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WO2008138506A1 - Dispositif double-embrayage à chevauchement axial court de la chambre de travail et de la chambre de compensation - Google Patents

Dispositif double-embrayage à chevauchement axial court de la chambre de travail et de la chambre de compensation Download PDF

Info

Publication number
WO2008138506A1
WO2008138506A1 PCT/EP2008/003573 EP2008003573W WO2008138506A1 WO 2008138506 A1 WO2008138506 A1 WO 2008138506A1 EP 2008003573 W EP2008003573 W EP 2008003573W WO 2008138506 A1 WO2008138506 A1 WO 2008138506A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
piston
input shaft
space
main hub
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.)
Ceased
Application number
PCT/EP2008/003573
Other languages
German (de)
English (en)
Inventor
Hans Jürgen Hauck
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.)
BorgWarner Inc
Original Assignee
BorgWarner Inc
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 BorgWarner Inc filed Critical BorgWarner Inc
Publication of WO2008138506A1 publication Critical patent/WO2008138506A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • 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
    • F16D2021/0661—Hydraulically actuated multiple lamellae clutches

Definitions

  • the invention relates to a clutch system for motor vehicle drives with a clutch input shaft and at least one transmission input shaft, which are all arranged concentrically to a clutch center line, wherein the transmission input shaft is connected via an actuated dip-lubricated friction clutch to the clutch input shaft, wherein the friction clutch between a fixed on a main hub Outer disk carrier and an inner disk carrier lying disc set comprises, wherein the disk set is operated for coupling directly or indirectly via at least one piston of a hydraulic actuator, wherein at least one piston separates a working space of a compensation chamber, the piston with its radially outer guide contour on a cylindrical portion a piston attached to the main hub Aus GmbHsraumbegrenzungswandung is sealingly guided and wherein the piston with its radially inner guide contour in the Main hub is sealingly guided.
  • the piston with its radially inner guide contour is sealingly guided on a cylinder ring arranged on the main hub.
  • the radially inward compensation chamber boundary wall protrudes into the installation space of the cylinder ring.
  • the Austiciansraumbegrenzungs- wall has at least one overflow recess whose shortest distance to the coupling center line is smaller than the distance of the guide surface of the cylinder ring to the coupling centerline.
  • the object of the invention is, in at least one coupling of the coupling system, the working space and the
  • Figure 1 partial longitudinal section through a double clutch
  • FIG. 1 Figure 1 with further details.
  • FIG. 1 shows a double clutch with two dip-lubricated and -cooled friction clutches 50, 150. These non-positive clutches have two radially successively arranged disk packs 55, 155. Accordingly, the first disk set 55 sits on a larger radius than the second 155. The two clutches 50th , 150 are hydraulically closed. Solving the individual
  • Clutch 50, 150 via spring elements and / or hydraulically via corresponding cylinder-piston units.
  • the spring elements 100, 200 are, for example, mechanical springs, such as coil springs and / or diaphragm springs.
  • This clutch system is usually used in passenger cars. The clutch system sits between a multi-shaft gearbox and the drive motor of the vehicle. The drive motor is usually a gasoline or diesel engine. Between the drive motor and the clutch system, a single or dual mass flywheel 3 is often mounted.
  • the clutch system Since the clutch system has a large diameter, it is arranged in the Geretegehause Scheme, which is referred to as bell housing 10.
  • the engine torque passes from the crankshaft to the flywheel 3, see. Figure 1.
  • the latter sits on a torsionally rigid shaft-hub connection 21 on the clutch input shaft 20, see. Figure 1.
  • the Mit psychologyinsitz 22 has a common mounting joint 23 with the drive plate mounted on it 30.
  • the radius of the assembly joint 23 is greater than 45% greater than the effective diameter of the shaft-hub connection 21st
  • the e.g. Deep-drawn drive plate 30 is rotationally rigidly connected to a first outer disk carrier 40, which in turn is rotationally rigidly connected to a second outer disk carrier 140.
  • the outer disk carriers 40, 140 have two annular disk support portions 58 and 158.
  • the first outer disk carrier 40 is fixed to a main hub 47.
  • the clutch input shaft 20 has a central bore 24 in which a first gearbox input is stored rollingly supported.
  • shaft 51 is stored.
  • a first Lamellentragerflansch 53 is arranged via a shaft-hub connection 52.
  • a first cup-shaped plate carrier 54 is welded.
  • the fins 56, 57 of the first clutch 50 are arranged between the first disk carrier 54 and the outer disk carrier section 58 of the first outer disk carrier 40.
  • external disks 56 engage in a form-locking manner in the profiling of the outer disk support section 58.
  • the outer disks 56 are mounted torsionally stiff but slidably displaceable on this disk support portion 58.
  • the seated between the outer disk 56 inner plates 57 are connected in a similar manner with the profiling of the first inner disk carrier 54.
  • the first outer disk carrier 40 forms, together with the main hub 47, a compensating ring cylinder 45.
  • a cylinder outer wall 48 which is substantially U-shaped in the partial cross section is arranged laterally offset laterally offset from the compensating ring cylinder 45 on the main hub 47.
  • a molded from deep-drawn sheet the first annular piston 61 is arranged between the cylinder outer wall 48 and the compensating ring cylinder 45.
  • the annular piston 61 has a piston section 62 and a force transmission section 67. Between the piston section 62 and the cylinder outer wall 48 there is a first working space 80.
  • This working space 80 is pressurized with pressure oil to press the power transmission section 67 against the first plate pack 55.
  • the power transmission section 67 engages via fingers 68 into the interior 46 of the first outer disk carrier 40.
  • the clutch input shaft 20 is moved over the first outer disk carrier 40 and the first inner disk.
  • Slider 54 is connected to the first transmission input shaft 51.
  • One of the gear wheels arranged on this shaft 51 then meshes with a gear wheel on the transmission output shaft in a force-transmitting manner.
  • the gear wheels and the transmission output shaft are not shown in FIG.
  • the diaphragm spring 100 is seated as an elastic return element. It releases the fingers 68 from the first disk set 55 when the first working space 80 is depressurized.
  • a second transmission input shaft 151 In the main hub 47 is a second transmission input shaft 151, e.g. stored over two needle bearings.
  • This transmission input shaft 151 embodied as a hollow shaft surrounds the first transmission input shaft 51 at least in regions.
  • a shaft-hub connection 152 At the front end of the shaft oriented towards the clutch input shaft 20 there is a shaft-hub connection 152, via which a second disk carrier flange 153 is rotationally fixed on the second transmission input shaft 151 is arranged.
  • the inner disk carrier 154 of the second clutch 150 is fastened to the disk carrier flange 153.
  • an inner disk carrying section 158 of the second outer disk carrier 140 is arranged between this second inner disk carrier 154 and the first inner disk carrier 54. It is welded to the first outer disk carrier 40. The second inner disk carrier 154 and the second outer disk carrier 140 fix the second disk set 155 in a known manner.
  • a compensation space limiting wall 191 fastened to the main hub 47 is arranged within the installation space of the second inner disk carrier 154.
  • the boundary wall 191 has the shape of a second compensation chamber 190 surrounding on three sides of the annular channel
  • a second annular piston 161 is arranged between the compensation chamber 190 and the first outer plate carrier 40.
  • the annular piston 161 which is divided into a piston section 162 and an actuating section 167, prints with the actuating section 167 on engagement with the second disk set 155 during engagement.
  • the piston portion 162 terminates a second working space 180, which is formed by the first outer disk carrier 40 and a cylinder ring 181. In this case, it is sealed against both components 40, 181 by means of lip seals.
  • the piston portion 62 of the first annular piston 61 has comparable seals.
  • the cylinder ring 181 is also fixed to the main hub 47.
  • the annular piston 161 is also sealed off from the compensation chamber 190.
  • the second outer disk carrier 140 When the second clutch 150 is actuated, the second outer disk carrier 140 is connected to the second inner disk carrier 154 when the first clutch 50 is open. The engine torque is thus transmitted to the second transmission input shaft 151. Corresponding gear wheels conduct the rotational movement in a torque-changed manner to the transmission output shaft (not shown) which drives the drive train.
  • a plurality of spring elements 200 for example in the form of helical compression springs arranged. They are cut off between the second annular piston 161 and the boundary wall 191. Over the spring elements 200 of the annular piston 161 is lifted when loosening the second clutch 150 from the corresponding disk set 155.
  • FIG. 2 shows u.a.
  • This compensation chamber 190 is bounded by the Ausretesraumbegrenzungs- wall 191, the cylinder ring 181 and guided between the two latter components piston portion 162 of the annular piston 161.
  • the gutter- or channel-like Aus GmbHsraumbegrenzungswandung 191 annularly surrounds the main hub 47 carrying them. Their opening cross-section oriented to the left according to FIGS. 1 and 2 is closed, for example, approximately 77% by the piston section 162 of the annular piston 161. The remaining cross-sectional area is covered by the cylinder ring 181.
  • the Austiciansraumbegrenzungswandung 191 has, for example, two cylindrical areas.
  • the first is an outer guiding region 192, on the inner wall 193 of which the piston section 162 slides sealingly along.
  • the second is a ring portion 194 disposed near the main hub 47 and having a plurality of overbias 195.
  • the compensation chamber 190 is filled and emptied via the overflow bores 195.
  • the emptying takes place when the second coupling 150 is actuated.
  • the hydraulic oil 4 displaced via the overflow bores 195 through the annular piston 161 flows in a largely radial direction into a gap space 5 located between the compensation chamber boundary wall 191 and the second inner disk carrier 154. It serves, inter alia, for cooling the disk packs 55, 155.
  • the cylinder ring 181 has a cylindrical guide portion 182 and a double-angled flange portion 184 supporting it. The latter is rotationally rigid together with the balance space limiting wall 191
  • the guide region 182 of the cylinder ring 181 has on its outer contour a Fuhrungsflache 183 on which the annular piston 161 - the working chamber 180 and the compensation chamber 190 separating - slidably along.
  • compensation chamber 190 is a standing under centrifugal oil quantity.
  • the large radius 197 of the compensation chamber 190 is predetermined by the outer guide surface 193.
  • the small radius 198 of the compensation chamber 190 determine the edges of the overflow recesses 195 oriented toward the coupling center line 9.
  • the rotating effective oil column of the compensation chamber 190 extends approximately from the small radius 198 to the large radius 197.
  • the working space 180 of the second annular piston 161 is bounded radially outward by a piston-side guide surface 165.
  • a seal 49 arranged in the outer disk carrier 40 slides along it.
  • the radius 187 of this guide surface 165 is smaller than the large compensation space radius 197.
  • the radially inner boundary of the working space 180 is located in the flange portion 184 of the cylinder ring 181.
  • the pressure oil supply of the working space 180 takes place at the level of the radius 188.
  • the rotating effective Oil column of the working space 180 thus extends approximately from the small radius 188 to the large radius 187th

Landscapes

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

Abstract

La présente invention concerne un système d'embrayage destiné à des entraînements de véhicule à moteur, comprenant un arbre d'entrée d'embrayage et au moins deux arbres d'entrée de boîte de vitesses, chaque arbre d'entrée de boîte de vitesses étant relié à l'arbre d'entrée d'embrayage par un embrayage à friction actionnable refroidi et lubrifié par un liquide, chaque embrayage friction étant actionné par au moins un piston d'un organe de réglage hydraulique, au moins un piston séparant une chambre de travail et une chambre de compensation, et le piston étant guidé de sorte que son contour de guidage qui se trouve radialement vers l'extérieur, est en contact avec une section cylindrique d'une paroi de limitation de chambre de compensation fixée au moyeu principal. Le piston est guidé dans la zone du moyeu principal avec son contour de guidage qui se trouve radialement vers l'intérieur. La paroi de limitation de chambre de compensation qui se trouve radialement vers l'intérieur, présente des ouvertures de trop-plein. L'invention met à disposition un système d'embrayage qui permet de minimiser l'action du remplissage de la chambre de travail subissant une force centrifuge, qui empêche une bonne désolidarisation de l'embrayage.
PCT/EP2008/003573 2007-05-10 2008-04-24 Dispositif double-embrayage à chevauchement axial court de la chambre de travail et de la chambre de compensation Ceased WO2008138506A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007022420.8 2007-05-10
DE102007022420A DE102007022420A1 (de) 2007-05-10 2007-05-10 Doppelkupplungsanordnung mit axial kurz bauender Schachtelung von Arbeits- und Ausgleichsraum

Publications (1)

Publication Number Publication Date
WO2008138506A1 true WO2008138506A1 (fr) 2008-11-20

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PCT/EP2008/003573 Ceased WO2008138506A1 (fr) 2007-05-10 2008-04-24 Dispositif double-embrayage à chevauchement axial court de la chambre de travail et de la chambre de compensation

Country Status (2)

Country Link
DE (1) DE102007022420A1 (fr)
WO (1) WO2008138506A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103836091A (zh) * 2012-11-20 2014-06-04 博格华纳公司 双离合装置和用于安装双离合装置的方法
CN105041907A (zh) * 2014-04-30 2015-11-11 舍弗勒技术股份两合公司 离合器装置
WO2017203060A1 (fr) 2016-05-27 2017-11-30 Punch Powertrain N.V. Système d'embrayage et unité d'actionnement associée
CN111163963A (zh) * 2017-09-27 2020-05-15 戴姆勒股份公司 复合变速器及具有复合变速器的混合动力动力传动系
CN112997019A (zh) * 2018-11-12 2021-06-18 戴姆勒股份公司 具有第一离合器和第二离合器的离合设备
CN113062932A (zh) * 2020-01-02 2021-07-02 广州汽车集团股份有限公司 一种湿式双离合器总成的油路系统
CN113738786A (zh) * 2020-05-29 2021-12-03 蜂巢传动科技河北有限公司 用于车辆的动力传动系统及车辆

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013200408A1 (de) * 2012-01-20 2013-07-25 Schaeffler Technologies AG & Co. KG Nasse Reibkupplung mit integriertem Dämpfersystem
DE112015002055A5 (de) * 2014-04-30 2017-01-19 Schaeffler Technologies AG & Co. KG Lamellenträger, Kupplungsbaugruppe und Doppelkupplungseinrichtung
DE102015207200A1 (de) * 2014-04-30 2015-11-05 Schaeffler Technologies AG & Co. KG Doppelkupplungseinrichtung
DE102015207201A1 (de) * 2014-04-30 2015-11-05 Schaeffler Technologies AG & Co. KG Doppelkupplungseinrichtung
FR3092373B1 (fr) * 2019-01-31 2021-04-30 Valeo Embrayages Double embrayage humide et dispositif de rappel elastique pour un tel double embrayage humide
DE102019209500A1 (de) * 2019-06-28 2020-12-31 Zf Friedrichshafen Ag Verfahren zur Sicherstellung einer Befüllung eines Ausgleichsraumes einer hydraulischen Betätigungseinrichtung eines Schaltelements

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3581858A (en) * 1968-09-03 1971-06-01 Borg Warner Fluid actuator
US4732253A (en) * 1985-08-31 1988-03-22 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Power transmission
US5421439A (en) * 1993-03-08 1995-06-06 Nissan Motor Co., Ltd. Clutch of automatic transmission
EP1568906A1 (fr) * 2004-02-27 2005-08-31 BorgWarner Inc. Embrayage double
WO2006030935A1 (fr) * 2004-09-17 2006-03-23 Toyota Jidosha Kabushiki Kaisha Dispositif d'embrayage pour transmission automatique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3581858A (en) * 1968-09-03 1971-06-01 Borg Warner Fluid actuator
US4732253A (en) * 1985-08-31 1988-03-22 Mitsubishi Jidosha Kogyo Kabushiki Kaisha Power transmission
US5421439A (en) * 1993-03-08 1995-06-06 Nissan Motor Co., Ltd. Clutch of automatic transmission
EP1568906A1 (fr) * 2004-02-27 2005-08-31 BorgWarner Inc. Embrayage double
WO2006030935A1 (fr) * 2004-09-17 2006-03-23 Toyota Jidosha Kabushiki Kaisha Dispositif d'embrayage pour transmission automatique

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103836091A (zh) * 2012-11-20 2014-06-04 博格华纳公司 双离合装置和用于安装双离合装置的方法
CN103836091B (zh) * 2012-11-20 2019-01-29 博格华纳公司 双离合装置和用于安装双离合装置的方法
CN105041907A (zh) * 2014-04-30 2015-11-11 舍弗勒技术股份两合公司 离合器装置
WO2017203060A1 (fr) 2016-05-27 2017-11-30 Punch Powertrain N.V. Système d'embrayage et unité d'actionnement associée
US10823280B2 (en) 2016-05-27 2020-11-03 Punch Powertrain N.V. Clutch system and actuation unit therefore
CN111163963A (zh) * 2017-09-27 2020-05-15 戴姆勒股份公司 复合变速器及具有复合变速器的混合动力动力传动系
CN112997019A (zh) * 2018-11-12 2021-06-18 戴姆勒股份公司 具有第一离合器和第二离合器的离合设备
CN112997019B (zh) * 2018-11-12 2023-05-26 梅赛德斯-奔驰集团股份公司 具有第一离合器和第二离合器的离合设备
CN113062932A (zh) * 2020-01-02 2021-07-02 广州汽车集团股份有限公司 一种湿式双离合器总成的油路系统
CN113062932B (zh) * 2020-01-02 2023-08-15 广州汽车集团股份有限公司 一种湿式双离合器总成的油路系统
CN113738786A (zh) * 2020-05-29 2021-12-03 蜂巢传动科技河北有限公司 用于车辆的动力传动系统及车辆
CN113738786B (zh) * 2020-05-29 2023-03-10 蜂巢传动科技河北有限公司 用于车辆的动力传动系统及车辆

Also Published As

Publication number Publication date
DE102007022420A1 (de) 2008-11-13

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