EP2875249A1 - Embrayage double - Google Patents

Embrayage double

Info

Publication number
EP2875249A1
EP2875249A1 EP13750628.3A EP13750628A EP2875249A1 EP 2875249 A1 EP2875249 A1 EP 2875249A1 EP 13750628 A EP13750628 A EP 13750628A EP 2875249 A1 EP2875249 A1 EP 2875249A1
Authority
EP
European Patent Office
Prior art keywords
carrier
friction
clutch
double clutch
carriers
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Withdrawn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
EP13750628.3A
Other languages
German (de)
English (en)
Inventor
Stephan Maienschein
Thorsten Krause
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 EP2875249A1 publication Critical patent/EP2875249A1/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Withdrawn legal-status Critical Current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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F16D25/087—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation the clutch being actuated by the fluid-actuated member via a diaphragm spring or an equivalent array of levers
    • 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
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
    • F16D2021/0615—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate is supported by bearings in-between the two clutches
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches
    • 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
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0692—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric with two clutches arranged axially without radial overlap

Definitions

  • the invention relates to a double clutch.
  • the invention relates to a dual clutch for use in a drive train of a motor vehicle.
  • a drive train of a motor vehicle comprises a drive motor and a gearbox with multiple gear stages.
  • a double clutch is arranged between the drive motor and the transmission to release the frictional connection from the drive motor to a first engaged gear and close at the same time to a second engaged gear.
  • the transmission has two different transmission input shafts, each associated with a group of gear stages.
  • the dual clutch may be constructed radially, with a clutch disposed radially within the other clutch, or axially, wherein the two clutches are axially offset.
  • Each of the clutches is usually constructed as a friction disc clutch, the dry or can run in an oil bath.
  • Single or multiple disc clutches can be used. In particular, to build an axial double clutch as compact as possible, different proposals have been made.
  • a dual clutch according to the invention comprises a first friction disc clutch with a first and a second friction partner and a second friction disc clutch with a third and a fourth friction partner.
  • the friction disc clutches are arranged axially relative to one another, the second and third friction partners being mounted so as to be stable in rotation with respect to one another.
  • the second friction partner is a first carrier and the third friction partner associated with a separate second carrier and the two carriers are rotatably connected to each other.
  • the manufacturability of the double clutch can be improved.
  • the carriers of the friction disc clutches can be individually easier and cheaper to produce, so that the double clutch can be produced at a reduced cost.
  • the carriers are identically shaped and arranged in opposite axial orientations. The use of only one type of carrier for both carriers can result in further cost advantages in the production of the dual clutch. A stockpiling for elements or spare parts of the double clutch can be facilitated.
  • a recess for passing a liquid medium may be provided between the carriers.
  • a radial channel may be formed to guide the medium.
  • the liquid medium may in particular comprise oil which circulates for cooling, lubrication and removal of particles through the double clutch.
  • the medium can be passed through the recess in an improved manner in a radially outer region, where the friction partners when opening or closing produce a frictional connection, which brings with it an attack of frictional heat.
  • the medium can absorb and dissipate this heat. A load and wear resistance of the friction partners can be improved.
  • the dual clutch comprises an input side with a toothing and the first carrier has a corresponding toothing, which engages in the toothing of the input side.
  • the first friction disc clutch comprises a plurality of disks and friction disks or disks of the first friction disk clutch engage in the toothing of the first carrier in a torque-locking and axially displaceable manner.
  • the toothing of the first carrier can then be used in addition for the engagement of the flanges, whereby the symmetrical structure of the two carriers is supported. Separate means for introducing a torque in one of the carrier can be omitted.
  • a mass element can be arranged between the carriers.
  • the mass element can contribute by its physical mass to dampen or reduce torsional vibrations in the drive train or serve as a flywheel for a drive motor, which can be connected to the input side.
  • the mass element may also act as a thermal mass to dampen temperature variations on the coupling or to compensate for unequal heating of different sections.
  • the mass element can also serve for mechanical stiffening of the coupling.
  • the mass member extends radially inwardly to a bearing member to radially support the first and second supports with respect to the bearing member.
  • the rotational movement of the interconnected carrier can thus be stabilized in a simple manner in the radial direction.
  • one of the beams includes a radial and an axial portion, and the radial portion forms part of the second and fourth friction partners, respectively.
  • the radial section may comprise a bearing point for supporting a lamella or a friction disk of the second or fourth friction partner.
  • the carriers can each be produced from a sheet metal.
  • the sheet can be made, for example, by means of stamping, pressing or bending in a suitable form, whereby the carrier can be inexpensively made dimensionally stable.
  • the carriers are connected to each other axially by means of a riveted joint.
  • the carriers can be easily manufactured individually and then connected to each other inexpensively.
  • the connection of the carrier can be made in this way precise, durable and inexpensive.
  • the rivet connection can extend axially, so that the riveting operation can be carried out easily.
  • Figure 1 shows a half section through a double clutch
  • Figure 2 shows a half section through a double clutch of Figure 1 with a
  • Figure 4 shows a half section through a double clutch of Figure 1 with an axial
  • FIGS. 1 to 4 show double clutches of different embodiments whose deviating features can be freely combined with one another. However, since most features can be found in all embodiments, their explanation will be given only with reference to one of the figures 1 to 4.
  • FIG. 1 shows a dual clutch 100 for use in a drive train of a motor vehicle.
  • the dual clutch 100 includes an input side 102 for connection to a drive motor, in particular an internal combustion engine, and a first output side 104 and a second output side 106, each configured for connection to input shafts of a dual clutch transmission.
  • a housing 108 is provided, which in the illustrated embodiment is designed in two parts with an axial dividing plane.
  • the dual clutch 100 comprises two friction disc clutches in an axial arrangement.
  • a first friction disk clutch 1 10 comprises a first friction partner 1 12 and a second friction partner 1 14, which may each be carried out several times. Between adjacent friction partners 1 12 and 1 14 a friction lining 1 16 is preferably provided, which is fixedly attached to one of the friction partners 1 12, 1 14.
  • the first friction partners 1 12 is associated with a first carrier 1 18, which comprises a radial portion 120 and an axial portion 122. At the axial portion 122, a radial toothing 124 is attached.
  • the first friction partners 1 12 engage in the toothing 124 to be connected to the first carrier 1 18 torque liquid and axially displaceable.
  • a corresponding toothing exists between the second friction partner 1 14 and a further carrier 126, which is non-positively connected to the first output side 104.
  • a second friction disc clutch 130 is constructed analogously to the first friction disc clutch 1 10.
  • the second friction disk clutch 130 comprises third friction partners 132 and fourth friction partners 134, between which friction linings 136 can be arranged in the axial direction.
  • a second carrier 138 comprises a radial portion 140 and an axial portion 142, to which a toothing 100 is mounted, in which the third friction partners 132 engage.
  • the fourth friction partners 134 engage by means of a further toothing in a further carrier 146 which provides a positive connection to the second output side 106.
  • the first carrier 1 18 and the second carrier 138 are produced separately, preferably each of a sheet metal.
  • the beams 1 18 and 138 are congruently shaped so that they are interchangeable.
  • the carrier 1 18 and 138 are aligned in anti-parallel, so that the radial portions 120 and 140 facing each other and the axial portions 122, 142 facing away from each other.
  • the supports 1 18 and 138 are connected to one another in a rotationally stable manner, preferably by means of a rivet connection 150 which extends axially in the region of the radial sections 120 and 140.
  • the input side 102 comprises a flange 160 which extends radially outwards as far as the first carrier 118. At its radial outer side, the flange 160 carries a toothing 162 which engages in the toothing 124 of the first carrier 1 18.
  • the gears 124 and 162 ensure that the dual clutch 100 is easily mountable in the axial direction.
  • a first axial actuator 170 and a second axial actuator 172 are provided.
  • hydraulic actuators 170, 172 with axially displaceable piston 174 and 176 which can be moved by a hydraulic pressure axially in the direction of the carrier 1 18 and 138 to the first Reibusionnkupplung 1 10 and the second To close the friction disc clutch 130. It is also possible to close the friction disk clutches 1 10, 130 by means of a spring element and to open them by means of the respective actuating device 170, 172. In other embodiments, the actuators 170, 172 may be actuated differently, for example by means of an electrical actuator, an eccentric, a lever or a Bowden cable.
  • FIG. 2 shows a half section through the double clutch 100 according to FIG. 1 in a further embodiment.
  • an optional mass element 202 is provided, which is arranged and fastened in a radially outer region between the carriers 110 and 130. Otherwise, the illustrated embodiment is similar to that of FIG. 1.
  • the radial portions 120 and 140 of the carriers 110 and 130 abut one another such that they form a radial channel 204 for guiding a liquid medium 206 which circulates within the housing 108 for cooling, lubricating and cleaning the double clutch 100.
  • the passage 204 includes a first passage 208 and at least one second passage 210.
  • the first passage 208 leads to a first axially and then radially extending bore of the first output side 104. Through this bore, the dual clutch 100 is supplied with fresh medium 206 be, for example by using a pump.
  • the first passage 208 is formed between the carriers 1 10 and 130, while in the illustrated embodiment, two second passages 210 each through one of the carrier 1 10, 130 lead.
  • the medium can flow radially outwards between the first carrier 110 and the further carrier 126 or between the second carrier 130 and the further carrier 146 and into the region of the friction partners 112 and 114 or 132 and enter.
  • the medium can then leave the region in the axial direction or in the axial direction through a third passage 212, which in the axial section 122 of the first carrier 1 10 or in the axial portion 142 of the second carrier 130 may be provided.
  • the third passage 212 may also be part of the channel 204.
  • FIG. 3 shows a half section through the double clutch 100 according to FIG. 2 with a radially extended mass element 202.
  • the mass element 202 extends in the radial direction as far as a bearing element 302, which is supported here in relation to the first output side 104. In the embodiments of FIGS. 1 and 2, this radial extent and the bearing function can take place through corresponding sections of the first carrier 1 18 or of the second carrier 138.
  • thrust bearings 304 are in the embodiments of Figures 1 and 2 preferably between the carrier 1 18 and the other carrier 126 and the carrier 130 and the other carrier 146. Furthermore, thrust bearings 304 are preferably on the respective opposite axial sides of the other carrier 126 and 146 arranged to the arrangement of the carriers 1 18, 138, 126 and 146 axially to the left or
  • One of the thrust bearings 304 is axially supported on the housing 108 in the illustrated embodiment, the other on the input side 102nd
  • FIG. 4 shows a half section through yet another embodiment of the dual clutch 100 according to FIG. 1. While in the embodiments of FIGS. 1 to 3 the radial sections 120 and 140 of the beams 1 10 and 130 are each encompassed by the third friction partners 132, in the embodiment shown in FIG. 4 there is instead in each case a dedicated friction partner 1 12 or 132 provided, which is supported relative to the respective radial portion 120 and 140, respectively.
  • an axial support 402 is provided in each case, which is preferably integrally formed with the radial portions 120 and 140 of the carrier 1 18 and 138, respectively.
  • the supports 402 can each be formed by a corresponding bead. It can also be provided only one support 402 on one of the friction disk clutches 1 10, 130. LIST OF REFERENCES

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

Embrayage double qui comporte un premier embrayage à disque de friction pourvu d'un premier partenaire de friction et d'un deuxième partenaire de friction et un second embrayage à disque de friction pourvu d'un troisième partenaire de friction et d'un quatrième partenaire de friction. Les embrayages à disque de friction sont disposés axialement l'un par rapport à l'autre, les deuxième et troisième partenaires de friction étant montés stables en rotation l'un par rapport à l'autre. Un premier support est associé au deuxième partenaire de friction et un deuxième support séparé est associé au troisième partenaire de friction, les deux supports étant reliés l'un à l'autre de manière stable en rotation.
EP13750628.3A 2012-07-20 2013-07-17 Embrayage double Withdrawn EP2875249A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102012212807 2012-07-20
DE102012215919 2012-09-07
DE102013208051 2013-05-02
PCT/DE2013/200059 WO2014012542A1 (fr) 2012-07-20 2013-07-17 Embrayage double

Publications (1)

Publication Number Publication Date
EP2875249A1 true EP2875249A1 (fr) 2015-05-27

Family

ID=49000749

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13750628.3A Withdrawn EP2875249A1 (fr) 2012-07-20 2013-07-17 Embrayage double

Country Status (4)

Country Link
EP (1) EP2875249A1 (fr)
CN (1) CN104428548B (fr)
DE (2) DE102013213983A1 (fr)
WO (1) WO2014012542A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170108054A1 (en) * 2014-03-27 2017-04-20 Schaeffler Technologies AG & Co. KG Sheet metal pressure plate and pressure pot as joint component
FR3025271B1 (fr) * 2014-09-03 2016-11-04 Valeo Embrayages Systeme de transmission comportant un mecanisme a double embrayage humide
FR3049024B1 (fr) * 2016-03-16 2019-04-26 Valeo Embrayages Double embrayage humide avec butees de securite aptes a limiter la course des pistons du systeme de commande
FR3075291B1 (fr) * 2017-12-18 2020-08-07 Valeo Embrayages Piston en deux parties, le piston etant destine a equiper un mecanisme d'embrayage
FR3080158A1 (fr) * 2018-04-16 2019-10-18 Valeo Embrayages Dispositif de transmission pour vehicule hybride
DE102018130331A1 (de) * 2018-09-26 2020-03-26 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung
DE102019120151B3 (de) * 2019-07-25 2020-09-10 Schaeffler Technologies AG & Co. KG Doppel-Kupplungseinheit für ein Schaltgetriebe

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10323514A1 (de) * 2003-05-24 2004-12-23 Dr.Ing.H.C. F. Porsche Ag Kupplungsvorrichtung, insbesondere Lamellenkupplung für ein Doppelkupplungsgetriebe
EP1686276B1 (fr) * 2005-01-27 2017-07-26 Getrag Ford Transmissions GmbH Embrayage double avec âme intermédiaire
JP5661743B2 (ja) * 2009-05-06 2015-01-28 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフトＳｃｈａｅｆｆｌｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ ＡＧ ＆ Ｃｏ． ＫＧ トーショナルバイブレーションダンパを備えるツインクラッチ
DE102011104247A1 (de) * 2010-06-29 2011-12-29 Schaeffler Technologies Gmbh & Co. Kg Doppelkupplungsanordnung
DE102010046633B4 (de) * 2010-09-20 2012-10-18 Gkn Stromag Ag Doppelschaltkupplung

Also Published As

Publication number Publication date
CN104428548B (zh) 2018-10-26
DE112013003617A5 (de) 2015-04-23
DE102013213983A1 (de) 2014-01-23
WO2014012542A1 (fr) 2014-01-23
CN104428548A (zh) 2015-03-18

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