EP3610166A1 - Système d'embrayage multiple, système de boîte de vitesses à double embrayage et véhicule à moteur - Google Patents

Système d'embrayage multiple, système de boîte de vitesses à double embrayage et véhicule à moteur

Info

Publication number
EP3610166A1
EP3610166A1 EP18709993.2A EP18709993A EP3610166A1 EP 3610166 A1 EP3610166 A1 EP 3610166A1 EP 18709993 A EP18709993 A EP 18709993A EP 3610166 A1 EP3610166 A1 EP 3610166A1
Authority
EP
European Patent Office
Prior art keywords
clutch
arrangement
clutch assembly
transmission
multiple 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Withdrawn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
EP18709993.2A
Other languages
German (de)
English (en)
Inventor
Angelika Ebert
Steffen Matschas
Johannes Friess
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP3610166A1 publication Critical patent/EP3610166A1/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Withdrawn legal-status Critical Current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
    • F16D25/12—Details not specific to one of the before-mentioned types
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/02—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of clutch
    • 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
    • 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/12—Mounting or assembling

Definitions

  • the invention relates to a multiple clutch arrangement for the arrangement between a drive unit and a transmission with at least two multi-plate clutches comprising a plate carrier and an actuating element.
  • the multiple clutch assembly has a single radial bearing on the engine side.
  • double clutches and triple clutches usually two radial bearings are available.
  • the bearing at the radial bearing point may be a radial bearing or an axial and radial bearing.
  • the bearing is a radial and thrust bearing, the motor side, it is anyway the only radial bearing point of the clutch assembly.
  • the bearing is preferably designed as a ball bearing.
  • the multiple clutch assembly motor side exactly two thrust bearings, have.
  • One of the two thrust bearings is preferably a radial bearing at the same time.
  • the second bearing is preferably a pure thrust bearing. It can be configured as a needle bearing.
  • Engine side means in the present application in the axial direction closer to the engine, namely on the internal combustion engine.
  • Transmission side means in the axial direction closer to the transmission.
  • the multiple-clutch arrangement can preferably have exactly two thrust bearings on the exhaust side. These are advantageously pure thrust bearings.
  • the axial bearing can be designed as a needle bearing.
  • the multi-coupling arrangement on the gutter side have exactly two radial bearings, in particular pure radial bearings.
  • These radial bearings can be designed as a needle bearing.
  • the radial bearings can be used in particular for supporting a hub and accordingly be arranged between a hub and a transmission input shaft.
  • the multi-clutch arrangement may comprise at least three multi-plate clutches, wherein the multi-plate clutches each comprise an outer disc carrier and the outer disc carrier form the housing of the multiple clutch assembly.
  • this construction makes possible a multiple coupling arrangement which, apart from the outer disk carriers, has no housing components and as a result is space-saving, cost-effective and assembly-optimized. Furthermore, this can improve the shelf life of the multiple clutch assembly.
  • one of the multi-plate clutches may be designed as a starting clutch and another as a separating clutch.
  • the multiple clutch assembly may be a triple clutch assembly. This can be used in particular in hybridized dual-clutch transmissions.
  • At least one, in particular all, multi-plate clutch can be designed to run wet.
  • the invention relates to a hybrid dual-clutch transmission arrangement with a multiple clutch arrangement.
  • the hybrid dual clutch transmission arrangement is characterized in that the multiple clutch assembly is formed as described.
  • at least one further radial bearing in particular a pure radial bearing, can be arranged on the motor side of the multiple coupling arrangement. However, this is outside the multiple clutch assembly.
  • the radial bearing of the clutch assembly and another radial bearing can support the same component and be arranged radially one above the other.
  • the component may be a drive plate.
  • At least two further, in particular exactly two, radial bearings can be arranged on the motor side of the multiple clutch arrangement.
  • the first advantageously follows radially inward on the first and third radial bearings then within a hub.
  • the sequence is then preferred from radially outward to inward: outer-plate carrier - ball bearing - driving plate - needle bearing - hub - needle bearing.
  • the input side of the multiple clutch arrangement can thus be supported with at least four, in particular with exactly five, radial bearings. These are located in the axial end portions of the multiple clutch assembly.
  • the dual-clutch transmission arrangement may advantageously comprise an electric motor which is arranged axially parallel to the transmission input shafts. Furthermore, the electric motor can be connected via a chain with the multiple clutch assembly. For this purpose, for example, be attached to one of the outer disk carrier a sprocket.
  • the hybrid dual clutch transmission arrangement is designed in countershaft design. This means that the transmission has at least one countershaft.
  • the invention relates to a motor vehicle with a multiple clutch assembly and / or a dual clutch transmission arrangement.
  • the motor vehicle is characterized in that the multiple clutch assembly and / or the double clutch transmission assembly is formed as described.
  • Figure 1 is a motor vehicle
  • Figure 2 is a coupling arrangement.
  • the first drive unit preferably comprises an internal combustion engine.
  • the second drive unit 3 in particular switched off in the form of an electric motor, can either act as indicated by the line 6 or the dashed line indicated 7 on the drive train.
  • An interaction with one or both transmission input shafts is referred to as a P2 arrangement and an interaction with the transmission itself as a P3 arrangement.
  • a P1 and a P4 arrangement are known. These represent the basic variants of a parallel arrangement of the first drive unit 2 and the second drive unit 3.
  • a clutch arrangement for a P2 arrangement will be described below.
  • FIG. 2 shows a clutch arrangement 8 as part of the dual-clutch transmission arrangement 4.
  • the dual-clutch transmission arrangement 4 is hybridized, as a result of which torque can reach the transmission via two paths.
  • the first path leads from the first drive unit 2 via a torsion damper for damping torsional vibrations, in particular a dual-mass flywheel 9, and a hub 10 to the separating clutch K0.
  • the hub 10 With the hub 10 while the input disk carrier of the clutch K0, namely the inner disk carrier 12, rotatably connected.
  • the torque can be transferred to the Au zinclamellenwhere 16.
  • a piston 18 is present.
  • a speed-adaptive absorber 20 is attached on the output side of the separating clutch KO, namely on the output disk carrier, in this case the outer disk carrier 16, a speed-adaptive absorber 20 is attached.
  • the speed-adaptive absorber 20 is detachably connected to the outer disk carrier 16.
  • the absorber 20 may be screwed to the outer disk carrier 16 by means of a screw 22.
  • the screw head 24 is within the clutch assembly 8, while the nut 26 is arranged outside.
  • a sleeve 27 Between Tilger 20 and screw 26 is still a sleeve 27. This is used in closed ring said the axial spacing of the web plates of the absorber 20th
  • the outer disk carrier 16 of the outer disk carrier 28 is rotatably connected.
  • the outer disk carrier 16 and the outer disk carrier 28 may be positively connected.
  • a snap ring 30 can be used for axial securing of the outer disk carrier 16 relative to the outer disk carrier 18.
  • the outer disk carrier 28 is the input disk carrier of the clutch K2, which is designed as a multi-plate clutch and one of the two power-shift clutches of the dual-clutch transmission assembly 4 represents. If the separating clutch K0 is closed, the torque is transmitted via the outer disk carrier 16, the outer disk carrier 28 and the disk set 32 of the clutch K2 to the inner disk carrier 34 and from there to the radially inner transmission input shaft 36.
  • the absorber 20 can be removed from the outer disk carrier 16, whereby the transition point is exposed.
  • the clutch K2 on the piston 38 For actuation, the clutch K2 on the piston 38.
  • the piston 38 has distributed in the circumferential direction a plurality of openings 40 in the form of elongated holes into which the outer disk carrier 28 can engage. More specifically, a plurality of fingers 42 of the outer disk carrier 28 engage in the openings 40 of the piston 38.
  • the piston 38 is axially displaceable relative to the outer disk carrier 28.
  • the clutch K2 Radially inside the clutch K2 is the clutch K1, which is designed as a starting clutch.
  • the outer disk carrier 28 is rotatably connected to the outer disk carrier 44 of the clutch K1. In particular, the outer disk carrier 28 and 44 welded.
  • the outer disk carrier 44 is accordingly the input disk carrier of the clutch K1.
  • the torque can reach the radially outer transmission input shaft 37.
  • the openings 40 for receiving the fingers 42 are preferably arranged on the radially outer edge, also referred to as a pot edge, of the piston 38.
  • the piston 38 has a cup shape. At the outer edge of the bottom, the fingers 42 of the outer plate carrier 28 can be inserted, which is why the openings 40 are preferably located there.
  • FIG. 2 shows a P2 arrangement with respect to the coupling of the electric motor 3.
  • the clutch assembly 8 is a multiple clutch assembly, and in particular a triple clutch arrangement. Except the outer disk carriers 16, 28 and 44, there are no other housing parts. This results in a space-optimized design.
  • the connection of the outer disk carrier 16 and 28 take place before the absorber 20 is connected to the coupling assembly 8.
  • the structure described with the outer disk carriers as a housing also allows a simplified mounting of the clutch assembly 8.
  • the clutch assembly 8 may have a single radial bearing point 54 on the motor side.
  • the bearing 56 may be formed as a radial ball bearing. It may preferably be an axial and radial bearings.
  • the bearing 57 is arranged radially inside the bearing 56 and preferably designed as a needle bearing.
  • the bearing 56 and the radial bearing 57 are arranged above and below the foot of a driving plate 61.
  • the radial bearing 59 follows. This supports the hub 10.
  • the multiple clutch arrangement 8 can be optimally supported against tilting.
  • the clutch assembly 8 on the engine side and the transmission side each have two thrust bearings 58 and 56 and 58, respectively.
  • the thrust bearings 58 are used for the axial mounting of the hub 10 and the inner disk carrier 34 and 48. They are accordingly arranged on the feet of the inner disk carrier 34 and 48.
  • the bearings 58 are designed as needle bearings.
  • the bearing 56 is as described also a thrust bearing. It supports the outer disk carrier 16 axially.
  • the clutch assembly 8 for radial mounting on two needle bearings 60 which support the hub 62.
  • the hub 62 is formed as ⁇ lzu Siliconnabe. It accordingly includes oil channels and seals.
  • the hub 62 is rotatably connected to the outer disk carrier 44.
  • the torque flow does not take place via the hub on the outer disk carrier, as is the case with known dual clutch arrangements, but the torque comes from the outer disk carrier, to be more precise from the outer disk carrier 28 via the outer disk carrier 44 to the hub 62.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

L'invention concerne un système d'embrayage multiple (8) destiné à être monté entre une unité d'entraînement (2) et une boîte de vitesses (4), ledit système comprenant au moins deux embrayages multidisques (K0, K1, K2) comportant un porte-disques extérieur (16, 28, 44) et un élément d'actionnement (18, 38, 63) respectif. L'invention est caractérisée en ce que le système d'embrayage multiple (8) présente un seul point d'appui radial (54) côté moteur. L'invention concerne par ailleurs un système de boîte de vitesses à double embrayage. L'invention concerne en outre un véhicule à moteur.
EP18709993.2A 2017-04-11 2018-03-05 Système d'embrayage multiple, système de boîte de vitesses à double embrayage et véhicule à moteur Withdrawn EP3610166A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017206221.5A DE102017206221B4 (de) 2017-04-11 2017-04-11 Mehrfachkupplungsanordnung, Doppelkupplungsgetriebeanordnung sowie Kraftfahrzeug
PCT/EP2018/055247 WO2018188851A1 (fr) 2017-04-11 2018-03-05 Système d'embrayage multiple, système de boîte de vitesses à double embrayage et véhicule à moteur

Publications (1)

Publication Number Publication Date
EP3610166A1 true EP3610166A1 (fr) 2020-02-19

Family

ID=61616987

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18709993.2A Withdrawn EP3610166A1 (fr) 2017-04-11 2018-03-05 Système d'embrayage multiple, système de boîte de vitesses à double embrayage et véhicule à moteur

Country Status (3)

Country Link
EP (1) EP3610166A1 (fr)
DE (1) DE102017206221B4 (fr)
WO (1) WO2018188851A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018008912B3 (de) * 2018-11-12 2020-01-09 Daimler Ag Hybrid-Doppelkupplungsgetriebe
FR3117063B1 (fr) * 2020-12-04 2023-02-10 Valeo Embrayages Dispositif de transmission de couple, en particulier pour véhicule automobile

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10133638A1 (de) * 2001-07-11 2003-01-30 Zf Sachs Ag Mehrfach-Kupplungseinrichtung, insbesondere Doppel-Kupplungseinrichtung
DE10223780C1 (de) 2002-05-29 2003-10-16 Porsche Ag Gangschaltgetriebe für ein Kraftfahrzeug mit hydraulisch betätigbarer Mehrfachkupplung
DE102004012948B4 (de) 2004-03-17 2012-05-31 Zf Friedrichshafen Ag Doppelkupplungseinrichtung in axialer Bauart
DE102007009964A1 (de) 2006-03-22 2007-09-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulische betätigte Doppelkupplung
DE102006014562A1 (de) 2006-03-29 2007-10-04 Volkswagen Ag Kupplungsvorrichtung mit einer Kupplung und einem damit verbundenen Drehschwingungsdämpfer sowie Getriebe mit einer solchen Kupplungsvorrichtung
DE112009003882B4 (de) 2009-01-19 2018-09-13 Schaeffler Technologies AG & Co. KG Hybridmodul für einen Antriebsstrang eines Fahrzeuges
DE102010003442A1 (de) 2010-03-30 2011-10-06 Zf Friedrichshafen Ag Hybridantriebsanordnung
DE102016217211A1 (de) 2015-09-16 2017-03-16 Schaeffler Technologies AG & Co. KG Kupplungssystem

Also Published As

Publication number Publication date
DE102017206221A1 (de) 2018-10-11
DE102017206221B4 (de) 2022-12-22
WO2018188851A1 (fr) 2018-10-18

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