EP4314586A1 - Embrayage à trois disques comprenant trois chambres de compensation d'huile centrifuge reliées à un canal d'huile centrifuge partagé - Google Patents

Embrayage à trois disques comprenant trois chambres de compensation d'huile centrifuge reliées à un canal d'huile centrifuge partagé

Info

Publication number
EP4314586A1
EP4314586A1 EP22711049.1A EP22711049A EP4314586A1 EP 4314586 A1 EP4314586 A1 EP 4314586A1 EP 22711049 A EP22711049 A EP 22711049A EP 4314586 A1 EP4314586 A1 EP 4314586A1
Authority
EP
European Patent Office
Prior art keywords
piston
clutch
centrifugal oil
centrifugal
chamber
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Withdrawn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
EP22711049.1A
Other languages
German (de)
English (en)
Inventor
Hansi Gremplini
Inan Cokdogru
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.)
Magna PT BV and Co KG
Original Assignee
Magna PT BV 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 Magna PT BV and Co KG filed Critical Magna PT BV and Co KG
Publication of EP4314586A1 publication Critical patent/EP4314586A1/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Withdrawn legal-status Critical Current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
    • F16D25/10—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
    • 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
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication

Definitions

  • the present invention relates to a triple clutch arrangement of a motor vehicle, with at least one first and one second and third friction clutch, a first piston arrangement, which serves to actuate the first friction clutch and has a first piston, a first piston chamber and a first centrifugal oil equalizing chamber, a second Piston arrangement, which is used to actuate the second friction clutch and has a second piston, a second piston space and a second centrifugal oil compensation space and a third piston arrangement, which is used to actuate the third friction clutch and has a third piston, a third piston space and a third centrifugal oil compensation space, and one third piston assembly, which is used to actuate the third friction clutch, wherein the pistons are arranged on the same side of the triple-plate clutch, the input shaft opposite the A and connected via a rotary union to a hydraulic control arrangement are, wherein the rotary feedthrough is arranged rotatably radially inside the friction clutches.
  • Dual clutch transmissions have a dual clutch arrangement and two partial transmissions.
  • the sub-transmissions are usually designed in countershaft design.
  • One of the sub-transmissions is assigned to the even gears, the other sub-transmission to the odd gears.
  • friction clutches are used, for example wet-running multi-plate clutches.
  • the two double clutches are nested radially into one another, with one of the friction clutches being located radially on the inside and the other further radially on the outside.
  • wet multi-plate clutches which comprise more than two clutches, e.g. B. from DE102017206251 A1.
  • the first and a second friction clutch can each be actuated fluidically, with piston arrangements which serve to actuate the friction clutches and each have a piston, a piston chamber and a centrifugal oil equalization chamber, the piston chambers and the centrifugal oil equalization chambers each being on opposite sides sides of the associated pistons and are connected to a valve arrangement via a rotary feedthrough, the rotary feedthrough having a pin section fixed to the housing, which is arranged within the friction clutches and has ring channels for supplying hydraulic fluid to the piston chambers and the centrifugal oil equalizing chambers, and the housing-fixed Journal section has three ring channels, two of which ring channels are associated with the two piston chambers and of which a single ring channel is associated with the two centrifugal oil equal
  • a double clutch is known from DE 602004012997 T2, with equalization chambers being fluidly connected to one another, so that functionally they form a common equalization chamber for both clutch pistons.
  • the clutch pistons generate the same dynamic forces, so that the connected equalization chambers, which form a common equalization space, are sufficient for both clutch pistons.
  • This arrangement can be practically achieved by openings in the inner part of the middle flange of the double clutch so that the oil pressure is equal on both sides and the oil can flow freely from one side to the other.
  • the static supply pressure for the compensating chambers is achieved through a cavity located in the stator above the inlet to the compensating chambers.
  • the stator forms a non-rotatable, axial supply leadthrough. From there, the equalizing chambers are supplied via ring channels, and the cooling and actuation of the pistons are made possible separately. Separate ring channels of the stator open into openings in the rotating center hub, which is a separate component.
  • the object of the invention is to propose a cost-optimized solution with which components can be saved, but the rotary union is suitably adjustable.
  • the object is achieved with a triple clutch arrangement of a motor vehicle, with a first and a second friction clutch and a third friction clutch with a first and second and third piston arrangement, the first piston arrangement serving to actuate the first friction clutch and a first piston, a first piston chamber first centrifugal oil piston and a first centrifugal oil equalizing chamber, a second piston arrangement, which is used to actuate the second friction clutch and has a second piston, a second piston chamber, a second centrifugal oil equalizing piston and a second centrifugal oil equalizing chamber, and a third piston arrangement, which is used to actuate the third Friction clutch is used and a third piston, a third piston chamber, a second ben and a third centrifugal oil equalizing chamber, wherein the pistons are arranged on the same ben side of the triple multi-plate clutch, the ge of the input shaft and opposite the piston chambers of which are connected via an axially running hollow pin of a rotary feedthrough via bushings in a housing with
  • the rotatable trunnion replaces the non-rotatable rotary feedthrough, which saves on components. In addition, assembly is easier. Due to the reduction to a single centrifugal oil channel in the journal, the component is easier to manufacture.
  • the wording that the pin extends at least partially below the friction clutch development includes the two embodiments, wherein in the first Embodiment of the pin runs completely under the friction clutches. In the second embodiment, the pin runs at least for the most part below the friction clutches.
  • the configuration of the invention allows the single centrifugal oil channel of the Zap fens to supply centrifugal oil or cooling oil to all centrifugal oil equalizing spaces.
  • centrifugal oil equalizing chambers in relation to one another is not decisive. They are all supplied with centrifugal oil/cooling oil via the common centrifugal oil channel.
  • the triple clutch arrangement according to the invention is designed in such a way that the friction clutches each have an input member, the input members being connected to the pin of the rotary feedthrough and being non-rotatably connected to a drive shaft.
  • journal has radial channels that are connected to partial sections of the fluid channel in order to supply the at least two friction clutches with fluid.
  • the sections have different axial lengths, so that the friction clutches can be supplied with cooling oil for actuation as well as for filling the centrifugal oil compensation chambers and for cooling the friction clutches.
  • the triple clutch arrangement is a double clutch with pistons that are axially offset from one another, and in another embodiment it is a double clutch or a triple clutch with pistons that are radially offset from one another.
  • Fig. 1 is a schematic longitudinal sectional view of a non-inventive dual clutch assembly, in connection with associated components of a dual clutch transmission.
  • Fig. 2 is a longitudinal sectional view of a triple clutch arrangement according to the invention.
  • a drive train of a motor vehicle is denoted generally by 10 in FIG.
  • the drive train 10 has an internal combustion engine or other drive motor 12, the output of which is ver with the input of a dual clutch transmission 14 connected.
  • the dual-clutch transmission 14 includes a stepped transmission in countershaft construction, which is not shown and includes two sub-transmissions. Furthermore, the double-clutch transmission 14 has a double-clutch arrangement 20, the input of which is connected to the output of the drive motor 12 and the output of which is connected to the stepped transmission.
  • the double clutch arrangement 20 has an input shaft 22 which can be connected in a rotationally fixed manner to the output shaft of the drive motor 12 by means of teeth.
  • the dual clutch arrangement 20 also has a first output shaft 24 in the form of a solid shaft, which is connected to a first sub-transmission of the stepped transmission 16 .
  • the double clutch arrangement 20 has a second output shaft 26 in the form of a hollow shaft, which is connected to the second part of the transmission.
  • the output shafts 24, 26 are arranged concentrically to each other.
  • the dual clutch assembly 20 includes a first friction clutch 28 configured to connect the input shaft 22 to the first output shaft 24 and a second friction clutch 30 configured to connect the input shaft 22 to the second output shaft 26 .
  • the two friction clutches 28, 30 are arranged radially offset from one another, the first friction clutch 28 being arranged radially on the outside and the second friction clutch 30 being arranged radially on the inside concentrically thereto.
  • the two friction clutches 28, 30 are accommodated in a housing 32.
  • the friction clutch 28 has an outer disk carrier 38 and an inner disk carrier 40 which is connected to a first basket 42 which is connected to the first output shaft 24 is connected.
  • the second friction clutch 30 has an outer disk carrier 46 which is connected to the second output shaft 26 .
  • a clutch carrier is shown at 60, which is mounted fixed to the housing, ie not rotating. Furthermore, at 58 a valve arrangement or a hydraulic control arrangement is shown schematically, by means of which the double clutch arrangement can be operated.
  • a rotary union assembly consisting of an axially extending, hollow pin 62 in sectional view concentrically disposed about the two output shafts 24,26.
  • the pin 62 extends from the side of the housing 32 with the Kupplungsträ ger 60 axially almost up to a second basket 48 which is connected to the second output shaft 26 is connected.
  • the pin 62 lies radially within the two friction clutches 28, 30.
  • the pin 62 of the rotary feedthrough arrangement is rotatably mounted with a fluff 61 in the housing.
  • Bushings 63 in housing 32 supply fluid from hydraulic control assembly 58 to trunnion 62 .
  • a bearing 64 is shown in FIG.
  • the rotary feedthrough 62 is rigidly connected to the input hub via the outer disk carrier 38 of the first friction clutch 28, so that the rotary feedthrough and the pin 62 rotate with the speed of the connected motor 12.
  • An inner disk carrier 68 of the second friction clutch 30 is fixed to a web 65 on the pin 62 .
  • a first piston 70 of the first friction clutch 28 is mounted on the pin 62 axially displaceable ver.
  • a first piston space 72 is formed between a support structure and the first piston 70 .
  • the first piston chamber 72 is connected via the rotary guide assembly with the pin 62 and the clutch carrier 60 with the Ventilan order 58.
  • the pin 62 is provided with the first actuation radial channel 74.
  • This can be formed by a plurality of bores which are offset in the circumferential direction and which are connected to a fluid channel 66 in the pin 62 .
  • the fluid channel 66 is in turn connected to the clutch carrier 60 or the valve arrangement 58 via the passages 63 in the housing 32 .
  • a plurality of restoring springs 76 are supported on the web 65 and are distributed uniformly over the circumference. The first piston 70 is therefore actuated against the force of the first return springs 76.
  • a first centrifugal oil compensation space 78 is provided between the piston 70 and the inner disk carrier 68 of the second friction clutch 30 .
  • the centrifugal oil equalizing chamber 78 has the function of generating a counterforce to a clutch actuation force generated by the centrifugal force, which is generated in the assigned first piston chamber 72 .
  • the centrifugal oil compensating chamber 78 is delimited by a centrifugal oil compensating piston 100 .
  • the hydraulic fluid present in the first piston chamber 72 is pressed outwards in such a way that a force is finally exerted on the piston in the direction of actuation of the first friction clutch 28 .
  • This force consequently counteracts a restoring force exerted by the restoring springs 76 when opening the first friction clutch 28 in the manner of a disruptive force.
  • hydraulic fluid is allowed to flow without pressure into the opposite centrifugal oil equalizing chamber 78. There, the centrifugal force generates a counterforce in the direction of "opening" the first friction clutch 28, which counteracts the disruptive force mentioned and cancels it out.
  • the first centrifugal oil compensation chamber 78 is connected to a fluid channel 66 in the journal 62 via a centrifugal oil channel 80 .
  • a second centrifugal oil equalizing chamber 86 which is delimited by a centrifugal oil equalizing piston 101 and is also connected to the centrifugal oil channel 80 .
  • the second centrifugal oil equalization space 86 is delimited on the axially other side by a second piston 90 .
  • a support member is attached to the rotary union, the pin 62, which extends axially between the second piston 90 and the second basket 48 in the radially outward direction.
  • a second piston chamber 92 is set up between the support member and the second piston 90 .
  • the second piston chamber 92 is connected to the fluid channel 66 via a second actuation radial channel.
  • second return springs 96 are also arranged.
  • the operation of the second friction clutch 30 corresponds to that of the first friction clutch 28, with only the direction of actuation being directed in the opposite direction. While the first piston 70 is arranged on one side of the two friction clutches 28, 30, the second piston 90 is net angeord on the opposite side.
  • the fluid channel 66 is divided into different sections 66a, 66b and 66c with different axial lengths.
  • the subsection 66a is connected to the first actuating radial channel 74, the subsection 66b to the flow oil channel 80 and the subsection 66c to the second actuating radial channel 94.
  • FIG. 1 shows the pin 62 with a first radial actuation channel 74, a second radial actuation channel 94 and a centrifugal oil channel 80, it goes without saying that corresponding channels or bores are distributed over the circumference of the pin 62 could be.
  • the spigot 62 includes all the seals 203 so that a simple assembly of the spigot in the flow 61 of the housing 32 can be achieved.
  • Figure 1 describes a double clutch with axially arranged pistons.
  • the core is the supply of all centrifugal oil chambers via a single centrifugal oil channel in a rotatably mounted rotary oil supply.
  • FIG. 2 shows, as a further exemplary embodiment, a triple clutch with a rotary supply, which consists of a pin 62 rotating on a bearing 33 in the housing 32 .
  • the triple-disc clutch includes a pintle swivel 62 that includes oil passages 202 .
  • An input shaft 22 surrounds the first output shaft 24 and a second output shaft 26.
  • a drive plate 207 is attached to the input shaft 22 and is connected via a support 208 to a common disk carrier 209 for the clutches 210 and 28.
  • the three clutches 210, 28, 30 are actuated with the aid of pistons 70, 90, 200.
  • All three pistons 70, 90, 200 are arranged on the same side of the triple-plate clutch, which is opposite to the input shaft 22.
  • the pistons are arranged offset radially one above the other.
  • the triple multi-plate clutch still has centrifugal oil compensating piston 100,
  • centrifugal oil equalization spaces 78, 86 and 103 form centrifugal oil equalization spaces 78, 86 and 103.
  • the centrifugal oil equalizing chambers 78, 86 and 103 are arranged concentrically with one another at a radial distance from one another, with all three centrifugal oil equalizing chambers 78, 86 and 103 being connected to one another.
  • the radial offset of the Centrifugal oil equalization chambers which also do not allow any radial overlapping of the centrifugal oil equalization chambers, enable a compact design in the axial direction.
  • the outer centrifugal oil equalizing chambers 100 are filled via the centrifugal oil equalizing chamber 103 , which fills the centrifugal oil equalizing chamber 22 via an oil passage in the piston 200 and an oil passage in the outer disk carrier of the clutch 30 .
  • the central centrifugal oil compensation chamber 86 fills the centrifugal oil compensation chamber 78 via a channel between the components of the piston 90 and an opening in the common plate carrier.
  • the fluid channel 66 has sections, the sections 66a, 66c, 66d being used for hydraulic actuation, while the section 66b leads to the supply of centrifugal oil to all centrifugal oil equalizing chambers.

Abstract

Est divulgué un agencement d'embrayage à trois disques (20) d'un véhicule automobile, comprenant un premier, un deuxième et un troisième embrayage à friction (28, 30, 210) et un premier, un deuxième et un troisième agencement de piston. Le premier agencement de piston sert à actionner le premier embrayage à friction (210) et comprend un premier piston (70), une première chambre de piston, un premier piston d'huile centrifuge (100) et une première chambre de compensation d'huile centrifuge (78). Le second agencement de piston sert à actionner le deuxième embrayage à friction (28) et comprend un deuxième piston (90), une deuxième chambre de piston, un deuxième piston d'huile centrifuge (101) et une deuxième chambre de compensation d'huile centrifuge (86). Le troisième agencement de piston sert à actionner le troisième embrayage à friction (30) et comprend un troisième piston (200), une troisième chambre de piston, un troisième piston d'huile centrifuge (102) et une troisième chambre de compensation d'huile centrifuge (103). Les trois pistons (70, 90, 200) permettant d'actionner les trois embrayages à friction (28, 30, 210) sont tous disposés du même côté de l'embrayage à trois disques, situés à l'opposé de l'arbre d'entrée (22), et les chambres de piston des pistons sont reliées, par l'intermédiaire d'une broche creuse s'étendant axialement (62) d'un passage de transmission rotatif et par l'intermédiaire de passages dans un boîtier (32), à un agencement de commande hydraulique. Le passage de transmission rotatif est monté rotatif dans le boîtier (32) de l'agencement d'embrayage à trois disques au moyen de la broche (62) et est disposé axialement au moins en partie au-dessous des embrayages à friction (28, 30, 210). La broche (62) présente des canaux radiaux d'actionnement (74, 94, 201) et chacun de ces canaux radiaux d'actionnement (74, 94, 201) est apparié aux trois chambres de piston, et un seul canal d'huile centrifuge est apparié aux trois chambres de compensation d'huile centrifuge (78, 86, 103), les embrayages à friction (28, 30, 210) étant alimentés en fluide de refroidissement par l'intermédiaire du canal d'huile centrifuge (80).
EP22711049.1A 2021-03-29 2022-03-08 Embrayage à trois disques comprenant trois chambres de compensation d'huile centrifuge reliées à un canal d'huile centrifuge partagé Withdrawn EP4314586A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021203150.1A DE102021203150B3 (de) 2021-03-29 2021-03-29 Mehrfachkupplungsanordnung
PCT/EP2022/055844 WO2022207250A1 (fr) 2021-03-29 2022-03-08 Embrayage à trois disques comprenant trois chambres de compensation d'huile centrifuge reliées à un canal d'huile centrifuge partagé

Publications (1)

Publication Number Publication Date
EP4314586A1 true EP4314586A1 (fr) 2024-02-07

Family

ID=80785246

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22711049.1A Withdrawn EP4314586A1 (fr) 2021-03-29 2022-03-08 Embrayage à trois disques comprenant trois chambres de compensation d'huile centrifuge reliées à un canal d'huile centrifuge partagé

Country Status (4)

Country Link
EP (1) EP4314586A1 (fr)
CN (1) CN117222822A (fr)
DE (1) DE102021203150B3 (fr)
WO (1) WO2022207250A1 (fr)

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10223780C1 (de) 2002-05-29 2003-10-16 Porsche Ag Gangschaltgetriebe für ein Kraftfahrzeug mit hydraulisch betätigbarer Mehrfachkupplung
DE20320464U1 (de) 2003-10-30 2004-08-26 Zf Friedrichshafen Ag Kupplungsanordnung in einem Getriebe mit zwei axial und radial benachbarten Kupplungen
ATE391858T1 (de) 2004-08-26 2008-04-15 Hoerbiger & Co Hydraulische doppelkupplung
DE102004055361B4 (de) 2004-11-05 2008-10-30 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Doppelkupplungsanordnung
US8534437B2 (en) * 2010-12-09 2013-09-17 GM Global Technology Operations LLC Centrifugally balanced hydraulic clutch assembly
JP6210017B2 (ja) * 2014-04-17 2017-10-11 マツダ株式会社 自動変速機
JP6156347B2 (ja) * 2014-12-10 2017-07-05 マツダ株式会社 自動変速機
DE102017206251B3 (de) 2017-04-11 2018-05-17 Bayerische Motoren Werke Aktiengesellschaft Wassertankeinrichtung für eine Brennkraftmaschine mit Wassereinspritzung
DE102018008912B3 (de) * 2018-11-12 2020-01-09 Daimler Ag Hybrid-Doppelkupplungsgetriebe
DE102019104074A1 (de) 2019-02-19 2020-08-20 Schaeffler Technologies AG & Co. KG Dreifachkupplung für achsparalleles Hybridmodul mit getriebeseitiger Ansteuerung von drei Kupplungen über Dreheinführung
DE102019001335A1 (de) * 2019-02-25 2020-08-27 Daimler Ag Hybridtriebkopf für ein Kraftfahrzeug sowie Kraftfahrzeug mit einem solchen Hybridtriebkopf
CN112443590B (zh) * 2019-09-05 2022-07-22 广州汽车集团股份有限公司 一种车辆及湿式双离合器

Also Published As

Publication number Publication date
DE102021203150B3 (de) 2022-09-01
WO2022207250A1 (fr) 2022-10-06
CN117222822A (zh) 2023-12-12

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