EP3094884A2 - Dispositif de transmission de couple - Google Patents

Dispositif de transmission de couple

Info

Publication number
EP3094884A2
EP3094884A2 EP14828134.8A EP14828134A EP3094884A2 EP 3094884 A2 EP3094884 A2 EP 3094884A2 EP 14828134 A EP14828134 A EP 14828134A EP 3094884 A2 EP3094884 A2 EP 3094884A2
Authority
EP
European Patent Office
Prior art keywords
transmission device
torque transmission
friction
torque
flange
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Withdrawn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
EP14828134.8A
Other languages
German (de)
English (en)
Inventor
Vincent Fender-Oberle
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 EP3094884A2 publication Critical patent/EP3094884A2/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Withdrawn legal-status Critical Current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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
    • F16D7/025—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs
    • 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
    • F16F15/139—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 characterised by friction-damping means
    • F16F15/1397—Overload protection, i.e. means for limiting torque
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F16D2013/703—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members the pressure plate on the flywheel side is combined with a damper

Definitions

  • the invention relates to a torque transmission device, in particular for
  • a hybrid powertrain in automobiles includes at least two energy converters and two in-vehicle energy storage systems to power the vehicle.
  • one of the energy converters is an internal combustion engine, usually a gasoline or diesel engine, and a second energy converter is an electric motor.
  • the energy storage systems are accordingly a fuel tank and an electric accumulator.
  • a torque transmission device comprising a primary side and a secondary side, which are connected to one another via an energy store and which are rotatable relative to one another against the force of the energy accumulator, is known per se as a dual mass flywheel (DMF). If such a dual mass flywheel is arranged in the drive train of a hybrid drive, torque peaks (impacts) can occur, which can lead to a failure of individual components and thus a failure of the entire drive train.
  • DMF dual mass flywheel
  • An object of the invention is therefore to avoid damage to the drive train by torque peaks.
  • a torque transmission device in particular for use in a hybrid drive of a motor vehicle, comprising a primary side and a secondary side, which are connected to each other via an energy store and which are rotatable relative to each other against the force of the energy store, wherein the torque transmitting device a Includes means for limiting the transmittable torque.
  • the means for limiting the transmittable torque is arranged in an embodiment of the invention on the secondary side, in particular on a secondary flange of the torque transmission device.
  • the energy storage comprises in one embodiment of the invention, one or more designed as compression springs bow springs, which are supported with a spring end on the primary side and the other end of the spring on the secondary side.
  • the bow springs With relative rotation of the primary side relative to the secondary side, the bow springs are tensioned and thus store energy that is released again when reversing.
  • the bow springs may have a linear spring characteristic, but may also have gradually increasing spring characteristics, for example by coaxially arranged inner and outer coil springs of different spring length.
  • friction elements can be arranged between the primary side and the secondary side, which dissipate energy during a relative rotation of the primary side relative to the secondary side by dry or viscous friction.
  • the primary side forms a primary mass, the secondary side corresponding to a secondary mass.
  • the repayment effect of the torque transmission device is essentially determined by the moments of inertia of primary mass and secondary mass and the spring stiffness of the energy storage.
  • the means for limiting the transmittable torque is a slip clutch in one embodiment of the invention.
  • a slip clutch is an automatic torque-switching clutch. When a maximum torque or switching torque is reached, the clutch at least partially disconnects the torque transmission without external influence.
  • the slip clutch is a friction clutch with adhesion between the primary side and the secondary side. The adhesion is achieved by static friction between two friction partners. If the static friction is overcome, the clutch opens. The drag torque transmitted after opening the clutch depends on the sliding friction between the friction partners and the relative speed between them. The drag torque is always lower than the switching torque.
  • the slip clutch in one embodiment of the invention comprises a secondary flange which is arranged between two output-side jaws.
  • the output side jaws clamp the secondary flange, so their surfaces are pressed onto the secondary flange with an axial compressive force. This is preferably done by the output side jaws form a circumferential groove into which the secondary flange engages without play in the manner of a press fit.
  • the axial contact pressure of the output-side jaws on the secondary flange is thus determined by the thickness of the secondary flange and the corresponding width of the groove formed between the output-side jaws and the elasticity of the base. and the secondary flange.
  • the axial contact force causes a frictional connection (adhesion) between the secondary flange and the output side jaws.
  • the friction clutch formed by the secondary flange and the output-side jaws opens and only transmits the drag torque determined by the sliding friction between the secondary flange and the output-side jaws.
  • the output-side jaws are formed by a friction flange and a Reiballeflansch, which form a circumferentially circumferential groove into which protrudes the friction element.
  • Output hub connected, in particular riveted. This allows a production of the output side jaws as punching bending components that can be easily and inexpensively manufactured.
  • a secondary additive mass is riveted together with the output-side jaws with the output hub. The additional mass increases the mass moment of inertia of the secondary side.
  • a friction lining is arranged in one embodiment of the invention, at least between one of the jaws and the secondary flange.
  • the friction lining can be glued or riveted.
  • At least one seal is arranged between the secondary side and the primary side.
  • the seal comprises at least one sealing ring and may comprise further sealing elements such as a sealing disc.
  • the seal seals the spring assembly and the slip clutch from the environment.
  • a sealing ring of the seal have the function of a friction ring, with relative rotation between the primary side and secondary side energy is dissipated by friction.
  • Fig. 1 shows an embodiment of a torque transmission device according to the invention in a sectional view.
  • the torque transmission device 1 shown in section in FIG. 1 is arranged between a drive shaft 2 and a torque transmission shaft 3.
  • the torque transmission device 1 transmits a drive torque from the drive shaft 2 to the
  • Torque transmission shaft 3 and serves the damping or eradication of torsional vibrations.
  • the torque transmission device 1 comprises a primary side 4, which is fixedly connected to the drive shaft 2, and a secondary side 5, fixed to the
  • Torque transmission shaft 3 is connected.
  • the primary side comprises a primary flange 6 which, together with an outer ring 7, forms a receiving space 8 for receiving a spring arrangement 9 as an energy store.
  • the primary flange 6 comprises a substantially disc-shaped region 10, which merges in its radially outer region into a cup-shaped region 11 extending essentially in the axial direction with respect to the axis of rotation R.
  • the axial direction parallel to the axis of rotation R, the radial direction perpendicular thereto and the circumferential direction is a rotation about the axis of rotation R.
  • the outer ring 7 is welded, for example with a circumferential seam.
  • the cup-shaped region 11 in corresponding seats carries a first additional mass 13 and a second additional mass 14. Both the first additional mass 13 and the second additional mass 14 can be welded to the cup-shaped region 11, but can also have an interference fit.
  • the primary flange 6 is preferably a stamped steel bending member.
  • the outer ring 7 comprises in its radially outer region a substantially extending in the radial direction mounting portion 7a, which merges into a seen from the view of the receiving space 8 convexly curved portion 7b and a radially inwardly adjoining region 7c.
  • the primary flange 6 is screwed to the drive shaft 2 with screws 15 which are arranged distributed over the circumference.
  • a roller bearing 16 is mounted with its bearing outer ring.
  • the rolling bearing 16 is for example a ball bearing.
  • the bearing inner ring of the bearing 16 takes a bearing pin 18 of
  • Torque transmission shaft 3 connected.
  • the output hub 20 is part of the secondary side. 5
  • a Reibflansch 21 and a Reiballeflansch 22 are by means of rivets 23 with the
  • Output hub 20 riveted.
  • the friction flange 21 and the Reiballeflansch 22 are arranged on the drive shaft 2 facing side of a receiving portion 24 of the output hub 20.
  • a secondary additive mass 25 is arranged, which is also riveted to the rivets 23 to the output hub 20.
  • bores 26 are introduced into the primary flange 7.
  • the friction flange 21 comprises a fastening region 27, which is riveted to the output hub 20 by means of the rivet 23, and by means of a crank 28 in the direction of the
  • the Reibumbleflansch 22 includes a mounting portion 30 and a means of a crank 31 in the direction of the drive shaft 22 axially offset portion 32.
  • the respective opposite the mounting portions 27, 30 axially offset regions 29, 32 form a circumferential annular groove 33, into which a friction element 34 of a secondary flange 35 protrudes.
  • the friction element 34 is in dry friction with the friction flange 21 and the Reiballeflansch 22, so it is frictionally connected with these.
  • the friction flange 21 and the Reiballeflansch 22 form output side jaws, between which the friction element 34 is arranged.
  • the friction element 34 is clamped between the friction flange 21 and the Reiballeflansch 22, so it acts in the axial direction of a normal force as a compressive force on the friction member 34 so that in the circumferential direction results in a frictional or non-positive connection between the secondary flange 35 and the output hub 20.
  • the compressive force is generated by the axial width (if the friction member 34 would not be disposed in the annular groove 33) of the circumferential annular groove 33 is less than the axial thickness of the friction element 34, so that there is an interference fit during assembly.
  • a second friction lining 37 is arranged, between the Reibumbleflansch 22 and the friction member 34.
  • the first friction lining 36 may either be firmly connected to the friction flange 21 or fixedly connected to the friction element 34
  • the second friction lining 37 may either be firmly connected to the Reiballeflansch 22 or be firmly connected to the friction member 34.
  • the friction linings 36, 37 increase the static friction and / or sliding friction between the friction partners and reduce or prevent excessive wear of friction element 34 and friction flange 21 as well as friction flange 22.
  • the secondary flange 35 um- includes in addition to the annular peripheral friction element 34 radially outwardly extending flange nose 38, which are respectively supported at spring ends of bow springs 39, which are part of the spring assembly 9.
  • the bow springs 39 are based on the respective other spring end of projections or lugs of the primary flange 6, not shown.
  • the bow springs 39 may, as shown in Fig. 1, consist of an outer bow spring 39a and a coaxially arranged inner bow spring 39b, but may also consist of a single bow spring.
  • the spring assembly 9 comprises a plurality of circumferentially distributed bow springs 39, usually two bow springs 39 and two outer bow springs 39a and inner bow springs 39b are arranged here.
  • an outer sealing ring 40 which consists of two legs arranged at right angles to each other, wherein one of the legs is fixedly connected to the axially offset portion 39 of the Reibflansches 21 and the other leg in Frictional contact with the friction element 34 is. Furthermore, a sealing washer 41 is fastened to the axially offset region 29 of the tire flange 21. The sealing disc 41 is with its radially outer edge with the inner portion 7c of the outer ring 7 in contact, thus sealing the receiving space 8 from the environment. By means of a mounting plate 42, an inner sealing ring 43 is attached to the primary flange 6.
  • the mounting plate 42 is fastened by means of the screws 15 to the primary flange 6.
  • the mounting plate 42 includes a mounting portion 44 with distributed over the circumference holes for receiving the screws 15, which merges by means of a crank 45 in an at least partially circumferential retaining lug 46.
  • the inner sealing ring 43 is in frictional contact with the primary flange 6 with a first end face 47 and in frictional contact with the fastening area 27 of the friction flange 21 with a second end face 48.
  • a toothing can also be provided between the fastening area 30 of the friction flange 22 and the damping ring 43 be so that a frictional contact substantially only on the first end face 47 with the primary flange 6 comes about because on the opposite side in the circumferential direction a positive connection is present.
  • the secondary side 5 can be rotated relative to the primary side 5 against the spring force of the spring arrangement 9.
  • the spring assembly 9 forms an energy storage or energy storage, which receives 5 energy at a relative rotation between the primary side 4 and secondary side and this gives off in a reverse rotation to the starting position again.
  • the damping ring 43 ensures damping by dry friction.
  • the friction element 34 forms with the Reibflansch 21 and the fixedly connected to the Reibflansch 21 Reibisseflansch 22 a slip clutch 49, which limits the transferable between the secondary flange 35 and output hub 20 torque.
  • the torque to be transmitted between the secondary flange 35 and the output hub 20 exceeds a maximum torque (switching moment) determined by the geometry, the preload between the friction flange 21 and the friction flange 22 relative to the friction element 34, the friction element 34 and thus the secondary flange 35 slip relative to the friction flange 21 and Reiballeflansch 22 and thus the output hub 20 against the force of the then existing sliding friction between said friction partners and the slip clutch 49 opens automatically, so that only one determined by the sliding friction drag torque is transmitted.
  • the maximum transmittable by the torque transmission device 1 torque is limited because after exceeding the maximum torque, the slip clutch 49 slips and prevents further increase in the transmitted torque.

Landscapes

  • 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)
  • Motor Power Transmission Devices (AREA)

Abstract

L'invention concerne un dispositif de transmission de couple s'utilisant en particulier dans une motorisation hybride d'un véhicule à moteur, qui comprend un côté primaire et un côté secondaire, reliés l'un à l'autre par un accumulateur d'énergie et qui peuvent subir une torsion l'un par rapport à l'autre à l'encontre de la force exercée par l'accumulateur d'énergie. Un éventuel endommagement dû à des pics de couple est évité du fait que le dispositif de transmission de couple comprend un moyen pour limiter le couple transmissible.
EP14828134.8A 2014-01-17 2014-11-26 Dispositif de transmission de couple Withdrawn EP3094884A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014200798 2014-01-17
PCT/DE2014/200658 WO2015106746A2 (fr) 2014-01-17 2014-11-26 Dispositif de transmission de couple

Publications (1)

Publication Number Publication Date
EP3094884A2 true EP3094884A2 (fr) 2016-11-23

Family

ID=52391726

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14828134.8A Withdrawn EP3094884A2 (fr) 2014-01-17 2014-11-26 Dispositif de transmission de couple

Country Status (4)

Country Link
EP (1) EP3094884A2 (fr)
CN (1) CN105917131B (fr)
DE (1) DE112014006187A5 (fr)
WO (1) WO2015106746A2 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016205123B4 (de) 2016-03-29 2023-08-17 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung
DE102016209821A1 (de) * 2016-06-03 2017-12-07 Zf Friedrichshafen Ag Schwungscheibe
FR3057313B1 (fr) * 2016-10-06 2019-11-01 Valeo Embrayages Composant pour systeme de transmission de vehicule
DE102017107995A1 (de) * 2017-04-13 2018-10-18 Schaeffler Technologies AG & Co. KG Als Zweimassenschwungrad aufgebauter Drehschwingungsdämpfer
DE102018109464A1 (de) * 2017-05-17 2018-11-22 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
DE102017119375B4 (de) 2017-08-24 2024-03-21 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
DE102018124860A1 (de) * 2018-10-09 2020-04-09 Schaeffler Technologies AG & Co. KG Drehschwingungsdämpfer
WO2020078513A1 (fr) * 2018-10-16 2020-04-23 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations de torsion
DE102018218549A1 (de) * 2018-10-30 2020-04-30 Zf Friedrichshafen Ag Drehschwingungsdämpfungsanordnung
DE102021213136A1 (de) 2021-11-23 2023-05-25 Zf Friedrichshafen Ag Drehschwingungsdämpfungsvorrichtung für einen Antriebsstrang eines Kraftfahrzeugs

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0304577B1 (fr) * 1984-07-19 1994-04-20 Aisin Seiki Kabushiki Kaisha Dispositif d'amortissement des variations du couple
JP3378097B2 (ja) * 1994-09-29 2003-02-17 本田技研工業株式会社 摩擦クラッチ
US8398492B2 (en) * 2008-10-30 2013-03-19 Aisin Aw Industries Co., Ltd. Damper having torque limiter function
DE102010025579B4 (de) * 2009-07-27 2022-03-03 Schaeffler Technologies AG & Co. KG Drehmomentübertragungseinrichtung und Verfahren zur Montage einer Drehmomentübertragungseinrichtung
WO2011076175A1 (fr) * 2009-12-21 2011-06-30 Schaeffler Technologies Gmbh & Co. Kg Dispositif à connexion à fiches
JP5772098B2 (ja) * 2011-03-15 2015-09-02 アイシン精機株式会社 トルク変動吸収装置
DE102013202686A1 (de) * 2012-03-16 2013-09-19 Schaeffler Technologies AG & Co. KG Reibungskupplung mit Fliehkraftpendel

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
None *
See also references of WO2015106746A2 *

Also Published As

Publication number Publication date
WO2015106746A3 (fr) 2016-02-04
CN105917131B (zh) 2019-06-18
CN105917131A (zh) 2016-08-31
WO2015106746A2 (fr) 2015-07-23
DE112014006187A5 (de) 2016-10-20

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