EP3172459A1 - Système d'amortissement des vibrations torsionnelles pour la chaîne cinématique d'un véhicule - Google Patents

Système d'amortissement des vibrations torsionnelles pour la chaîne cinématique d'un véhicule

Info

Publication number
EP3172459A1
EP3172459A1 EP15733659.5A EP15733659A EP3172459A1 EP 3172459 A1 EP3172459 A1 EP 3172459A1 EP 15733659 A EP15733659 A EP 15733659A EP 3172459 A1 EP3172459 A1 EP 3172459A1
Authority
EP
European Patent Office
Prior art keywords
torsional vibration
output
modular
input
torque
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Withdrawn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
EP15733659.5A
Other languages
German (de)
English (en)
Inventor
Uwe Grossgebauer
Thomas Weigand
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 EP3172459A1 publication Critical patent/EP3172459A1/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Withdrawn legal-status Critical Current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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13157—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses with a kinematic mechanism or gear system, e.g. planetary
    • 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
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/1204—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system
    • F16F15/1206—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system with a planetary gear system
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • 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
    • F16H—GEARING
    • F16H45/00—Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0268—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means the damper comprising a gearing

Definitions

  • the present invention relates to a torsional vibration damping arrangement, for the drive train of a vehicle comprising an input to be driven for rotation about a rotation axis input area and an output area, wherein between the input area and the output area a first torque transmission path and parallel to a second torque transmission path and a coupling arrangement for superimposing over the Torque transmission paths are provided to guided torques, wherein in the first torque transmission path, a phase shifter arrangement for generating a phase shift of the first Drehmomentübertragungsweg conducted rotational irregularities with respect to the second torque transmission path directed rotational irregularities is provided.
  • a phase shifter arrangement is provided which is constructed in the manner of a vibration damper, ie with a primary side and a compressibility of a spring arrangement with respect to this rotatable secondary side. Especially when this vibration System goes into a supercritical state, that is excited with vibrations that are above the resonant frequency of the vibration system, occurs a phase shift of up to 180 °. This means that at maximum phase shift, the vibration components emitted by the vibration system are phase-shifted by 180 ° with respect to the vibration components picked up by the vibration system.
  • the vibration components routed via the other torque transmission path experience no or possibly a different phase shift, the vibration components contained in the combined torque components and then phase-shifted with respect to each other can be destructively superimposed on one another, so that in an ideal case the total torque introduced into the output region is essentially one Vibration components contained static torque is.
  • a torsional vibration damping arrangement preferably in axially narrow spaces, as in the form of a modular system in such a way that it consists of mutually compatible components.
  • a torsional vibration damping arrangement for the drive train of a motor vehicle, comprising an input region to be driven for rotation about a rotation axis (A) and an output region, wherein the input region comprises a primary mass and the output region comprises a secondary mass and one with the output region associated coupling arrangement
  • the coupling arrangement comprises a planetary gear with a planet carrier, a Planetenradbolzen and a planetary gear element, and with a first input element, a second input element and an output element, and a torque transmission path for transmitting a total torque, which extends between the input area and the output area wherein the torque transmission path from the input area to the coupling arrangement in a first torque transmission path, for transmitting a first torque component, and in a par allelic second torque transmission away, for transmitting a second torque component, wherein the first and the second torque transmission path and thus the first and the second torque component are coupled to the coupling assembly to an output torque, and a phase shifter assembly in the first torque
  • the primary mass of the torsional vibration damping arrangement can be non-rotatably connected with, for example, here the crankshaft and also rotatably connected to a Anberichtblech.
  • the planet carrier of the coupling arrangement which is advantageously formed of a support member and a flange, also rotatably connected to the primary mass and thus constitutes a part of the primary mass.
  • the compound can be advantageously realized by multiple circumferentially arranged crankshaft bolts. These components, along with the planetary gears, provide a primary side of the power split.
  • a spring arrangement of the phase shifter arrangement is actuated by the primary mass via at least one control plate.
  • An output of the phase shifter assembly is non-rotatably connected to a drive Hohlradelement.
  • the drive hollow wheel element may consist of a drive hollow wheel carrier and a drive ring gear or be made of one component.
  • the spring arrangement of the phase shifter arrangement transmits the rotary moment to the Antriebsholradtrager.
  • At the Antriebshohlradtrager is rotatably a drive ring gear.
  • an additional mass to increase the moment of inertia can be mounted non-rotatably on Antriebsholradong.
  • On the planetary carrier, which is non-rotatably connected to the primary mass the stepped or ungraded planet gears are rotatably mounted. These mesh with the drive ring gear and a driven ring gear, which is rotatably connected to a driven hollow wheel carrier and together can be referred to as an output element.
  • An output flange element is non-rotatably connected to the output hollow wheel carrier.
  • a rotationally fixed connection with a transmission input shaft can be made via a splined, a friction clutch, a converter or a similar unit can be positioned.
  • An interior of the torsional vibration damping assembly which may also be referred to as a common wet space of the phase shifter assembly and coupling assembly, is sealed to a surrounding area by a first sealing member and a second sealing member.
  • the seal is designed so that a viscous medium, which is located for lubrication and / or cooling in the interior of the torsional vibration damping arrangement, can not reach the surrounding area.
  • the first sealing element is positioned between a flange element and a radially inwardly guided extension of the output planetary gear carrier.
  • the second sealing member is positioned between the output flange member and a cover member rotatably connected to the primary mass.
  • the output flange member is provided with one or more bores which allow access to the crankshaft bolts.
  • both the An Tavernblech the phase shifter assembly, and the planet carrier of the coupling arrangement are connected to the primary mass.
  • the planet carrier is designed as the modular modular planet carrier element, which can be combined as a standardized component with various embodiments of the torsional vibration damping arrangement.
  • the modular modular planet carrier element is designed so that it comprises a first connection region in a radially outer region, on which the primary mass is rotatably attached. This advantageously takes place by means of a welded joint or another ren suitable connection such as by a screw or a riveted joint.
  • the compound is impermeable to a viscous medium.
  • the modular building planplane support element is designed as a mounting flange with which the modular building block planet support element can be connected to a crankshaft of a drive unit. Due to the possibility of combining the modular Baukastenplaneten- carrier element with the primary mass, can be addressed in a simple and cost-effective manner to the various requirements of different drive units.
  • the modular modular planetary carrier element can be provided with differently designed phase shifter arrangements. It is also possible to combine the first component element with the phase shifter arrangement with different second component elements, for example with differently tuned planetary gears. This has the advantage on the one hand that for a modified vibration damping behavior not the entire torsional vibration damping arrangement needs to be changed, but only a partial area.
  • the first input element of the coupling arrangement is connected to an output element of the phase shifter arrangement and the planetary gear element and the second input element of the coupling arrangement is connected to the input area and the planetary gear element and the planetary element with both the first input element, and the second input element and the output element is connected and wherein the output element forms the output region.
  • the first torque component and also the first torsional vibration component is directed via the first torque transmission path by means of the first input member to the planetary gear of the coupling assembly, whereas the second input member directs the second torque component and the second torsional component by means of the second torque transmission path rigidly to the planet.
  • the first and the second torque component, as well as the first and the second torsional vibration component are brought together again or better expressed, superimposed and used as output torque. ment and output as output torsional vibration to the output element.
  • the output element in an advantageous embodiment, for example, receive a friction clutch
  • the phase shifter arrangement comprises a vibration system with the primary mass and an intermediate element rotatable about the axis of rotation A against the action of a spring arrangement.
  • a vibration system can thus be constructed in the manner of a known vibration damper, in which the resonant frequency of the vibration system can be defined defined and thus can be determined in particular by influencing the primary-side mass and the secondary-side mass or the stiffness of the spring arrangement which frequency a transition to the supercritical state occurs.
  • the modular building plan planet carrier element comprises a mounting area with which the modular modular planet carrier element is non-rotatably connected to the entrance area.
  • the input area is advantageously formed by attachment to a crankshaft of a drive unit.
  • Said fastening region of the modular construction planet carrier element is located primarily in a radially inner region and is provided with a fastening geometry corresponding to the crankshaft.
  • the modular modular planet carrier element with the fastening region is fastened in a rotationally fixed manner to the crankshaft by means of a screw connection.
  • the modular modular planetary carrier element thus provides firstly the connection to the crankshaft of the drive unit and secondly it is installed as part of the primary mass in the torsional vibration damping arrangement.
  • the first mounting region of the modular modular planet carrier element is connected in a rotationally fixed manner radially outside with the primary mass, wherein the primary mass forms a receiving region for the spring arrangement of the phase shifter assembly.
  • the modular modular planet carrier element comprises a second connecting region, with which the modular building block tenplanetenitatielement rotatably connected to a connecting element of the input area.
  • the modular building block planet carrier element can be applied to an even wider range of applications for torsional vibration damping arrangements, since the modular modular planet carrier element can be fastened to, for example, a crankshaft by means of the connecting element.
  • An interface of the drive unit to the torsional vibration damping arrangement thus forms the connecting element, which can be designed for a correspondingly corresponding mounting geometry of the crankshaft.
  • the modular modular planet carrier element does not have to have a corresponding fastening geometry, but instead this is done by the connecting element.
  • connection region which preferably takes place by means of a radially extending weld. It is advantageous if the weld for the connection between the connecting element and the modular Baukastenplanetenlusterlement impermeable to a viscous medium is performed. However, it is also possible to choose another known connection method such as, for example, riveting, screwing or a similar suitable connection method.
  • a further advantageous embodiment provides that the first and the second connection region is impermeable to a viscous medium.
  • the torsional vibration damping arrangement encloses a spatial area, which can also be referred to as a wet room.
  • a viscous medium such as oil or grease.
  • the first and also the second connection region of the modular modular planetary carrier element to the primary mass and to the connecting element are connected to one another such that no viscous medium can escape through the connection.
  • the torsional vibration damping arrangement comprises a torque converter and a lock-up clutch.
  • the torsional vibration damping arrangement can also be used in combination with an automatic transmission. These are the torque converter and the Lock-up clutch combined with the torsional vibration damping arrangement.
  • a torque transmission path for an opened lockup clutch is to be distinguished from a torque transmission path for a closed lockup clutch.
  • the torque transmission path in the open lockup clutch of, for example, the crankshaft via the thus rotatably connected primary mass and thus rotatably connected impeller of the torque converter.
  • Via a turbine wheel, which is non-rotatably connected to a Popeschelement the torque reaches, for example, a transmission input shaft.
  • the torque passes from the crankshaft to the primary mass.
  • the lock-up clutch is on the one hand rotatably connected to the primary mass.
  • An output element of the lock-up clutch is non-rotatably connected to the modular modular planet carrier element and rotatably connected to at least one cover plate.
  • the torque is divided here into two torque components.
  • the first portion of torque is passed through the cover plate in a spring set, which can be made single-row or multi-row.
  • the first torque is advantageously via a hollow drive and a drive rotatably connected to the drive ring gear to a planetary gear of a planetary gear, which is rotatably mounted on the modular modular planet carrier element, passed.
  • the second torque component is passed from the output element of the lock-up clutch directly to a planet carrier of the modular modular planet carrier element and thus reaches the planetary gear, where it is superimposed with the first torque component.
  • the torque thus superimposed is advantageously conducted via an output ring gear and a output hollow gear carrier connected therewith in a rotationally fixed manner, which in turn is non-rotatably connected to the turbine wheel, to the output flange element and thus to, for example, a transmission input shaft. Consequently, also for the application of the torsional vibration damping arrangement in combination with the torque converter and the lock-up clutch, the modular modular planetary carrier element can be used as a standardized component.
  • FIG. 1 shows a torsional vibration damping arrangement with a modular modular planet carrier element and a first connection region
  • Fig. 2 is a torsional vibration damping arrangement as in Fig. 1, but with a
  • Fig. 3 is a torsional vibration damping arrangement as in Fig. 1, but with a changed position of the sealing elements and a modified cover
  • Fig. 5 is a torsional vibration damping arrangement, however, in combination with a torque converter and a lock-up clutch.
  • Fig. 6 is a torsional vibration damping arrangement as described in Figure 1, but with a modified cover.
  • Fig. 7 is a torsional vibration damping arrangement as described in Figure 1, but with a modified cover.
  • FIG. 8 shows a torsional vibration damping arrangement with a modular modular planet carrier element in conjunction with a double-row phase shifter arrangement.
  • a torsional vibration damping arrangement 10 which operates on the principle of power or torque split.
  • the torsional vibration damping arrangement 10 can in a drive train of a vehicle between a drive unit 60 and the following part of the drive train, ie
  • a starting element 65 such as a friction clutch, a hydrodynamic torque converter or the like, are arranged.
  • the torsional vibration damping arrangement 10 comprises an input area, generally designated 50.
  • This input area 50 can be connected, for example, as here by a crankshaft 18 of a drive unit 60 designed as an internal combustion engine.
  • the torque absorbed by the drive unit 60 branches into a first torque transmission path 47 and a second torque transmission path 48.
  • the torque components guided via the two torque transmission paths 47, 48 are introduced into the coupling arrangement 41 by means of a first input element 53 and a second input element 54 and then recombined to an output region 55.
  • a vibration system In the first torque transmission path 47, a vibration system, generally designated by reference numeral 56, is integrated.
  • the vibration system 56 is effective as a phase shifter assembly 43 and includes a, for example, to the drive unit 60, to be bonded primary mass 1, and a torque transmitting intermediate element 57, here as a Antriebshohlradong 84, on which also an additional mass 20 may be mounted rotationally fixed, as here in Fig. 1 also shown.
  • a starter ring gear 34 rotatably, preferably by means of a welded connection, attached.
  • the starter ring gear 34 can also be attached to the primary mass 1.
  • the spring arrangement 4 comprises a plurality of circumferentially successive and optionally also nested arranged spring arrangements 58, wherein each spring arrangement preferably comprises at least one helical compression spring or a Bogenfe- the.
  • the spring assembly 58 of the spring assembly 4 is supported on the one hand by means of a Anberichtbleches 2 on the primary mass 1 and on the other hand on a drive element 82, wherein the drive member 82 here the hollow drive 84 and a drive ring gear 83 rotatably connected thereto.
  • the drive element 82 may also be made of a component.
  • the rotationally fixed connection of drive hollow wheel carrier 84 and drive ring gear 83 is preferably attached by means of a welded connection, a riveted connection, a screw connection, an adhesive connection, a press connection, a positive connection or a comparable connection method or a combination of the mentioned connection methods.
  • the drive ring gear 83 conducts the torque which has been conducted via the first torque transmission path 47 and thus via the phase shifter assembly 43 to a planetary gear element 45 of the coupling arrangement 41.
  • the planetary gear 45 here includes a Antriebsplanetenrad 80 and a driven planetary gear 81, which are arranged axially staggered.
  • the drive ring gear 83 which meshes with the drive planet gear 80, the first input element 53 of the coupling assembly 41 is.
  • the torque is conducted via the crankshaft 18 into the second input element 54.
  • This is non-rotatably connected to the crankshaft 18, primarily by a screw 68, formed here by means of the crankshaft screw 17, and forms the carrier element 12 of the planet carrier 9 of the coupling arrangement 41st Together with the flange element 70, the support element 12 and the flange element 70 thus form the actual planet carrier 9.
  • the planet gear pin 1 1 is mounted on both sides, ie on the carrier element 12 and on the flange element 70. This prevents tilting of the planetary pin.
  • the planetary gear 45 of the coupling assembly 41 which is rotatably mounted on the planet carrier 9 by means of a planetary gear 1 1, performs the first torque transmission path 47 which is passed via the Antriebsholrad 83 in the coupling assembly 41 and the second torque transmission path 48, via the second input element 54, formed by the planet carrier 9, is passed to a torque together.
  • the torque which is brought together is transmitted to an output flange element 75, which is connected to the output hollow wheel carrier 87 in a torque-proof manner via an output ring gear 86 and a output hollow gear carrier 87, which together form an output element 85, and here the output Gangselement 49 forms, forwarded and delivered from there, for example, to a, not shown here, secondary mass, a friction clutch or directly to a transmission.
  • a first sealing element 24 and a second sealing element 25 are used.
  • the first sealing element 24 is positioned between the output hollow wheel carrier 87 and a flange element 70. Between the output hollow gear carrier 87 and the flange 70, a relative rotation can take place.
  • the flange element 70 is connected to the planet carrier 9 so that no viscous medium can escape from the wet space 63 at a connection region of the flange element 70 with the planet carrier 9 to the surrounding area 69.
  • the flange 70 is designed so that this further supports the Planetenradbolzen 1 1.
  • the Planetenradbolzen 1 1 is advantageously secured against tilting.
  • the second seal member 25 is positioned between the cover member 22 and the output flange member 75. Between the cover member 22 and the technicallyflanschelement 75, a relative rotation can take place.
  • first sealing element 24 and the second sealing element 25 are of identical construction here. This results in advantages when purchasing the components and when using a smaller number of assembly tools, since only one size is used for the sealing elements. In not shown in this figure, but also different sizes of sealing elements can be used.
  • the planet carrier 9 is designed as a modular modular planet carrier element 95 with a first connection region 31.
  • the modular building block planet carrier element 95 is designed in such a way that it can be installed as a standard component in combination with differently designed connection components. This is particularly advantageous when the spring set 4 of the phase shifter assembly 43 has to be designed differently due to different types of motors.
  • the modular modular planet carrier element 95 can then be connected in a rotationally fixed manner to the first connection region 31, which is located radially on the outside, with the primary mass 1, which here also receives the spring assembly 4. This is advantageously done by means of a welded connection or a similar known and suitable connection.
  • this compound is impermeable to a viscous medium.
  • the modular construction planet carrier element 95 is designed as a mounting flange 21 in order to non-rotatably connect the modular construction planet carrier element 95 to the crankshaft 18, preferably by means of crankshaft bolts 17.
  • modular modular planet carrier member 95 includes an additional second connection portion 32 located radially inwardly therein.
  • modular modular planet carrier element 95 can be further standardized, since a connection to a corresponding crankshaft mounting geometry is no longer effected by modular modular planet carrier element 95, but by a separate component, such as here connecting element 15.
  • Modular modular planet carrier element 95 becomes with the second connection portion 32, preferably by means of a welded connection or another known and suitable connection, which is preferably impermeable to a viscous medium, rotatably connected to the connecting element 15.
  • This embodiment is the modular modular planet carrier element 95 for a still wider embodiment of different torsional vibration damping arrangements available. Consequently, the modular modular planetary support member 95 can be inexpensively manufactured as a standard component.
  • FIG. 3 shows a torsional vibration damping arrangement 10 as already described in FIG. 1, but with a first sealing element 24 and a second sealing element 25, wherein the first sealing element 24 and the second sealing element 25 have different sizes.
  • the output flange element 75 is additionally rotatably mounted on the flange element 70 by means of a bearing element 77, which may advantageously be designed as a ball bearing.
  • the cover 22 is provided with a lateral stabilization geometry 23, which additionally forms a centering edge 26 for receiving a starter ring gear 34.
  • the stabilizing geometry 23 serves not only for receiving the starter ring gear, but also serves to stabilize the cover 22, which has a positive effect at high centrifugal forces and is also positive for a seal with the second sealing member 25, since the cover 22 by the stabilization geometry less deformed under centrifugal force.
  • FIG. 4 shows a section of FIG. 3 in the region of the phase shifter arrangement 43.
  • a projection 90 which is formed from the primary mass 1 by, for example, a forming method, can advantageously be seen there.
  • the Anformung 90 takes on the An Tavernblech 3 and can pinch or press the An Kunststoffblech 3 by another forming process.
  • the formation 90 can be designed like a rivet 91 formed from the primary mass 1.
  • the advantages result from the fact that the formation 91 can be used as a rivet 91, without the primary mass having to be drilled to perform a rivet. This is particularly advantageous if this area is to be impermeable to a viscous medium.
  • laser welding, brazing, riveting, spot welding, or resistance welding may also be provided.
  • FIG. 5 shows a torsional vibration damping arrangement 10 with a modular modular planet carrier element 95 which is installed in a combination with a torque converter 88 and a lockup clutch 89.
  • the torque transmission path with a closed lockup clutch 89 or with an opened lockup clutch 89 are known from the prior art.
  • the torque transmission path with closed lock-up clutch 89 will be discussed.
  • the torque is divided and over a first torque transmission 47 and a second torque transmission 48 further.
  • the torque portion of the cover plates 27 via a radially inner spring assembly 5 and a hub disc 14 to a radially outer spring assembly 4 is passed.
  • the torque component passes via a hollow drive carrier 84 and via a drive ring gear 83 connected thereto in a rotationally fixed manner to a coupling arrangement 41, here in the form of a planetary gear 61.
  • the second torque transmission path 48 extends from the output element 99 of the lock-up clutch 89 directly to a planet carrier 9 of a modular modular planet carrier element 95.
  • the modular modular planetary carrier element 95 is provided with a first connection region 31, which is located radially outward, by means of a rivet connection 64 with the output member 99 of the lock-up clutch 89 rotatably connected.
  • FIG. 6 shows a torsional vibration damping arrangement 10, as already described in FIG. 1, but with a modified cover element 22.
  • the aim is to mold the cover element in such a way that it deforms only slightly under the action of a centrifugal force and that the enclosed space is as small as possible only need a small amount of viscous material for lubrication. It is, as already described above, perform the rotationally fixed connection between the cover 22 and the primary mass 1 impermeable to the viscous material.
  • the rotationally fixed connection between the cover and the primary mass by means of a shirred seam 78.
  • a central position of the welded joint has the further advantage that the connection is as far away from increased stress concentrations in the corners.
  • FIG. 7 shows a torsional vibration damping arrangement 10, as already described in FIG. 6, but with a modified cover element 22.
  • cover element 22 which has already been described in FIG. 6 applies.
  • the cover plate 22 is as stiff as possible.
  • the cover plate 22 has an additional centering 26, which can be used for receiving a starter ring gear, not shown here.
  • FIG. 8 shows a torsional vibration damping arrangement 10, which, like FIG. 1, operates according to the principle of power branching.
  • the embodiment here comprises a double-row phase shifter arrangement 44, with a first spring arrangement 51, which is arranged radially outward there, and a second spring arrangement 59, which is arranged radially inside the first spring arrangement 51.
  • the torsional vibration damping arrangement 10 comprises an input region 50. In the input region 50, the absorbed torque branches into a first torque transmission path 47 and a second torque transmission path 48.
  • the torque components Mal and Ma2 guided via the two torque transmission paths 47, 48 and the torsional vibration components DSwA1 and DsWA2 contained therein are introduced into the control system by means of a first input element 53 and a second input element 54 Coupling arrangement 41 introduced and rejoined and then forwarded as an output torque mouse with an output torsional vibration contained therein ADSw to an output range 55.
  • the double-row phase shifter assembly 44 is integrated with the first spring assembly 51 and the second spring assembly 59.
  • the spring arrangements 51 and 59 may be made of a plurality of consecutive in the circumferential direction and depending on the embodiment also nested arranged helical compression springs or as a bow spring.
  • the first spring arrangement 51 is supported, on the one hand, by means of control elements 6, which are connected to the primary mass 1, on the primary mass 1 and, on the other hand, on a hub disk 66.
  • the second spring arrangement 59 is supported on the one hand on the hub disc 66 and on the other hand on an intermediate element 57 and with a cover plate 67 firmly connected thereto.
  • the drive ring gear 83 is fastened here in a rotationally fixed manner by means of a connecting element 73.
  • the use of the connecting element 73 represents only one embodiment variant.
  • the drive ring gear can also be fastened directly to the intermediate element 57.
  • the additional masses 20 which, depending on the embodiment and tuning in the required number of pieces to the intermediate member 57 can be rotatably attached to increase the moment of inertia of the intermediate member 57, so as to improve the function of the phase shifter assembly.
  • the modular modular planet carrier element 95 which is fastened in a rotationally fixed manner to the primary mass 1 by means of a connecting flange 74.
  • the output is in known
  • the disc member 79 may be omitted and the Austriebshohlradtrager 87 may then be directly connected to the transmission, such as a dual-clutch transmission.

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

Abstract

L'invention concerne un système d'amortissement des vibrations torsionnelles (10) pour la chaîne cinématique d'un véhicule automobile, comprenant une zone d'entrée à entraîner en rotation sur un axe de rotation (A) et une zone de sortie (55), et un système d'accouplement (41) en liaison avec la zone de sortie (55), ainsi qu'un système déphaseur (43) en liaison avec la zone d'entrée (50) et une voie de transmission de couple (46) servant à la transmission d'un couple total (Mges), laquelle s'étend entre la zone d'entrée (50) et la zone de sortie (55). La voie de transmission de couple (46), entre la zone d'entrée (50) et le système d'accouplement (41), est partagée en une première voie de transmission de couple (47) et une deuxième voie de transmission de couple (48) parallèle qui sont de nouveau fusionnées au niveau du système d'accouplement (41), et une vibration torsionnelle d'entrée (EDSw), par le biais de la transmission sur la première et sur la deuxième voie de transmission de couple (47; 48), est partagée en deux parts de vibrations torsionnelles (DSwA1, DSwA2) qui sont ensuite superposées de manière destructive en une vibration torsionnelle de sortie (ADSw) au niveau du système d'accouplement (41) afin d'obtenir ainsi, au niveau d'un élément de sortie (85) du système d'accouplement (41), une vibration torsionnelle de sortie (ADSw) minimisée par rapport à la vibration torsionnelle d'entrée (EDSw). Le porte-satellites (9) est réalisé sous la forme d'un élément porte-satellites modulaire (95) et comprend au moins une première zone de liaison (31) radialement en-dehors d'une fixation de l'axe de pignon planétaire (11) sur le porte-satellites (9), avec laquelle l'élément porte-satellites modulaire (95) est relié solidairement en rotation avec la masse primaire (1).
EP15733659.5A 2014-07-24 2015-06-22 Système d'amortissement des vibrations torsionnelles pour la chaîne cinématique d'un véhicule Withdrawn EP3172459A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102014214529 2014-07-24
DE102015207825.6A DE102015207825A1 (de) 2014-07-24 2015-04-28 Drehschwingungsdämpfungsanordnung für den Antriebsstrang eines Fahrzeugs
PCT/EP2015/063918 WO2016012169A1 (fr) 2014-07-24 2015-06-22 Système d'amortissement des vibrations torsionnelles pour la chaîne cinématique d'un véhicule

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EP3172459A1 true EP3172459A1 (fr) 2017-05-31

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US (1) US20170219047A1 (fr)
EP (1) EP3172459A1 (fr)
CN (1) CN106574685A (fr)
DE (1) DE102015207825A1 (fr)
WO (1) WO2016012169A1 (fr)

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Publication number Priority date Publication date Assignee Title
US9856958B2 (en) * 2015-12-08 2018-01-02 GM Global Technology Operations LLC Torsional vibration damper
DE102017207031A1 (de) * 2017-04-26 2018-10-31 Zf Friedrichshafen Ag Drehschwingungsdämpfungsanordnung für den Antriebsstrang eines Fahrzeugs
CN111379837A (zh) * 2018-12-28 2020-07-07 株式会社法雷奥凯佩科 用于变矩器的锁止装置

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CN2547951Y (zh) * 2002-05-30 2003-04-30 陈伯恒 通用型汽车机械自动变速器
CN2553191Y (zh) * 2002-07-04 2003-05-28 陈伯恒 汽车机械自动变速器
US9316299B2 (en) 2010-05-25 2016-04-19 Zf Friedrichshafen Ag Hydrodynamic coupling device, in particular a torque converter
DE102011075240A1 (de) * 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Hybridantriebsmodul
DE102011075241A1 (de) * 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Nasslaufende Kupplungsanordnung
DE102011075243A1 (de) * 2010-05-25 2011-12-01 Zf Friedrichshafen Ag Hydrodynamische Kopplungseinrichtung, insbesondere Drehmomentwandler
CN102166947B (zh) * 2011-03-10 2013-05-01 上海交通大学 多模无级变速混合动力驱动系统
DE102013214060A1 (de) * 2012-07-20 2014-02-20 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung
DE102012214455A1 (de) * 2012-08-14 2014-02-20 Zf Friedrichshafen Ag Drehschwingungsdämpfungsanordnung für den Antriebsstrang eines Fahrzeugs
DE102012218729A1 (de) * 2012-10-15 2014-04-17 Zf Friedrichshafen Ag Drehschwingungsdämpfungsanordnung für den Antriebsstrang eines Fahrzeugs

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DE102015207825A1 (de) 2016-01-28
US20170219047A1 (en) 2017-08-03
WO2016012169A1 (fr) 2016-01-28
CN106574685A (zh) 2017-04-19

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