. This extends substantially in a radial direction.
  • the wear reduction structure 80 is placed, which is not shown in Fig. 5.
  • the cup spring assembly 53 is supported via an angle ring 55 on the primary side 5.
  • the angle ring 55 has a greater extent radially outward than the plate spring package 53, so that the plate spring assembly in the axial direction is fully supported on the angle ring 55 and not on an inner side of the primary side 5.
  • a plastic ring 160 is disposed between the first guide structure 17-a and the cup spring assembly 53, which may also be referred to as thrust washer. In other embodiments, this may also include or be made of another material.
  • the vibration damper unit has, as can be seen in FIG. 6, a connection structure 1 62, which is connected to the primary side 5 via a bearing flange 164.
  • a connection structure 1 62 which is connected to the primary side 5 via a bearing flange 164.
  • a plurality of rivet bolts 166 is used.
  • the connection structure may be formed in other ways or in other ways with the primary side 5 Ver. to be bound.
  • an additional mass 1 68 is attached to the primary side 5 designed as a housing.
  • the cover component 21 has, in the embodiment of FIGS. 5 and 6, as can be seen in FIG. 6, an indentation 170.
  • the indentation 170 By the indentation 170, the cover member 21 is deformed in the axial direction towards the spring element 9 and a spring portion 1 1 tapers.
  • a control of the spring element 9 is possible.
  • the control of the spring element can also be done in other ways, for example via spring control shoes.
  • FIGS. 7 and 8 show different views of a vibration damper unit 180 according to a further embodiment. This is essentially analogous to the vibration damper unit 130 according to the embodiment of FIGS. 5 and 6, and also includes the sealing membrane 132. Therefore, only differences will be described below. The same or substantially similar components are given the same reference numerals.
  • the angle ring 55, against which the plate spring package 53 is supported, is supported in the radial direction on a washer 186.
  • the leg of the angle ring 55 which is arranged parallel to the primary side 55, radially outward on a smaller extent than the plate spring package 53.
  • the cup spring assembly 53 is supported at least in sections on an inner side of the primary side 5. In some other embodiments, not shown, this arrangement can also be designed differently.

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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 une unité d'amortissement de vibrations (1, 90) destinée par exemple à la chaîne cinématique d'un véhicule automobile et comprenant un amortisseur de torsions (3) qui présente au moins un côté primaire (5) et au moins un côté secondaire (7) entre lesquels au moins un élément ressort (9) est raccordé de telle manière qu'une transmission de couple du côté primaire (5) vers le côté secondaire (7) est effectuée par l'intermédiaire de l'élément ressort (9). Le ou les éléments ressorts (9) sont agencés dans une partie ressort (11) qui comprend un lubrifiant pendant le fonctionnement de l'unité d'amortissement de vibrations (1, 90). L'unité d'amortissement de vibrations (1, 90) comprend par ailleurs un amortisseur de vibrations (13, 92) qui comprend au moins une masse d'amortissement (15, 94) et au moins une structure de guidage (17, 98) réalisée pour guider le mouvement de la masse d'amortissement (15, 94) pour amortir une composante d'oscillation d'un mouvement de rotation. L'unité d'amortissement de vibrations (1, 90) comporte également une membrane d'étanchéité (19, 102) qui sépare au moins en partie la partie ressort (11) de la ou des masses d'amortissement (15, 94) pour réduire la pénétration de lubrifiant vers la ou les masses d'amortissement (15, 94). La membrane d'étanchéité (19, 102) est en appui sur la structure de guidage (17, 98) et sur un élément de recouvrement (21) de l'unité d'amortissement de vibrations (1, 90).
EP15712641.8A 2014-04-28 2015-03-30 Unité d'amortissement de vibrations Withdrawn EP3137787A1 (fr)

Applications Claiming Priority (2)

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DE102014207962.4A DE102014207962A1 (de) 2014-04-28 2014-04-28 Schwingungsdämpfereinheit
PCT/EP2015/056834 WO2015165672A1 (fr) 2014-04-28 2015-03-30 Unité d'amortissement de vibrations

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Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012219959A1 (de) * 2011-11-28 2013-05-29 Schaeffler Technologies AG & Co. KG Fliehkraftpendel
DE102014225663A1 (de) * 2014-12-12 2016-06-16 Schaeffler Technologies AG & Co. KG Zweimassenschwungrad mit einteiligem Nabenflansch
CN110621906B (zh) * 2017-05-17 2021-07-30 舍弗勒技术股份两合公司 具有离心力摆的无盖的双质量飞轮
DE102017112345A1 (de) * 2017-06-06 2018-12-06 Schaeffler Technologies AG & Co. KG Abstandsbolzen für ein Fliehkraftpendel
DE102017220224A1 (de) 2017-11-14 2019-05-16 Zf Friedrichshafen Ag Drehschwingungsdämpferanordnung
DE102018001878A1 (de) * 2018-03-08 2019-09-12 Borgwarner Inc. Fliehkraftpendelvorrichtung und Torsionsschwingungsdämpfer mit einer solchen Fliehkraftpendelvorrichtung
DE102018207480A1 (de) * 2018-05-15 2019-11-21 Zf Friedrichshafen Ag Kupplungsanordnung
DE102020205467A1 (de) 2020-04-30 2021-11-04 Zf Friedrichshafen Ag Tilger und Getriebe mit Tilger zum Dämpfen von Torsionsschwingungen
DE102021115830A1 (de) 2021-06-18 2022-12-22 Schaeffler Technologies AG & Co. KG Fliehkraftpendeleinrichtung sowie Drehmomentübertragungseinrichtung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009030971A1 (de) * 2008-07-16 2010-01-21 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Drehmomentübertragungseinrichtung
BRPI0922684B1 (pt) * 2008-12-08 2020-10-27 Schaeffler Technologies AG & Co. KG conjunto amortecedor com pêndulo centrífugo
DE102011086927A1 (de) 2010-12-20 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Torsionsdämpfervorrichtung und Drehmomentübertragungsvorrichtung für ein Kraftfahrzeug
DE102011083168A1 (de) * 2011-09-22 2013-03-28 Schaeffler Technologies AG & Co. KG Treibrad
DE102012212734A1 (de) * 2012-07-19 2014-01-23 Zf Friedrichshafen Ag Dämpferanordnung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2015165672A1 *

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DE102014207962A1 (de) 2015-10-29

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