WO2013174634A1 - Embrayage double humide - Google Patents

Embrayage double humide Download PDF

Info

Publication number
WO2013174634A1
WO2013174634A1 PCT/EP2013/059174 EP2013059174W WO2013174634A1 WO 2013174634 A1 WO2013174634 A1 WO 2013174634A1 EP 2013059174 W EP2013059174 W EP 2013059174W WO 2013174634 A1 WO2013174634 A1 WO 2013174634A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
central web
wet
vibration damper
housing
Prior art date
Application number
PCT/EP2013/059174
Other languages
German (de)
English (en)
Inventor
Elmar Lorenz
Original Assignee
Schaeffler Technologies AG & 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 & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to CN201380026650.7A priority Critical patent/CN104321553B/zh
Priority to DE112013002655.4T priority patent/DE112013002655A5/de
Publication of WO2013174634A1 publication Critical patent/WO2013174634A1/fr

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
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/385—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs double clutches, i.e. comprising two friction disc mounted on one driven shaft
    • 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
    • F16D2021/0623—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate having a damper 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
    • F16D2021/0669—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
    • 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 present invention relates to a wet double clutch for switching a
  • Double gear in particular a motor vehicle.
  • a dual clutch is used for torque transmission from an output shaft of a drive unit, in particular an internal combustion engine, to a transmission with two transmission input shafts.
  • a prior art vibration damper consists of a disc with circular dampers adapted to damp out unwanted vibrations and torsional vibrations, thus decoupling the drive train from the drive unit.
  • the present invention has for its object to provide a wet dual clutch, which takes a particularly small space to complete.
  • a wet dual clutch which has the following components: a wet area, a rotating clutch housing, which comprises a clutch cover and a clutch basket, at least two clutch systems, each comprising at least one clutch disc with a corresponding number of pressure plates.
  • the wet double clutch is characterized in that a rotatably connectable with the clutch basket central web is arranged with an outer edge with an outer diameter between the two coupling systems.
  • a rotationally effective connection means a connection by which a rotational movement of one component is transmitted to the other component, either with or without a relative rotational angle of the two components relative to one another.
  • further components can be interposed in the rotationally effective connection, the connection thus takes place directly or indirectly between the components.
  • the wet area is filled with a liquid, preferably with a mineral oil, and mainly comprises the heat-loaded, that is, the friction-loaded fins, which can better dissipate the resulting heat.
  • the force transmission unit can be arranged in the wet area.
  • the rotating clutch housing has the task to define the wet area and seal it against the dry area. Furthermore, it is the task of the rotating clutch housing to transmit the torque from the output shaft of the drive unit to the lamellae, for example the central web and the pressure plates. In some embodiments, the clutch housing also has the task of forming an abutment for the contact pressure and to transfer the force in solid add-on parts.
  • the central web forms a pressure plate for the clutch discs, wherein the central web, in contrast to the pressure plates with one side is always frictionally connected to one of the two clutch systems.
  • the central web forms upon engagement of the first coupling system, the innermost pressure plate of the first coupling system with, for example, the left surface and the innermost pressure plate of the second coupling system upon engagement of the second coupling system with, for example, the right side.
  • the two clutch systems each form independent clutch systems consisting of at least one pressure plate, each with a corresponding clutch disc, so that a friction surface is formed, which generates a transmission of the torque of the output shaft and at the same time the radial extent is adapted to the available space.
  • the wet dual clutch also has a vibration damper with an input side and an output side, which is arranged in the wet area to the double clutch.
  • the vibration damper has the task to dampen vibrations in the drive train and thus dampen not only noise but also torque load peaks.
  • the arrangement of the vibration damper in the wet space of the double clutch a variety of components can be saved. In order to allow damping of the vibrations, however, corresponding recesses must be provided for the functional parts, which are sufficiently spaced even during oscillation of the vibration damper, so that they are not affected by the vibration of the vibration damper.
  • the arrangement of the vibration damper in the wet area moreover, the oscillating mass is increased by the liquid, so that a lower mass part is required.
  • the liquid also has a damping effect, so that the damper portion of the vibration damper can be performed reduced with the same damping effect.
  • the property of a damper is to convert a mechanical vibration into a dampening fluid, preferably into heat energy by friction in the dampening fluid. Because a wet double clutch must already be designed to dissipate a large amount of heat, the vibration damper is already sufficiently cooled by the location in the wet area.
  • FIGS. show particularly preferred embodiments, to which the invention is not limited.
  • the figures and in particular the illustrated proportions are only schematic. Show it:
  • Fig. 1 a double clutch in section with outside arranged vibration damper
  • Fig. 2 a double clutch in section with laterally arranged vibration damper
  • Fig. 3 a double clutch in section with arranged in the clutch housing
  • FIGS. 1 to 3 shows a motor vehicle with a transverse drive unit and a double clutch, for example, one of FIGS. 1 to 3.
  • Fig. 1 shows a double clutch 1 in section, in which the vibration damper 19 is disposed outside of the coupling housing 3 on an extension of the clutch cover 4 and resting on the clutch basket 5.
  • the vibration damper 19 is composed of two springs or spring systems 22, 23 together.
  • a central web is arranged with an outer diameter 8 to the outer edge 7, which is axially fixed to a stop which is formed by the clutch basket 5.
  • a first clutch system 9 is shown, which is composed of a clutch disc 1 1 and a pressure plate 15.
  • a second clutch system 10 is shown, which is composed of two clutch plates 13 and 14 and two pressure plates 17 and 18.
  • the vibration damper 19 has an input side 20 and an output side 21. Furthermore, the Abtnebswellenan gleich 32 for an unillustrated output shaft 27 of a drive unit 26 (both not shown) can be seen in Fig. 1. In the region of the output shaft connection 32, a radial shaft sealing ring 33 is shown. Furthermore, a force transmission unit 34 can be seen, which presses against the driving ring 36 via a lever spring 35, which is mounted with the lever spring bearing 37. The lever spring bearing 37 is arranged on the driving teeth 38 of the clutch basket 5. Furthermore, an actuator 39 is shown for the engagement force, which is located in a fixed attachment 40. The first clutch system 9 is connected to a first transmission shaft 41 and the second clutch system 10 is arranged on a second transmission shaft 42, which are arranged concentrically in the center of the dual clutch 1.
  • Fig. 2 shows a similar arrangement as Fig. 1, wherein the vibration damper 19 is arranged laterally to the overall clutch system and is connected to the input side 20 with clutch cover 4 and is connected to the output side 21 to the clutch basket 5.
  • the vibration damper 19 has an inner diameter 24 that is smaller than the outer diameter.
  • the two coupling systems are 9,10 symmetrically constructed with respect to the friction surfaces and Reib lakebaum and each consist of two clutch plates 1 1, 12 or 13, 14 and two pressure plates 15, 16 and 17, 18th Incidentally, reference is made to the description of FIG. 1.
  • Fig. 3 shows a similar arrangement as before in Figs. 1 and 2, in which case the vibration damper 19 is connected at the outer edge 7 with the input side 20.
  • the output side 21 of the vibration damper 19 is connected to the clutch housing 3, in each case with the housing cover 4 and the clutch basket 5, which are almost completely symmetrical in this example.
  • the two coupling systems 9, 10 are constructed symmetrically in the region of the friction surfaces and consist in each case of two clutch disks 1 1, 12 or 13, 14 and two pressure plates 15, 16 or 17, 18. Otherwise, referred to the previously described Figs. 1 and 2.
  • FIG. 4 shows a motor vehicle 25 with a double clutch 1, for example according to FIGS. 1 to 3.
  • a drive unit 26 is arranged with the output shaft 27, via which the output unit 26 is connected to the double clutch 1, which in turn is connected to the purely schematically illustrated drive train 28 is connected.
  • the drive unit 26 with the axis 31 is arranged transversely to the longitudinal axis 30 of the motor vehicle 25.
  • Fig. 5 shows a double clutch 1 with a central web 6, a first clutch system 9 and a second clutch system 10.
  • the central web 6 and the two clutch systems 9, 10 are arranged in a clutch housing 3 with a driving device 43 and a clutch basket 5.
  • the clutch housing 3 is fixedly connected to the output shaft terminal 32 and therefore rotates.
  • About the driving teeth 38 of the central web 6 and the pressure plates 18 are taken and transmit the torque, starting from the output shaft connection 32 when the pressure plates 18 are pressed against the clutch plates 1 1 and 14 respectively.
  • the clutch disc 14 has a friction surface 44.
  • the first clutch disc 1 1 has on the left and right sides on a friction surface.
  • the pressure plates 18 are pressed by the power transmission unit 45 with the driving ring 36.
  • the power transmission unit 45 is driven on the input side by the actuating device 46, which is arranged in a fixed attachment 40, that is to say a non-rotating attachment.
  • the power transmission unit 45 consists of
  • the rotating portion 48 includes the driving ring 36, which is connected to the actuating finger 48 and optionally a lever spring 35.
  • the lever spring of the second clutch system 10 is held on the driving teeth 38 in the lever spring counter bearing 37.
  • the clutch basket 5 shown is bell-shaped or stepped and has a stop 49 for the central web 6, so that it is axially fixed.
  • the driving teeth 38 is formed on the outer diameter 8 of the central web 6 and the pressure plates 18, so that they engage in the driving teeth 38.
  • the first clutch disc 1 1 has a first diameter 50 and the second clutch disc 14 has a second diameter 51, which is smaller than the first diameter 50.
  • the transmission of the contact pressure on the pressure plates 18 must be diverted into an attachment.
  • the central web 6 is set up in the present case.
  • the contact pressure transmitted by the pressure pot to the pressure plates 18 is absorbed by the central web 6 and transmitted via the centrally arranged rotating bearing 52 in the fixed attachment 40.
  • the rotating bearing is disposed on a diameter 53 which is smaller than the innermost diameter 54 of the friction surfaces 44 of the clutch discs 1 1, 14.
  • the first transmission shaft 41 which is connected to the first clutch system 9
  • the second transmission shaft 42 which is connected to the second clutch system 10 shown.
  • On the left side of the drive shaft connection 32 a radial shaft sealing ring 55 is shown. This is designed to seal the coupling system to the outside.

Abstract

L'invention concerne un embrayage double humide, comportant une zone humide, un carter d'embrayage rotatif, lequel comprend un couvercle d'embrayage et une cage d'embrayage, au moins deux systèmes d'embrayage qui comportent chacun au moins un disque d'embrayage pourvu d'un nombre correspondant de plateaux de pression. Un élément de liaison central pouvant être relié de manière rotative à la cage d'embrayage et comprenant une arête extérieure pourvue d'un diamètre extérieur est agencé entre les deux systèmes d'embrayage.
PCT/EP2013/059174 2012-05-22 2013-05-02 Embrayage double humide WO2013174634A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201380026650.7A CN104321553B (zh) 2012-05-22 2013-05-02 湿式双离合器
DE112013002655.4T DE112013002655A5 (de) 2012-05-22 2013-05-02 Nasse Doppelkupplung

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012208580 2012-05-22
DE102012208580.7 2012-05-22

Publications (1)

Publication Number Publication Date
WO2013174634A1 true WO2013174634A1 (fr) 2013-11-28

Family

ID=48236962

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/059174 WO2013174634A1 (fr) 2012-05-22 2013-05-02 Embrayage double humide

Country Status (3)

Country Link
CN (1) CN104321553B (fr)
DE (2) DE102013208074A1 (fr)
WO (1) WO2013174634A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107132859B (zh) * 2017-03-24 2023-04-04 中国第一汽车股份有限公司 一种搭载湿式双离合器变速器的传动系扭振控制方法
DE102018211054B4 (de) * 2018-07-04 2020-09-03 Magna Pt B.V. & Co. Kg Kupplungsanordnung für einen Kraftfahrzeugantriebsstrang

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4966270A (en) * 1988-06-09 1990-10-30 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Hydraulically operated double clutch for a motor vehicle
US20010025760A1 (en) * 2000-04-04 2001-10-04 Mannesmann Sachs Ag Double clutch assembly
DE102004012948A1 (de) * 2004-03-17 2005-10-06 Zf Friedrichshafen Ag Doppelkupplungseinrichtung in axialer Bauart
DE102011104247A1 (de) * 2010-06-29 2011-12-29 Schaeffler Technologies Gmbh & Co. Kg Doppelkupplungsanordnung
WO2013079045A1 (fr) * 2011-11-30 2013-06-06 Schaeffler Technologies AG & Co. KG Ensemble petit embrayage double

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102112763B (zh) * 2008-07-14 2014-02-12 舍弗勒技术股份两合公司 双离合器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4966270A (en) * 1988-06-09 1990-10-30 Dr. Ing. H.C.F. Porsche Aktiengesellschaft Hydraulically operated double clutch for a motor vehicle
US20010025760A1 (en) * 2000-04-04 2001-10-04 Mannesmann Sachs Ag Double clutch assembly
DE102004012948A1 (de) * 2004-03-17 2005-10-06 Zf Friedrichshafen Ag Doppelkupplungseinrichtung in axialer Bauart
DE102011104247A1 (de) * 2010-06-29 2011-12-29 Schaeffler Technologies Gmbh & Co. Kg Doppelkupplungsanordnung
WO2013079045A1 (fr) * 2011-11-30 2013-06-06 Schaeffler Technologies AG & Co. KG Ensemble petit embrayage double

Also Published As

Publication number Publication date
DE102013208074A1 (de) 2013-11-28
CN104321553B (zh) 2017-04-12
CN104321553A (zh) 2015-01-28
DE112013002655A5 (de) 2015-02-19

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