WO2020169140A1 - Système d'embrayage compact à système support de disques - Google Patents

Système d'embrayage compact à système support de disques Download PDF

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Publication number
WO2020169140A1
WO2020169140A1 PCT/DE2020/100025 DE2020100025W WO2020169140A1 WO 2020169140 A1 WO2020169140 A1 WO 2020169140A1 DE 2020100025 W DE2020100025 W DE 2020100025W WO 2020169140 A1 WO2020169140 A1 WO 2020169140A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
axis
rotation
carrier
arrangement
Prior art date
Application number
PCT/DE2020/100025
Other languages
German (de)
English (en)
Inventor
Pascal Carl
Oliver Nöhl
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
Publication of WO2020169140A1 publication Critical patent/WO2020169140A1/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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/68—Attachments of plates or lamellae to their supports
    • F16D13/683—Attachments of plates or lamellae to their supports for clutches with 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
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Definitions

  • the invention relates to a clutch arrangement for a drive train of a
  • Motor vehicle such as a car, truck, bus or other commercial vehicle, with three clutches.
  • the clutch arrangement is particularly suitable for a hybrid drive unit.
  • a hybrid drive unit is between an internal combustion engine, a
  • the hybrid drive unit comprises a hybrid module with a clutch arrangement to which the electric motor and the internal combustion engine are connected.
  • the clutch assembly includes a
  • Triple clutch consisting of a double clutch with two clutches and a separating clutch for coupling a drive element, for example the internal combustion engine.
  • a clutch arrangement has at least one clutch with two clutch components designed as disk carriers, namely for receiving an inner disk set on a first clutch component and for receiving an inner disk set on a second clutch component.
  • a well-known clutch component designed as a disk carrier has a disk pack on its radial inside or outside. This is pushed on axially and then secured against axial displacement on the coupling by a locking ring. The locking ring is in a
  • the securing ring groove is created by the material of the disk ring being stamped out radially in the radially opposite direction to the disk pack in order to ensure that the disk pack can be pushed on axially.
  • the material of the disk ring is used to manufacture the
  • Components usually have a corresponding installation space.
  • the object of the present invention is to create a clutch arrangement that is as compact as possible.
  • the invention thus relates to a clutch arrangement with an axis of rotation for a drive train of a motor vehicle, the clutch arrangement having:
  • first clutch component having a first first clutch component for a non-rotatable connection to an input shaft, wherein the first first clutch component has externally toothed first clutch inner disks,
  • Second clutch inner disks correlating to torque transmission
  • disk carrier is circumferentially meandering for the non-rotatable reception of the internally toothed first clutch outer disks and the externally toothed second clutch inner disks, so that the disk carrier has an outer tip radius and an inner root radius
  • the input shaft is in particular the crankshaft of an internal combustion engine.
  • Coupling component of the first clutch and the second clutch is used, the number of installed components can be reduced. Ultimately, this means that a single clutch component, i.e. the disk carrier, has two separate ones
  • Coupling components replaced. By saving a coupling component, installation space is thus saved.
  • a hydraulic fluid in particular oil
  • the rising pressure in the pressure chamber can act as the spring force of the outside of the pressure chamber on the pressure pot
  • the friction clutch can in particular be designed as a multi-disc clutch, in which the outer discs are non-rotatably connected to an outer disc carrier but axially displaceable, in particular designed as friction linings or steel plates, and the outer discs are non-rotatably connected to an inner disc carrier but are axially movable,
  • inner disks are provided alternately one behind the other, which can be frictionally pressed between the counter plate and the pressure plate in order to bring about a torque flow between the outer disk carrier and the inner disk carrier.
  • traction operation this can be done in an internal combustion engine and / or an electric one
  • Machine generated torque is introduced via the outer disc carrier and via the inner disc carrier, in particular to a transmission input shaft of a
  • the disk carrier is closed at a closed end along the axis of rotation insofar as it has a support structure that extends at least partially radially to the axis of rotation, the disk carrier circumferentially with a ring of fingers extending parallel to the axis of rotation, in particular uniformly distributed finger elements, the finger elements at the open end of the lamella carrier opposite the closed end having radially penetrating recesses on a projection plane perpendicular to the axis of rotation in order to counter a locking ring axially along the axis of rotation, the radially penetrating recesses one towards the finger rim
  • the closed end and the open end are separated axially along the axis of rotation by a disk pack to be assembled.
  • the axial end of the disk carrier which has the support structure running at least partially radially to the axis of rotation, is therefore considered to be the closed end.
  • the support structure is not closed radially, but is designed as a radial ring.
  • the open end is the axial end of the disk carrier, into which the ends of the finger elements point.
  • the design of the radially penetrating recesses is particularly advantageous because of their lack of material protrusion. This has the advantage that
  • Disk packs both an inner disk pack and an outer disk pack can be pushed on axially. This prevents the need for at least one of the two disk packs to be pushed onto the common disk carrier with increased application of force, so that a possible deformation of the disk carrier can be avoided.
  • the radially penetrating recesses are punched out. This is an inexpensive way of producing the recesses, whereby it is ensured that there is no radial material protrusion.
  • recesses are arranged in the root radius of the plate carrier.
  • a circlip can be mounted radially on the inside so that it is secured against opening at speed. The smaller the radius of one
  • the retaining ring is, the stiffer it is for the same axial length along the
  • the disk carrier is closed at a closed end along the axis of rotation insofar as it has a support structure that extends at least partially radially to the axis of rotation, the disk carrier circumferentially with a ring of fingers extending parallel to the axis of rotation, in particular uniformly distributed finger elements, wherein the finger rim at the closed end has material projections pointing radially outward on a sectional plane perpendicular to the axis of rotation, in order to counter a radially outer support body axially along the axis of rotation.
  • a support body which is secured against axial displacement along the axis of rotation, can thus be leaned against these material projections, in particular from the transmission side.
  • the closed end and the open end are separated axially along the axis of rotation by a disk pack to be assembled.
  • the axial end of the disk carrier which has the support structure running at least partially radially to the axis of rotation, is therefore considered to be the closed end.
  • the support structure is not closed radially, but is designed as a radial ring.
  • the open end is the axial end of the disk carrier, into which the ends of the finger elements point.
  • the material projections on the tip circle radius and / or on the root circle radius of the Finger ring are arranged. Advantages result in the power flow distribution depending on the design of the support body to be axially secured.
  • the inner section of the support body which correlates to the circumferential meander shape of the lamellar carrier, is used in particular
  • the meander shape can also be described as circumferentially distributed teeth. As many teeth can be used on the support body as the plate carrier has counter teeth. A few teeth on the support body are also sufficient. The support body ensures that the loads in the
  • Plate pack are evenly supported and introduced into the material protrusions of the plate carrier.
  • the support body has a double-arched shape, in particular an S-shape, with at least one arching axially counteracting the first clutch inner disks or the first clutch outer disks along the axis of rotation. It has been found that this configuration is as optimal as possible
  • the invention further relates to a disk carrier for a clutch arrangement with at least one of the preceding features, with at least one of the aforementioned features of the disk carrier.
  • the invention also relates to a support body for a coupling arrangement with at least one of the preceding features, with at least one of the aforementioned features of the support body.
  • Fig. 3 a perspective view of a finger element of the plate carrier according to Fig. 2,
  • FIG. 4 a sectional view of a disk carrier of the clutch arrangement according to FIG. 1,
  • FIG. 5 a perspective view of the plate carrier according to FIG. 4,
  • FIG. 6 a sectional view of a support body of the coupling arrangement according to FIG. 1
  • FIGS. 6 and 7 a perspective view of the support body according to FIGS. 6 and
  • FIG. 8 a sectional view of a triple coupling with a coupling arrangement according to FIG. 1.
  • FIG. 1 shows a section of a clutch arrangement 10 with an axis of rotation D for a drive train of a motor vehicle, the clutch arrangement 10 having:
  • first clutch component 14 for a rotationally fixed connection to an input shaft 16, wherein the first first clutch component 14 has externally toothed first clutch inner plates 18, furthermore having one with the first first coupling component 14
  • Second clutch component 26 which with the externally toothed
  • Second clutch inner disks 28 for torque transmission having correlating internally toothed second clutch outer disks 30,
  • the disk carrier 20 is circumferentially meandering for receiving the internally toothed first clutch outer disks 22 and the externally toothed second clutch inner disks 28 so that the disk carrier 20 has an outer tip circle radius K and an inner root circle radius F, an output configuration for a torque to be transmitted to a
  • the disk carrier 20 is thus designed as a common disk carrier 20 for the first clutch 12 and the second clutch 24. It is important here that both disk packs, that is to say the internally toothed first clutch outer disks 22 and the externally toothed second clutch inner disks 28, should be able to be pushed onto the disk carrier 20 along the axis of rotation D.
  • a disk carrier 20 according to the prior art, shown in FIG. 2, provides the finger elements 36 thereof, shown in more detail in FIG. 3, have radially embossed areas to form a locking ring groove for a locking ring.
  • an inner disk pack can be pushed onto the finger element 36 from the open end, but the embossed area blocks the pushing on of an outer disk pack.
  • the invention therefore preferably proposes that at the open end 38 of the disk carrier 20 radially
  • Cross-cut recesses 40 form a locking ring groove in which a
  • Retaining ring 41 for the axial securing and force support on the disk carrier 20 lies.
  • the recesses 40 can be punched out completely. This is advantageous since both the outer and the inner plate packs can be mounted on the plate carrier 20. If the retaining ring groove were to be produced only by stamping the material from the inside to the radially outside, as in the prior art according to FIGS. 2 and 3, the external lamellae would not be able to be installed without risking component deformation.
  • the recesses are at the root radius F of the plate carrier 20
  • the locking ring 41 can be mounted radially on the inside. Thus it is secured against opening under speed.
  • material projections 42 are embossed radially outward on the closed end 31 of the plate carrier 20. These material projections 42 are embossed radially outward at the tip circle radius K of the disk carrier 20. Alternatively, the material projections 42 can also be on the
  • Root radius F are embossed radially outward, or at the head and
  • Root radius K, F. A support body 44 is leaned against these material projections 42. This support body 44 also has teeth that are in a
  • Meander-shaped external toothing of the plate carrier 20 grip. These teeth serve in particular to prevent the support body 44 from rotating and do not transmit any torque. As many teeth can preferably be used as the plate carrier 20 also has teeth. However, a few teeth that are especially evenly distributed are sufficient.
  • the support body 44 has the effect that the loads supported disk pack are evenly supported and introduced into the material projections 42 of the disk carrier 20.
  • Clutch arrangement 10 for a drive train of a motor vehicle for a drive train of a motor vehicle.
  • Coupling arrangement 10 from FIG. 1 can thus form a section of the triple coupling according to FIG. 8.
  • the triple coupling has:
  • a housing 52 which, for example, delimits a wet space 54,
  • Input shaft 16 connected to the first separating clutch component and a second part rotatably connected to the first separating clutch component
  • Second clutch component 26 which with the externally toothed
  • Second clutch inner disks 28 for torque transmission having correlating internally toothed second clutch outer disks 30,
  • the disk carrier 20 is designed in a meandering shape around the circumference for the non-rotatable reception of the internally toothed first clutch outer disks 22 and the externally toothed second clutch inner disks 28,
  • Carrier body 56 interacts.
  • the input shaft 16 can in particular be a crankshaft of an internal combustion engine.
  • the output shaft of the first primary clutch component 14 is a solid transmission shaft and the output shaft of the second
  • Second clutch component 26 is a hollow transmission shaft.
  • damper unit 58 By integrating the damper unit 58 into the housing 52 designed as a wet space 54, it is possible, in particular, to save axial installation space along the axis of rotation D.
  • the formulation wet space 54 means here that it is a wet-running, that is to say oil-lubricated, clutch arrangement 10.

Abstract

L'invention concerne un système d'embrayage (10) pour une chaîne cinématique d'un véhicule à moteur, ledit système d'embrayage (10) comportant : un premier embrayage (18) et un deuxième embrayage (24) qui se partagent un support de disques (36) commun, le système d'embrayage (10) présentant un corps d'appui (44), de manière à placer les composants d'embrayage en contre-appui dans le sens axial sur le support de disques (36). Cette configuration du système d'embrayage (10) permet d'obtenir un encombrement compact.
PCT/DE2020/100025 2019-02-19 2020-01-15 Système d'embrayage compact à système support de disques WO2020169140A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019104079.5A DE102019104079A1 (de) 2019-02-19 2019-02-19 Kompakte Kupplungsanordnung mit Lamellenträgersystem
DE102019104079.5 2019-02-19

Publications (1)

Publication Number Publication Date
WO2020169140A1 true WO2020169140A1 (fr) 2020-08-27

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ID=69591523

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2020/100025 WO2020169140A1 (fr) 2019-02-19 2020-01-15 Système d'embrayage compact à système support de disques

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DE (1) DE102019104079A1 (fr)
WO (1) WO2020169140A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3123097B1 (fr) * 2021-05-18 2023-11-10 Valeo Embrayages Porte-disque assemblé et double embrayage humide comprenant ce porte-disque assemblé
DE102021126265B3 (de) 2021-10-11 2023-01-19 Schaeffler Technologies AG & Co. KG Kupplungsvorrichtung
DE102021126262B4 (de) 2021-10-11 2024-01-25 Schaeffler Technologies AG & Co. KG Kupplungsvorrichtung mit einer Schraubverbindung
DE102022101346A1 (de) 2022-01-21 2023-07-27 Schaeffler Technologies AG & Co. KG Lamellenträger mit Sicherungselement und Kupplungsvorrichtung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3922932A (en) * 1972-11-24 1975-12-02 Renault Crenellation drum; and epicyclic transmission incorporating the same
JPH0456968U (fr) * 1990-09-25 1992-05-15
DE102007027121A1 (de) * 2007-06-13 2008-12-18 Volkswagen Ag Doppelkupplung
WO2018153398A1 (fr) * 2017-02-24 2018-08-30 Schaeffler Technologies AG & Co. KG Système d'embrayage, module hybride et groupe motopropulseur pour véhicule automobile

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3922932A (en) * 1972-11-24 1975-12-02 Renault Crenellation drum; and epicyclic transmission incorporating the same
JPH0456968U (fr) * 1990-09-25 1992-05-15
DE102007027121A1 (de) * 2007-06-13 2008-12-18 Volkswagen Ag Doppelkupplung
WO2018153398A1 (fr) * 2017-02-24 2018-08-30 Schaeffler Technologies AG & Co. KG Système d'embrayage, module hybride et groupe motopropulseur pour véhicule automobile

Also Published As

Publication number Publication date
DE102019104079A1 (de) 2020-08-20

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