EP2872788A1 - Dispositif d'actionnement de double embrayage - Google Patents

Dispositif d'actionnement de double embrayage

Info

Publication number
EP2872788A1
EP2872788A1 EP13730193.3A EP13730193A EP2872788A1 EP 2872788 A1 EP2872788 A1 EP 2872788A1 EP 13730193 A EP13730193 A EP 13730193A EP 2872788 A1 EP2872788 A1 EP 2872788A1
Authority
EP
European Patent Office
Prior art keywords
component
dual
clutch
pressure chamber
dual clutch
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Withdrawn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
EP13730193.3A
Other languages
German (de)
English (en)
Inventor
Luben Krahtov
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 EP2872788A1 publication Critical patent/EP2872788A1/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Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • F16D2021/0669—Hydraulically actuated clutches with two clutch plates
    • 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
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0224—Details of conduits, connectors or the adaptors therefor specially adapted for clutch control

Definitions

  • the invention relates to a dual-clutch actuating device for a double clutch, which is adapted to hydraulically actuate an engaging device or disengaging device of a double clutch.
  • a dual-clutch actuating device is known, for example, from the company LuK Lamellen- und Kupplungsbau under the name CSC (Concentric Slave Cylinder). Due to the often small space available, it is necessary to build a double clutch operation very compact. To achieve this goal, a multifunctional or integral design of the dual clutch operation is sought. This leads to a component with often complex geometries. These can be produced economically only by plastic injection molding. However, a plastic element has the disadvantage of low strength. Due to the high pressures required to operate the hydraulic piston, the walls of such a plastic element must be made thick accordingly. As a result, an increased space is needed.
  • the present invention has the object, at least partially overcome the known from the prior art disadvantages.
  • the object is solved by the features of the independent claims.
  • Advantageous developments are the subject of the dependent claims.
  • the invention relates to a double-clutch actuating device for a double clutch, which has at least the following components:
  • At least one metallic component which the first pressure chamber and / or second
  • Pressure chamber forms
  • At least one supply element made of plastic, which forms a first supply line to the first pressure chamber and / or a second supply line to the second pressure chamber.
  • a dual-clutch actuator has two pressure chambers, via which in each case a piston is hydraulically actuated.
  • the two pressure chambers are each supplied separately with a hydraulic fluid via the respective separate supply lines.
  • the pressure in the pressure chambers is separately controllable.
  • an engagement device or a disengagement device of a friction clutch is actuated with the pistons, so that the friction elements of the clutch transmitting a torque are actuated by means of the hydraulic system. rule disengagement of the piston in the dual-clutch actuator are pressed or released.
  • the double-clutch actuator proposed here is divided into at least one component, preferably two components, of metal and at least one supply element, preferably a single supply element, made of plastic.
  • the here proposed double clutch actuator made of metal and plastic their production is simplified and significantly cheaper.
  • the pressure chambers are formed by the metal components, wherein the pressure chambers are supplied via the supply element.
  • a separate hydraulic supply for the respective pressure chamber takes place.
  • a pressure chamber has a hydraulic fluid inlet, an enclosed space having a base surface opposed to a piston driving surface, and side walls serving as a tread and sealing surface for a piston.
  • the pistons are advantageously arranged concentrically with one another.
  • the first pressure chamber is arranged on the outside and the second pressure chamber on the inside.
  • the components are preferably deep-drawn sheet metal parts. This not only allows a very cost-effective production compared to the production of injection-molded plastic, but due to the material, a significantly thinner-walled design than in a production of plastic. As a result, the size of the dual-clutch actuator can be reduced overall.
  • the supply element is made of plastic, the supply lines to the pressure chambers can be integrally formed. In a suitable arrangement, the supply element can be set up so that it does not have to absorb any or (in regions) only small, compressive loads, but the pressure loads are absorbed by the at least one component made of metal, or the at least one component made of metal, the supply element ( regionally) suitably supported.
  • the at least one supply element comprises at least one lateral connecting piece for a hydraulic line.
  • the connecting piece is an integrally formed (standardized and / or plastic) connecting piece for a hydraulic line.
  • a lateral connecting piece increases the complexity of a component due to undercuts and cavities. Due to the division of tasks of the components of the dual-clutch actuating device into the at least one component made of metal for pressure absorption and the at least one supply element, the required component complexity can be limited solely to the supply element. Even in such a very compact arrangement with lateral supply of hydraulics so that at least one metal component to form the first pressure chamber and the second pressure chamber can be made with a very low-complexity structure. Thus, despite increased assembly costs, the dual-clutch actuator can be made overall more cost-effective and with less space - among other things, because of the lateral supply of the hydraulic line.
  • the at least one supply element forms a receptacle with a seal for the at least one metal component.
  • the at least one component made of metal and the supply element are mutually arrangeable, without the need for further assembly measures are necessary.
  • the supply element can be constructed such that the recording reinforced by the pressure prevailing in the first pressure chamber and the second pressure chamber, the sealing effect and the supply element no or only a small compressive load must absorb, this pressure load receiving preferably in a necessary by the geometry as very stiff area is recorded.
  • the supply element in the region of a feed opening to the pressure chambers on a high depth - and thus stiffness - along the feed line, so that here a pressure load is not critical.
  • the supply element on the at least one component Metal are supported, so that the supply element itself does not have to be designed against the prevailing pressures.
  • the at least one component has a fastening device, and the Doppelkupp- lungsbetusch Incs Rhein can be mounted with the fastening device.
  • a fastening device can be provided, via which the entire dual-clutch actuating device can be mounted, for example, in a double clutch.
  • the attachment means may be formed, for example, as a thread or as through-holes for attachment for screws or the like.
  • the remaining components of the Doppelkupplungsbetuschistseinrich- device via the fastening device itself also clamped.
  • the at least one component is U-shaped and can be inserted into a corresponding groove in the supply element.
  • a metal U-shaped component already forms a closed chamber together with the drive surface of the piston.
  • the component has the U-shaped cross section with a distance (or radius) to a center of rotation and forms a shape that is pronounced of a Gugelhupf baking mold. If this component is inserted into a corresponding groove in the supply element, the supply function can be ensured via at least one bore in the metal component and at least one correspondingly arranged supply in the supply element, without the supply element having to absorb the pressure loads of the pressure chamber of the component, because the component forms a closed pressure chamber by its U-shape. Apart from the line pressure, the feed element thus receives no pressure loads.
  • the at least one component is L-shaped and the supply element can be inserted therein.
  • the component can, for example, a stop for the supply element, furthermore a fastening device. tion on the outer circumference and form a wall of one of the pressure chambers with the wall arranged perpendicular thereto.
  • the component is preferably a rotationally symmetrical component about the central axis of the dual-clutch actuating device, wherein the cross-section is L-shaped and is radially spaced apart.
  • this shape is reminiscent of a hollow shaft with end-to-end connection flange.
  • the dual clutch actuation device comprises a first component and a second component made of metal, wherein the first component is U-shaped and the second component L-shaped, and wherein the first pressure chamber formed by the U-shaped first component is and the second pressure chamber between an inner wall of the second component and an outer wall of the first component is formed.
  • the supply element is held between the first and the second component, so that the forces in the pressure chambers do not act on the supply element or the supply element is supported in the correspondingly loaded areas by the components.
  • the assembly is very simple by simply nesting.
  • the at least one component is provided by at least one adjusting element, in particular one
  • an adjusting element for the at least one metal component may be provided on the supply element.
  • the adjusting element is designed as a snap connection, so that the metal component is brought into position, adjusted and fixed solely by insertion into the supply element made of plastic.
  • the feed element preferably forms a barb which recoils during insertion and hooks in the end position and clearly defines the position of the component. This can, if internal stresses are allowed in the supply element, also be carried out with a multiple fit, so that the at least one component is firmly fixed in its adjusted position.
  • a second component can be mounted on the first component or the supply element via an adjusting element.
  • a double clutch for releasably connecting an output shaft to a drive train is proposed, which has at least the following components:
  • first friction pack and a second friction pack each having at least one pressure plate and at least one corresponding friction disc;
  • a dual-clutch actuator for actuating the first return device and the second return device, wherein in particular the dual-clutch actuator is mountable by fixing to the clutch housing.
  • a dual clutch is arranged for connecting an input shaft with one of two output shafts.
  • the first output shaft and the second output shaft are connected to a double gear and are each connected to alternately successive translations.
  • the switching time is reduced, because when releasing the connection with the first output shaft already the second output shaft or vice versa is switched on.
  • This is done via a first and a second friction pack, which are usually connected via friction plates with the first output shaft and the second output shaft respectively.
  • the pressure plate of the Reibevere is rotationally fixed to the input shaft.
  • a return device and a second return device are provided for actuating the friction packs or for pressing the pressure plate against a corresponding friction disc.
  • this return device When activated, this return device can release the connection or press the pressure plate against the friction plates.
  • the first and the second return device are actuated via the dual-clutch actuator according to the above description.
  • the dual-clutch actuator according to the above description takes only a small space, whereby the entire double clutch can be made with a smaller size.
  • the dual clutch operation can be mounted by fixing the static clutch housing. That is, the dual-clutch actuator can be pre-assembled or put together only in the dual-clutch arrangement and, for example, with the aid of the attachment coupling. device at the at least one component are assembled and fixed in total. This facilitates the assembly and increases the flexibility of the assembly order of the dual clutch operation, so that the assembly processes can be flexibly adjusted.
  • a motor vehicle which comprises a drive unit with an output shaft, a drive train and a dual clutch, wherein in particular the drive unit is arranged in front of a driver's cab in the motor vehicle and transversely to a longitudinal axis of the motor vehicle.
  • the drive unit for example an internal combustion engine or an electric motor
  • the drive unit for example an internal combustion engine or an electric motor
  • the installation space situation for passenger cars of the small car class according to European classification is exacerbated.
  • the units used in a passenger car of the small car class are not significantly reduced compared to passenger cars larger car classes. Nevertheless, the available space for small cars is much smaller.
  • the dual-clutch actuator described above is particularly suitable for use in small size double clutches, because this previously can be replaced space-tensive dual-clutch actuators and the rest of the converted parts can be adjusted and reduced accordingly.
  • Passenger cars are classified according to vehicle class according to, for example, size, price, weight, power, but this definition is subject to constant change according to the needs of the market.
  • vehicles of the class small cars and microcars are classified according to European classification of the class of subcompact car and in the British market they correspond to the class Supermini, for example, the class City Car.
  • Examples of the micro car class are a Volkswagen Fox or a Renault Twingo.
  • Examples of the small car class are an Alfa Romeo Mito, Volkswagen Polo, Ford Fiesta or Renault Clio.
  • Fig. 2 is a schematic of a dual clutch
  • Fig. 3 a motor vehicle with dual clutch.
  • a dual-clutch actuator 1 with a first component 3 and a second component 4, and a single supply element 5 is shown in section, in which the first component 3 is formed (in cross section) U-shaped and in a groove 15 of the supply element 5 is used.
  • the feed element 5 is inserted into the second component 4, which is (in cross section) L-shaped.
  • the first pressure chamber 6 of the first component 3 is supplied.
  • a first seal 10 is provided in the transition from the feed element 5 to the first component 3, a first seal 10 is provided.
  • the second pressure chamber 7 is supplied via the second connecting piece 13, which is indicated here by dashed lines, because this channel is not in the sectional plane shown.
  • the second pressure chamber 7 is formed by an inner wall 16 of the second component 4 and an outer wall 17 of the first component 3. Furthermore, the second pressure chamber 7 is sealed by a second seal 1 1 relative to the feed element 5.
  • a first piston 8 in the first pressure chamber 6 and a second piston 9 in the second pressure chamber 7 are indicated by dashed lines.
  • a fastening device 14 is shown in this illustration, which belongs to the second component 4 and can be connected via a through-hole 40 with the supply element 5 by mounting.
  • the first component 3 is held by an adjusting element 19, which is designed here as a snap connection, in the feed element.
  • FIG. 2 shows a diagram of a double clutch 2, which is actuated via a double clutch actuating device 1, as illustrated, for example, in FIG. 1.
  • the clutch housing 22 is an input shaft 23 which is rotatably fixed to the first pressure plate 28 of the second pressure plate 29 and the central web 38 is connected. Between the first pressure plate 28 and the central web 38, a first friction disc 30 is fixedly connected to the first output shaft 24. These form the first friction package 26. Accordingly, the second friction disc 32 is disposed between the second pressure plate 29 and the central web 38 and fixedly connected to the second output shaft 25. Thus, the second friction pack 27 is formed.
  • the pressure plates 28 and 29 are axially displaceable and are pressed via the first return device 32 and the second return device 33 against the first friction disk 30 and against the second friction disk 31, respectively.
  • the first return device 32 is actuated via the first piston 8 and the second return device 33 is actuated via the second piston 9.
  • the pistons 8 and 9 are supplied via the hydraulic line 18 in the dual-clutch actuator 1.
  • a motor vehicle 34 which has front of the cab 36 of a drive unit 20 which is connected via its output shaft 35 with a dual clutch 2 with a drive train 21 shown purely schematically.
  • the drive unit 20 is arranged with its motor axis transverse to the longitudinal axis 37 of the motor vehicle 34. Due to the smaller dimensions of the dual-clutch actuator 1 proposed here (not shown here), a significantly smaller dual clutch 2 can be built, so that in some cases small space in the motor vehicle 34, the use of a dual clutch 2 is possible for the first time.
  • the proposed here double clutch actuator can be made cheaper and built with the appropriate choice of material smaller than was possible with conventional dual clutch actuators.

Abstract

L'invention concerne un dispositif d'actionnement (1) destiné à un double embrayage (2), comportant au moins les composants suivants : • - au moins un composant métallique (3, 4) qui forme la première chambre de pression (6) et/ou la deuxième chambre de pression (7) ; • - au moins un élément d'amenée (5) en matière plastique qui forme une première conduite d'amenée (12) vers la première chambre de pression et/ou une deuxième conduite d'amenée (13) vers la deuxième chambre de pression. Le dispositif d'actionnement de double embrayage décrit ici peut être fabriqué plus économiquement et, en choisissant le matériau approprié, avec une plus petite taille que ce qui était possible avec les dispositifs d'actionnement de double embrayage conventionnels.
EP13730193.3A 2012-07-12 2013-06-14 Dispositif d'actionnement de double embrayage Withdrawn EP2872788A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012212189 2012-07-12
PCT/EP2013/062318 WO2014009098A1 (fr) 2012-07-12 2013-06-14 Dispositif d'actionnement de double embrayage

Publications (1)

Publication Number Publication Date
EP2872788A1 true EP2872788A1 (fr) 2015-05-20

Family

ID=48669921

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13730193.3A Withdrawn EP2872788A1 (fr) 2012-07-12 2013-06-14 Dispositif d'actionnement de double embrayage

Country Status (4)

Country Link
EP (1) EP2872788A1 (fr)
CN (1) CN104471268B (fr)
DE (2) DE102013211083A1 (fr)
WO (1) WO2014009098A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3053753B1 (fr) * 2016-07-06 2019-05-24 Valeo Embrayages Cylindre hydraulique recepteur pour un systeme de commande hydraulique
FR3089580B1 (fr) * 2018-12-07 2020-11-27 Valeo Embrayages Dispositif d’entretoisement pour mécanisme d’embrayage humide et mécanisme d’embrayage humide comprenant un tel dispositif d’entretoisement

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2789140B1 (fr) * 1999-01-29 2001-03-02 Valeo Dispositif de debrayage a commande hydraulique
AU7641300A (en) * 1999-08-24 2001-03-19 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Release system
JP5023372B2 (ja) * 2000-11-22 2012-09-12 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 クラッチ装置
DE10228051B4 (de) * 2001-06-28 2013-12-24 Schaeffler Technologies AG & Co. KG Hydraulisch betätigbares Ausrücksystem für Kraftfahrzeug-Reibungskupplung
EP1298339B1 (fr) * 2001-09-28 2004-03-10 ZF Sachs AG Arrangement d'accouplement multiple, notamment embrayage double
JP2004308708A (ja) * 2003-04-03 2004-11-04 Exedy Corp クラッチ操作機構
ATE356943T1 (de) * 2004-03-31 2007-04-15 Luk Lamellen & Kupplungsbau Hydraulisches kupplungsbetätigungssystem
DE502005006048D1 (de) * 2004-09-03 2009-01-08 Luk Lamellen & Kupplungsbau Drehmomentübertragungseinrichtung
DE102009050346B4 (de) * 2008-11-17 2019-08-08 Schaeffler Technologies AG & Co. KG Kupplungsausrücksystem mit Verdrehsicherung für Nehmerzylinderkolben
DE102009056378B4 (de) * 2008-12-22 2019-05-23 Schaeffler Technologies AG & Co. KG Kupplungsbetätigungssystem
DE102010032661A1 (de) * 2009-08-20 2011-02-24 Schaeffler Technologies Gmbh & Co. Kg Ausrücksystem für eine Doppelkupplung
GB2473869A (en) * 2009-09-28 2011-03-30 Gm Global Tech Operations Inc Casing for a dual clutch actuation device of a transmission
GB2474517A (en) * 2009-10-19 2011-04-20 Gm Global Tech Operations Inc A clutch actuation device for a dual clutch including concentric slave cylinders

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
None *
See also references of WO2014009098A1 *

Also Published As

Publication number Publication date
DE112013003471A5 (de) 2015-03-19
CN104471268A (zh) 2015-03-25
WO2014009098A1 (fr) 2014-01-16
CN104471268B (zh) 2017-08-15
DE102013211083A1 (de) 2014-01-16

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