EP3948023A1 - Amortisseur de vibrations torsionnelles et convertisseur hydrodynamique de couple de rotation en étant équipé - Google Patents

Amortisseur de vibrations torsionnelles et convertisseur hydrodynamique de couple de rotation en étant équipé

Info

Publication number
EP3948023A1
EP3948023A1 EP20714111.0A EP20714111A EP3948023A1 EP 3948023 A1 EP3948023 A1 EP 3948023A1 EP 20714111 A EP20714111 A EP 20714111A EP 3948023 A1 EP3948023 A1 EP 3948023A1
Authority
EP
European Patent Office
Prior art keywords
torsional vibration
vibration damper
intermediate flange
helical compression
output
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Withdrawn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
EP20714111.0A
Other languages
German (de)
English (en)
Inventor
David SCHNÄDELBACH
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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 Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3948023A1 publication Critical patent/EP3948023A1/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Withdrawn legal-status Critical Current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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1232—Wound springs characterised by the spring mounting
    • F16F15/12346—Set of springs, e.g. springs within springs
    • 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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/1232—Wound springs characterised by the spring mounting
    • 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
    • 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
    • F16F15/121—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 using springs as elastic members, e.g. metallic springs
    • F16F15/123—Wound springs
    • F16F15/12353—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
    • 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
    • F16F2232/00—Nature of movement
    • F16F2232/02—Rotary
    • 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
    • F16F2236/00—Mode of stressing of basic spring or damper elements or devices incorporating such elements
    • F16F2236/08—Torsion
    • 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
    • F16H2045/0226—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 comprising two or more vibration dampers
    • 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
    • F16H2045/0263—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 pendulum
    • 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
    • F16H2045/0273—Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284—Multiple disk type lock-up clutch

Definitions

  • the invention relates to a torsional vibration damper and a hydrodynamic torque converter with the latter, the torsional vibration damper having an input part that can be rotated about an axis of rotation and an output part, with an intermediate flange being provided between the input part and the output part against a spring device that is effective in the circumferential direction, and the intermediate flange is formed from two axially spaced, interconnected side parts, which axially receive the input part and the output part between them.
  • Generic torsional vibration dampers for example for hydrodynamic torque converters, are used in drive trains of motor vehicles to isolate torsional vibrations from torsional vibrations of an internal combustion engine subject to torsional vibrations.
  • torsional vibration dampers of this type can be provided between a converter lock-up clutch and an output hub and / or between a turbine wheel driven by an impeller of the torque converter and the output hub.
  • the publication DE 10 2010 014 674 A1 shows, for example, a hydrodynamic torque converter with a torsional vibration damper arranged within its housing.
  • the torsional vibration damper has an input part connected to a turbine wheel and a converter lockup clutch, an output part connected to an output hub and an intermediate flange connected in series between these by means of spring devices.
  • the intermediate flange carries a centrifugal pendulum.
  • the object of the invention is to develop a generic torsional vibration damper and a hydrodynamic torque converter with this.
  • the object of the invention is to design the application of the spring devices before part.
  • the proposed torsional vibration damper serves to isolate torsional vibrations from torsional vibrations, in particular in a drive train of a motor vehicle with an internal combustion engine subject to torsional vibrations.
  • the torsional vibration damper is integrated into a housing of a hydrodynamic torque converter.
  • the torsional vibration damper contains an input part that can be rotated about an axis of rotation and an output part, with an intermediate flange arranged between the input part and the output part, which is arranged against a respective spring device acting in the circumferential direction.
  • the intermediate flange is formed from two axially spaced, interconnected Be tentmaschine, which take the input part and the output part between them.
  • a centrifugal pendulum can be arranged on the intermediate flange to improve the torsional vibration isolation of the torsional vibration damper.
  • the two side parts can serve as a pendulum mass carrier for pendulum masses distributed over the circumference, for example pendulum masses arranged in an order of two to four.
  • the pendulum masses formed in a layered manner from several sheet metal parts are arranged axially between the side parts. Side parts and pendulum masses have axially aligned recesses with raceways on which a pendulum roller axially overlaps the recess rolls.
  • the input part and the output part can be designed as disk parts formed axially next to one another.
  • a side part facing a converter lock-up clutch of a hydrodynamic torque converter can be shortened radially on the inside so that a connection such as riveting can be formed between the output part of the converter lock-up clutch and the input part of the torsional vibration damper.
  • the input part can be centered on an output hub and the output part can be connected to this drive hub in a rotationally fixed manner.
  • the output part and the drive hub from can be formed in one piece, riveted to one another or connected to one another by means of internal and external teeth in a rotationally fixed manner and with axial play.
  • the disk parts can have impact areas for the spring devices arranged in one plane.
  • parts of the disk parts can axially overlap and be designed radially one above the other, so that the spring devices, for example designed as helical compression springs, are each acted upon axially centrally by the input part or the output part, based on their cross section.
  • the spring devices can each be formed from linearly designed helical compression springs distributed over the circumference.
  • the helical compression springs can each be housed individually captive on a circumference.
  • so-called helical compression spring packages can be provided in which several helical compression springs are nested inside one another as an inner spring and an outer spring.
  • the helical compression springs of a helical compression spring assembly can be designed to have different lengths for setting a multi-stage characteristic curve of the torsional force over the angle of rotation of the rotary vibration damper.
  • different Helical compression springs and / or different helical compression spring packages be arranged.
  • the helical compression springs can be arranged on different diameters.
  • the helical compression springs of the two spring devices are preferably arranged on the same diameter and alternately over the circumference.
  • Helical compression springs are loaded through the side parts.
  • axially aligned spring windows are provided in the Be tentile of the intermediate flange, in which the helical compression springs or helical compression spring packs are introduced captive and radially supported against centrifugal force.
  • the radial walls of the spring window serve as areas of application of the intermediate flange.
  • the areas of application of the input part and / or the output part can be of planar design or have lugs that extend in the circumferential direction and engage in the interior of at least a part of the screw compression springs.
  • the lugs can be designed in such a way that the screw compression spring ends are pulled radially inward during an impact, and therefore friction between them is prevented or at least reduced radially on the outside.
  • the disk parts When the torsional vibration damper is not loaded, the disk parts preferably have radially outwardly open recesses for the helical compression springs that are axially aligned with the spring windows, with a support that extends over the helical compression spring in the circumferential direction on at least one disc part.
  • the input part, the intermediate flange and the output part are arranged in series by means of the helical compression springs acting in the circumferential direction and the input Gang part and the output part can be thoroughlybil det as axially adjacent disk parts, which are arranged between the two axially spaced and connected to each other which side parts of the intermediate flange.
  • the spring devices In order to provide reliable loading of the spring devices, in particular independently of the design of the spring devices, their loading by means of the intermediate flange is provided at least partially by loading means arranged between the side parts.
  • the spring devices in particular designed as helical compression springs, can be acted upon by means of components axially arranged between these parts. For example, a minimum of 50% overlap of the cross-sections of all helical compression springs linked by the intermediate flange can be provided.
  • the inner springs can be acted upon by the Beauftschungsmit means arranged between the side parts.
  • the outer springs can be acted upon exclusively by the walls of the spring windows receiving them and / or by the acting means arranged between the side parts.
  • the acting means arranged between the side parts can at least partially be formed from spacer bolts connecting the side parts.
  • the loading means can also be formed from at least one side part.
  • the loading means can be formed from sheet metal parts or rivets connected to at least one side part. For example, between two in the circumferential direction of adjacent end faces of the helical compression springs, a rivet connected on one side to a side part, such as a stop rivet, can be provided as a loading means.
  • sheet metal disks or the like can be connected to a side part at this point, for example welded.
  • the acting means arranged between the side parts can be adapted in the circumferential direction to the end faces of the helical compression springs, for example be designed flat or adapted to a course of the end turn of the helical compression springs.
  • the proposed hydrodynamic torque converter is used in particular in a drive train of a motor vehicle to transmit torque from a crankshaft of an internal combustion engine to a transmission input shaft of a gearbox, possibly adjusting different speeds and to increase torque during a start-up phase of the motor vehicle.
  • the torque converter contains a housing with which a pump wheel is integrated in a rotationally fixed manner or can be connected by means of a separate clutch.
  • the pump wheel drives a turbine wheel hydrodynamically.
  • the torque introduced into the torque converter is wan delt via an output hub that can be or is connected to the turbine wheel, for example transmitted excessively to a transmission input shaft of a transmission, for example a multi-stage automatic transmission.
  • a converter lock-up clutch integrated into the housing can be provided between the housing and the output hub.
  • a first torsional vibration damping device is provided between the output part of the converter lockup clutch and the output hub.
  • the turbine wheel can be rotated added on the output hub counter to the action of a second Wheelschwingungseinrich device, a so-called turbine damper.
  • the two torsional vibration damping devices are provided by means of the proposed single torsional vibration damper.
  • the input part of the torsional vibration damper is connected to the output of the torque converter lockup clutch and the output part is connected to the output hub.
  • the torsional vibration damper has an intermediate flange which is effectively arranged by means of spring means effective in the circumferential direction between the input part and the output part.
  • the turbine wheel To connect the turbine wheel to the torsional vibration damper, it is non-rotatably connected to the intermediate flange, for example riveted and centered on the drive hub.
  • a centrifugal pendulum is added to the intermediate flange.
  • the centrifugal pendulum can be matched to a single damper order by similar training of all Pen delmassen and their self-aligning bearings with predetermined pendulum tracks with respect to the intermediate flange.
  • two damper orders can be provided which are matched to the vibration modes of the open and closed wall ler bridging clutch and / or to a different number of cylinders operated by the internal combustion engine.
  • two sets of pendulum masses with different masses and / or different surfaces by means of appropriate training of the raceways of the pendulum bearings between pendulum mass carriers and pendulum masses provided Pendulum tracks can be provided.
  • the turbine mass can serve as an additional damper mass of the intermediate flange.
  • Figure 1 shows the upper part of a rotatable about an axis of rotation
  • Figure 2 shows the torsional vibration damper of Figure 1 in partial view
  • Figure 3 shows the upper part of a compared to the torsional vibration damper of
  • Figures 1 and 2 modified torsional vibration damper in section.
  • FIG. 1 shows the upper part of the torsional vibration damper 1 rotatable about the axis of rotation d in section.
  • the input part 2 is connected to the output-side plate carrier 3 of a torque converter lockup clutch of a hydrodynamic torque converter by means of the rivets 4 distributed over the circumference.
  • the input part 2 is received in a rotatable centered manner on the output hub 5.
  • the output part 6 is non-rotatably connected to the output hub 5.
  • Input part 2 and output part 6 are designed as disk parts 7, 8 arranged parallel to one another.
  • the disk part 7 is axially fixed and rotatably received by means of the locking disk 9 and the ring flange 10 of the output hub 5 and is centered on the output hub 5.
  • the disk part 8 is axially pretensioned between the annular rim 10 and the thrust washer 11 and is held non-rotatably on the output hub 5 by means of a toothing (not shown).
  • the intermediate flange 12 is formed from the two axially spaced apart side parts 14, 15 connected to one another by means of the spacer bolts 13.
  • the discs parts 7, 8 are axially between the side parts 14, 15 of the intermediate flange 12 added.
  • the side part 14 facing the disk carrier 3 is radially inward recessed in order to make the connection of the plate carrier 3 to the input part 2 possible.
  • the side parts 14, 15 form the pendulum mass carrier 16 of the centrifugal pendulum 17 and take between them distributed over the circumference the pendulum masses 18 formed from, for example, riveted sheet metal disks between them.
  • the Pendelmas sen 18 are suspended by means of pendulum bearings, not shown, on the pendulum mass carrier 16 in the centrifugal force field of the torsional vibration damper 1 rotating about the axis of rotation d ent long a predetermined pendulum path.
  • Spring devices 19, 20 are effective between the input part 2, the intermediate flange 12 and the output part 6.
  • the spring devices 19, 20 are arranged in Se rie, that is, when the input part 2 is rotated relative to the output part 6 about the axis of rotation d depending on the direction of the applied torque, that between the input part 2 and the intermediate flange 12 and that between the intermediate flange 12 and the output part 6 effectively arranged spring devices 19, 20 loaded in series.
  • the spring devices 19, 20 are formed from linear, nested screw compression springs 21, 22, 23, 24, which are arranged distributed over the circumference.
  • the particular made of plastic and rotatably in the side part 15 is suspended thrust washer 1 1 limits the axial play of the intermediate flange 12.
  • the inter mediate flange 12 is rotated by means of the side part 15 on the output hub 5 taken and centered.
  • the helical compression springs 21, 22, 13, 24 are in the spring windows 25, 26 of the side parts 14, 15 captively housed and supported radially on the outside.
  • the loading of the helical compression springs 21, 22, 23, 24 in the circumferential direction is carried out in each case by means of loading that cannot be seen from this sectional view.
  • the radial walls of the spring windows 25, 26 act on the outer helical compression springs 21, 23 and only overlapping the inner helical compression springs 22, 24.
  • the side part 14 is cranked to increase the coverage in the area of the cross section of the helical compression springs 21, 23 educated.
  • the spacer bolts 13 are also provided, which act on part of the outer helical compression springs 21, 23 and a large part of the inner helical compression springs 22, 24.
  • the diameter D of the spacer bolts 13 is expanded such that it is essentially identical to the radial walls of the spring windows 25, 26. In this way, an areal loading of the helical compression springs 21, 22, 23, 24, in particular the inner helical compression springs 22, 24, is achieved without additional parts.
  • FIG. 2 shows the torsional vibration damper 1 of FIG. 1 in a partial view with the front side part 14 removed (FIG. 1) and the disk part 7 on the input side removed (FIG. 1).
  • This representation becomes the one distributed over the circumference Arrangement of the pendulum masses 18 of the centrifugal pendulum 17 radially outside the spring devices 19, 20 with the nested helical compression springs 21, 22, 23, 24 clearly.
  • the pendulum masses 18 are accommodated on the intermediate flange 12 in a pendulous manner by means of the self-aligning bearings 28.
  • the helical compression springs 21, 22, 23, 24 are received in the spring windows 26 and are acted on on the one hand by the acting means 29 of the disc part 8 of the output part 6 and the non-visible acting means of the disc part 8 of the input part and on the other hand by the acting means 27 of the intermediate flange 12 .
  • the loading means 27 are formed from the radial walls 30 of the side parts 14, 15 (FIG. 1) and the spacer bolts 13.
  • FIG. 3 shows the upper part of the rotary vibration damper 1a arranged about the axis of rotation d in section.
  • the loading means 27a of the intermediate flange 12a are next to the radial walls 30a of the spring windows 25a, 26a of the side parts 14a, 15a forming the intermediate flange 12a from additionally in the circumferential direction between the spring windows 25a, 26a on radial Fleas of the helical compression springs 21a, 22a, 23a, 24a rivets 31a introduced into the side part 15a are formed.
  • the cranked in the area of the wall 30a side part 14a acts on the inner and outer screw compression springs 21 a, 22a, 23a, 24a.
  • the side part 15a acts on the outer helical compression springs 21a, 23a.
  • the rivets 31a introduced into the side part 15a each act on the inner helical compression springs 22a, 24a.
  • the position of the spacer bolts (not shown) that connect the side parts 14a, 15a can be selected outside the diameter of the helical compression springs 21a, 22a, 23a, 24a.

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

Abstract

La présente invention concerne un amortisseur de vibrations torsionnelles (1) et un convertisseur hydrodynamique de couple de rotation en étant équipé. L'amortisseur de vibrations torsionnelles (1) comprend une partie d'entrée (2) et une partie de sortie (6) pouvant tourner autour d'un axe de rotation (d), entre la partie d'entrée (2) et la partie de sortie (6) étant disposé un flasque intermédiaire (12) ayant de chaque côté un dispositif à ressort (19, 20) actif dans la direction circonférentielle et le flasque intermédiaire (12) étant formé de deux parties latérales (14, 15), distantes axialement l'une de l'autre et reliées entre elles, qui reçoivent axialement entre elles la partie d'entrée (2) et la partie de sortie (6). Pour améliorer l'action des dispositifs à ressort (19, 20), une action des dispositifs à ressort (19, 20) est réalisée au moyen du flasque intermédiaire (12) au moins en partie par des moyens d'action (27) disposés entre des parties latérales (14, 15).
EP20714111.0A 2019-04-05 2020-03-10 Amortisseur de vibrations torsionnelles et convertisseur hydrodynamique de couple de rotation en étant équipé Withdrawn EP3948023A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019109020.2A DE102019109020B4 (de) 2019-04-05 2019-04-05 Drehschwingungsdämpfer und Hydrodynamischer Drehmomentwandler mit diesem
PCT/DE2020/100170 WO2020200356A1 (fr) 2019-04-05 2020-03-10 Amortisseur de vibrations torsionnelles et convertisseur hydrodynamique de couple de rotation en étant équipé

Publications (1)

Publication Number Publication Date
EP3948023A1 true EP3948023A1 (fr) 2022-02-09

Family

ID=70005566

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20714111.0A Withdrawn EP3948023A1 (fr) 2019-04-05 2020-03-10 Amortisseur de vibrations torsionnelles et convertisseur hydrodynamique de couple de rotation en étant équipé

Country Status (5)

Country Link
US (1) US11796032B2 (fr)
EP (1) EP3948023A1 (fr)
CN (1) CN113412382B (fr)
DE (1) DE102019109020B4 (fr)
WO (1) WO2020200356A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019125872A1 (de) * 2019-09-25 2021-03-25 Schaeffler Technologies AG & Co. KG Hybridantriebsstrang

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US6224487B1 (en) * 1997-04-02 2001-05-01 Borgwarner Inc. Two stage torsional vibration damper
DE10024191B4 (de) * 1999-05-21 2012-06-28 Schaeffler Technologies Gmbh & Co. Kg Drehmomentübertragungseinrichtung
WO2007054061A2 (fr) * 2005-11-10 2007-05-18 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Dispositif convertisseur de couple hydrodynamique pour chaine cinematique d'automobile
DE202010018604U1 (de) * 2009-04-27 2018-04-27 Schaeffler Technologies AG & Co. KG Hydrodynamischer Drehmomentwandler
DE112011100547B4 (de) * 2010-02-16 2021-01-14 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung
DE112011100546B4 (de) * 2010-02-16 2019-12-12 Schaeffler Technologies AG & Co. KG Hydrodynamischer Drehmomentwandler
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DE102011017653B4 (de) * 2011-04-28 2018-12-20 Zf Friedrichshafen Ag Hydrodynamische Kopplungsanordnung, insbesondere hydrodynamischer Drehmomentwandler
DE102012213015A1 (de) * 2012-07-25 2014-02-13 Zf Friedrichshafen Ag Anfahrelement mit Torsionsschwingungsdämpfer und Schwingungstilger
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JP6514791B2 (ja) * 2016-01-29 2019-05-15 アイシン・エィ・ダブリュ工業株式会社 ダンパ装置
US10400874B2 (en) * 2016-03-23 2019-09-03 Toyota Jidosha Kabushiki Kaisha Torque converter having torsional vibration damping device
DE102017205815A1 (de) * 2017-04-05 2018-10-11 Zf Friedrichshafen Ag Tilgersystem

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US11796032B2 (en) 2023-10-24
DE102019109020A1 (de) 2020-10-08
WO2020200356A1 (fr) 2020-10-08
CN113412382B (zh) 2024-07-23
CN113412382A (zh) 2021-09-17
US20220205509A1 (en) 2022-06-30
DE102019109020B4 (de) 2021-07-01

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