WO2020127370A1 - Transmission device for a motor vehicle - Google Patents

Transmission device for a motor vehicle Download PDF

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Publication number
WO2020127370A1
WO2020127370A1 PCT/EP2019/085782 EP2019085782W WO2020127370A1 WO 2020127370 A1 WO2020127370 A1 WO 2020127370A1 EP 2019085782 W EP2019085782 W EP 2019085782W WO 2020127370 A1 WO2020127370 A1 WO 2020127370A1
Authority
WO
WIPO (PCT)
Prior art keywords
torque
clutch
input
axis
output
Prior art date
Application number
PCT/EP2019/085782
Other languages
French (fr)
Inventor
Emmanuel Commeine
Gilles Lebas
Original Assignee
Valeo Embrayages
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 Valeo Embrayages filed Critical Valeo Embrayages
Priority to EP19832332.1A priority Critical patent/EP3899300A1/en
Priority to CN201980090635.6A priority patent/CN113366236A/en
Publication of WO2020127370A1 publication Critical patent/WO2020127370A1/en

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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
    • B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • 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
    • 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
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4825—Electric machine connected or connectable to gearbox input 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
    • F16D2021/0661—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 present invention relates to the field of transmissions for motor vehicles. It relates in particular to a torque transmission device intended to be placed in the traction chain of a motor vehicle, between a heat engine and a gearbox.
  • the invention relates more specifically to a torque transmission device for a hybrid type motor vehicle in which a rotating electric machine is arranged in the traction chain.
  • hybrid type motor vehicles comprising a torque transmission device disposed between an internal combustion engine and a gearbox, a rotary electrical machine as well as a clutch and a drive member. actuation of this clutch for coupling or uncoupling in rotation a crankshaft of the internal combustion engine to a rotor of the rotary electric machine.
  • the rotating electric machine can also constitute an electric brake or provide extra energy to the internal combustion engine to assist it or prevent it from stalling.
  • the electric machine can act as an alternator.
  • the rotating electric machine can also drive the vehicle independently of the internal combustion engine.
  • Such a rotary electrical machine can be in line with the torque transmission device, that is to say that the axis of rotation of the rotor of the rotary eclectic machine is coincident with the axis of rotation of the torque transmission device. torque as described in document FR 3 015 380.
  • the rotary electric machine can be offset relative to the torque transmission device, that is to say that the axis of rotation of the rotor of the rotary eclectic machine is offset from the axis of rotation of the torque transmission device.
  • the architecture of the torque transmission devices is becoming more and more compact and it is sometimes difficult to house all the components.
  • it is necessary to position the input clutch and the associated actuating member on the side of the heat engine, which poses a number of problems and in particular the supply of fluid to the clutch and its actuating member.
  • the torque transmission device between the heat engine and the electric machine described in the document FR 3 015 380 is not fully satisfactory. Indeed, it includes, on the same radial height, offset axially, the springs of a torsional oscillation damper and the linings of a friction clutch.
  • the clutch actuator also offset axially from the friction linings completes the device. This axial succession of elements of the transmission chain does not meet the compactness expectations of the current market.
  • the invention aims to improve the existing design by benefiting from a torque transmission device making it possible to reconcile the requirements of axial and / or radial compactness while guaranteeing a good supply of fluid to the clutch.
  • a torque transmission device in particular for a motor vehicle, comprising:
  • a first torque input element in rotation about an X axis capable of being coupled in rotation to a crankshaft of a heat engine, comprising a rear part and a front part,
  • an input clutch selectively and frictionally coupling the torque input and torque output elements
  • an actuation system associated with the input clutch comprising a pressure chamber and an axially movable piston, a protective casing arranged to at least partially envelop the torque input element, the torque output element, the input clutch and the actuation system, said casing having an axially extending internal wall around the X axis and comprising a network for the passage of a fluid arranged to supply said actuation system with fluid,
  • the protective casing is composed of a radial wall and an internal wall, the internal wall extending axially around the axis X.
  • the casing has a general shape substantially in "L" shape, the base of the "L” being located on the side of the axis of rotation X.
  • the fluid passage network comprises a first axial portion located in the internal wall and an upstream radial orientation pipe located in the radial wall of the protective casing and connected to the first portion.
  • the upstream pipe is formed in an upper portion of the casing, intended to be disposed above the X axis.
  • the upstream pipe thus makes it possible to conduct the fluid by gravity or by means of a device ensuring the flow of fluid, such as a pump or an actuator, to the first portion.
  • the protective casing can be fixed to the internal combustion engine by means of fixing means, for example of the screw or rivet type.
  • the housing protection can be fixed on the casing of the electric motor so as to ensure proper positioning of the clutch.
  • the fluid passage network is made of material with the protective casing. Consequently, the fluid passage network follows the shape of the protective casing and has a general shape substantially in an "L” shape, the base of the "L” being situated on the side of the axis of rotation X.
  • the rear part of the torque input element formed radially outside and inside said internal wall of the protective casing comprises at least one through hole which allows said fluid to pass through. across said part of the torque input element.
  • said element no longer forms an obstacle to the circulation of the fluid from the fluid passage network, this which facilitates the access of the fluid to certain elements arranged in its vicinity, such as a pressure chamber associated with an axially movable piston intended to transmit a force for actuation of the piston towards a multidisc assembly of the clutch inlet, a balancing chamber located opposite the pressure chamber with respect to the piston, and / or a needle bearing disposed between the torque input element and the hub of a shaft full of gearbox speeds.
  • the fluid is a cooling and / or lubrication fluid.
  • the fluid is oil, such as gearbox oil
  • the rear part of the torque input element is composed of a first and second axial portion as well as a radial wall connecting the first axial portion to the second axial portion.
  • the input clutch, the first axial portion, the internal wall of the protective casing, and the second axial portion succeed one another radially in approach to the axis X.
  • the radial succession is understood in terms of radial distance.
  • the various aforementioned elements do not overlap radially, that is to say that they are successively one under the other.
  • the device further comprises a rolling member located radially between the internal wall of the protective casing and the torque input element.
  • the rolling member supports the torque input element and is composed of an internal ring in contact with the torque input element, in particular the front part of the torque input element and d '' an outer ring in contact with the protective casing, in particular with the internal wall of the protective casing.
  • the device further comprises a first output clutch rotating around the axis X, selectively and frictionally coupling a second torque input element capable of being coupled to said first torque output element and a second torque output element capable of being coupled in rotation to a first input shaft of a gearbox.
  • the device further comprises a second output clutch rotating around the axis X, selectively and frictionally coupling said second torque input element and a third torque output element capable of being coupled in rotation to a second input shaft of a gearbox, the first and second output clutch being stacked radially.
  • the first output clutch is that located radially on the outside, that is to say the furthest from the axis of rotation X of the device.
  • the second output clutch is the one located radially inside, that is to say the one closest to the axis of rotation of the device.
  • the second torque input element corresponds to the input disc holder of a double clutch mechanism comprising the first and second output clutch.
  • the piston of each clutch actuating member can be controlled by an internal position sensor which controls the clutch or by measuring the hydraulic pressure when the clutch is closed or by measuring the volume of fluid injected or by measuring a displacement quantity in the electric motor or by measuring a force quantity or by measuring the current consumed in the electric motor.
  • the second torque input element comprises an electrical connection zone capable of being linked in rotation with an electric machine rotating about an axis parallel to the axis of rotation X.
  • the electrical connection zone is axially offset from the input clutch and / or the output clutches. The electric machine is then called "off-line”.
  • the electrical connection area can be welded, riveted or come in one piece with the second torque input element.
  • This arrangement makes it possible to position the electric machine as a function of the space available in the vehicle's traction chain. This arrangement makes it possible in particular not to have to place the electric machine axially following the clutches, which would be negative for the axial compactness. This arrangement makes it possible in particular not to have to place the electric machine radially beyond the clutches, which would be negative for the radial compactness.
  • the electrical connection zone of the second torque input element comprises a crown capable of being meshed directly by a pinion of the rotary electric machine.
  • the crown has a helical toothing of complementary shape to the pinion of the rotary electric machine.
  • a chain or belt can be used to connect the rotating electrical machine to the electrical connection area.
  • the second torque input element prefferably defines a rotor support for an electric machine rotating around the axis of rotation.
  • the electric machine is then "in-line”.
  • the clutches can be of the multi-disc type.
  • a multidisk assembly is an assembly comprising at least one friction disc integral in rotation with one of the input and output disc carriers, at least two plates respectively arranged on the side and other of each friction disc, integral in rotation with the other of the inlet and outlet disc holders and friction linings arranged between the plates and a friction disc, the clutches describing a disengaged position and a engaged position in which said plates and the friction disc pinch the friction linings so as to transmit a torque between an input disc holder and an output disc holder.
  • the clutch comprises between two and seven friction discs, preferably four friction discs.
  • the input and output clutches are wet.
  • the clutches being contained in at least one sealed chamber filled with a fluid, in particular oil.
  • a wet clutch is a clutch which is suitable for operating in an oil bath.
  • the electrical connection zone, the first output clutch and the second output clutch are stacked radially in proximity to the axis X.
  • FIG. 1 shows an axial sectional view of one of the torque transmission device according to an embodiment of the invention.
  • a torque transmission device 1 comprising:
  • the third output element 7 is arranged in parallel with the second output element 6 in the direction of the torque transmission. Each of these elements rotates around an axis of rotation X of the device.
  • the second and third output elements 6, 7 comprise output interfaces whose internal periphery is grooved and able to cooperate, respectively with a first and a second gearbox shaft.
  • a torsion damper device (not shown) can be positioned between the crankshaft of the heat engine and the torque input element 2.
  • the device also comprises an input clutch 10 which selectively and frictionally couples the torque input element 2 and the first torque output element 4 in the direction of the torque transmission.
  • the input clutch 10 comprises:
  • a multi-disc assembly 13 comprising several friction discs, here three, integral in rotation with the outlet disc holder 12, several plates respectively arranged on either side of each friction disc, integral in rotation with the disc holder inlet 11 and friction linings arranged between the plates and a friction disc, fixed on each side of the friction discs, the clutch 10 describing a disengaged position and a engaged position in which said plates and the friction disc pinch the linings friction so as to transmit a torque between the input disc holder and the output disc holder.
  • Each disc holder 1 1, 12 synchronizes in rotation all of the plates and all of the friction discs.
  • Each disc holder 11, 12 has a cylindrical skirt on which the plates and the friction discs are mounted.
  • the friction discs of the multidisc assembly 13 cooperate with the cylindrical skirt of the outlet disc holder 12 along their radially inner periphery by splines. The friction discs are therefore radially outside the cylindrical skirt.
  • the plates of the multidisc assembly 13 cooperate with the cylindrical skirt of the input disc carrier 1 1 along their radially outer periphery by splines. The plates are therefore radially inside the cylindrical skirt.
  • the torque input element 2 allows the arrangement of an actuation system 20 associated with the input clutch 10.
  • the device 1 also comprises a first output clutch E1 selectively and frictionally coupling the second torque input element 5 and the second torque output element 6.
  • the first output clutch E1 comprises :
  • a multi-disc assembly 123 comprising several friction discs, here four, integral in rotation with the outlet disc holder 122, several plates respectively arranged on either side of each friction disc, integral in rotation with the disc holder inlet 121 and friction linings arranged between the plates and a friction disc, fixed on each side of the friction discs, the clutch E1 describing a disengaged position and a engaged position in which said plates and the friction disc pinch the linings friction so as to transmit a torque between the input disc holder and the output disc holder.
  • the device 1 also comprises a second output clutch E2, selectively and frictionally coupling the second torque input element 5 and the third torque output element 7.
  • the first output clutch E2 includes:
  • a multi-disc assembly 133 comprising several friction discs, here five.
  • the 133 multi-disc assembly has the same technical characteristics as the E1 clutch multi-disc assembly.
  • the linings can be fixed to the friction discs, in particular by gluing, in particular by riveting, in particular by overmolding.
  • the linings are fixed to the plates.
  • Each disc holder 11, 12, 121, 122, 131, 132 can synchronize in rotation all of the plates or all of the friction discs.
  • the plates can be secured in rotation to the input disc holder 1 1, 121, 131 and the friction discs can be secured to the outlet disc holder 12, 122, 132.
  • the plates can be integral in rotation with the output disc holder 12, 122, 132.
  • the discs can be secured in rotation with the input disc holder 1 1, 21, 31.
  • the clutches are wet type and have between two and seven friction discs, preferably four friction discs. Such multi-disc clutches make it possible to limit the radial height and limit the axial extent.
  • the output clutches E1, E2 can be arranged so as not to be simultaneously in the same clutch configuration. However, they can simultaneously be configured in their disengaged position.
  • the device 1 further comprises a protective casing 27 arranged to at least partially envelop the torque input element 2, the torque output element 4 the input clutch 10 and the actuation system 20.
  • the casing 27 is composed of a radial wall 26 and an internal wall 28 extending axially around the axis X and has a general shape substantially in "L" shape, the base of the "L” being located on the side of the axis of rotation X.
  • the casing comprises a network for the passage of a fluid 80 arranged to supply fluid to said actuation system 20.
  • the network for the passage of fluid 80 comprises a first axial portion 81 situated in the wall internal and an upstream pipe 82 of radial orientation situated in the radial wall 26 of the protective casing connected to the first portion 81.
  • the upstream pipe 82 is formed in an upper portion of the casing, intended to be disposed above the X axis.
  • the upstream pipe 82 thus makes it possible to conduct the fluid by gravity or by means of a device ensuring the flow of the fluid, such as a pump or an actuator, to the first portion 81.
  • the torque input element 2 consists of a rear part 2a and a front part 2b.
  • the rear part 2a of the torque input element 2 is formed radially outside and inside said internal wall 28.
  • the internal wall 28 is surrounded radially on both sides by the rear part 2a.
  • the rear part 2a of the torque input element 2 is composed of a first and second axial portion 2ai, 2a3 as well as a radial wall 2a2 connecting the first axial portion to the second axial portion.
  • the input clutch 10, the first axial portion 2ai, the internal wall 28 of the protective casing 27, and the second axial portion 2a 3 succeed one another radially in proximity to the axis X.
  • c ' is the first axial portion 2ai which is formed radially outside the internal wall 28 and it is the second axial portion 2a3 which is formed radially inside the internal wall 28.
  • the casing 27 is sealed by means of a series of seals. More particularly, a seal 29 is arranged radially between the internal wall 28 and the second axial portion 2a 3 . According to another embodiment, the seal 29 can be integrated at bearing 90 or be located in front of the bearing.
  • the seals used in the context of the present invention can be dynamic lip seals.
  • the casing 27 can be fixed to the internal combustion engine or to the engine of the electric machine by means of fixing means, for example of the visible screw or rivet type.
  • the rear part 2a of the torque input element 2 comprises at least one through hole which allows the passage of the cooling and / or lubrication fluid through said rear wall 2a.
  • the rear part 2a comprises at least two bores 83 passing radially through the first axial portion 2ai, said portion being located radially outside the internal wall 28 so as to allow the passage of the fluid radially through the first axial portion 2ai.
  • the through holes 83 allow the fluid to be brought into the actuation system 20.
  • the device further comprises a main hub 50 of axis of rotation X.
  • the second torque input element 5 also called input disk holder 5 common to the output clutches E1 and E2 is fixedly fixed by welding to main hub 50.
  • the main hub 50 supports the first and second output clutch E1, E2 via the common input disc carrier 5.
  • the main hub 50 is therefore coupled in rotation to the torque input element 2
  • the torque input element 2 is coupled to an engine shaft driven in rotation by the crankshaft of an engine, as described above, and the clutch 10 is closed, then the main hub 50 is driven by 'a rotation movement similar to that of the motor shaft.
  • the first output clutch E1 is arranged radially above the second output clutch E2.
  • the input clutch 10, the first clutch E1 and the second clutch E2 are in the open state, also called “normally open”, and are selectively actuated in operation by a control device (not shown) for passing from the open state to the closed state.
  • the clutches are each controlled by an actuation system 20, 30, 40 which will be described later.
  • Each actuation system 20, 30, 40 is arranged to be able to configure the clutches in any configuration between the clutch configuration and the disengaged configuration.
  • control device manages the oil supply.
  • the control device is connected to the housing of protection 27 which includes the fluid passage network 80 as well as to the main hub 50 which comprises channels not visible on the section planes of FIG. 1.
  • Each actuation system 20, 30, 40 includes:
  • a pressure chamber 21, 31, 41 arranged to receive a pressurized fluid
  • Each actuation system 20, 30, 40 further comprises an elastic return element 24, 34, 44, arranged to generate an axial force opposing the movement of the piston
  • the piston 22 is arranged to transmit a first axial force, exerted parallel to the longitudinal axis X, to the input clutch 10 via an upper part collaborating with the friction elements (flanges 13 and friction discs 14) of said input clutch 10, and of a lower part collaborating with a force generator to configure the input clutch 10 in one of the configurations detailed above.
  • the piston 22 includes external supports 61 which extend axially towards the front AV in order to be able to press the end flange 13 of the multidisk assembly 12 of the input clutch 10 against a friction disc 14 on the one hand, and against an external reaction means formed directly in the first torque output element 4 on the other hand.
  • the supports 61 are discontinuous.
  • the piston 22 is axially movable, here from rear to front between a disengaged position and a engaged position which correspond respectively to the open and closed states of the input clutch 10.
  • the piston 22 of the clutch inlet 10 is disposed axially between the pressure chamber 21, located axially at the rear and the balancing chamber 23 located axially at the front.
  • the piston 22 takes the form of a corrugated sheet and is curved axially forwards AV at its outer radial end.
  • the external supports 61 extend parallel to the longitudinal axis X towards the front AV and through openings arranged through the entry web 15.
  • the piston 22 can be obtained by stamping.
  • the pressure chamber 21 of the actuation system 20 of the input clutch 10 is arranged to receive a certain volume of hydraulic fluid under pressure in order to generate an axial force on the lower part of the piston 22 and thus to configure the input clutch 10 in one of the configurations described above.
  • the pressurized hydraulic fluid is advantageously routed via the fluid passage network 80 (pipes 81 and 82 as shown on the cutting plane) then by at least one bore passing at least in part through the torque input element. 2, in particular the first axial portion 2ai, and opening radially into the pressure chamber 21 at an external face of said axial portion 2ai.
  • the pressure chamber 21 which generates the force of the piston 22 of the input clutch 10 is associated with a balancing chamber 23 arranged to receive a certain volume of hydraulic fluid.
  • the fluid, of the lubrication or cooling type is advantageously conveyed by means of low pressure fluidic circulation conduits (not shown on the cutting plane) then by at least one bore passing at least partially through the inlet element. of torque 2, in particular the first axial portion 2ai, and opening radially into the balancing chamber 23 at an external face of said axial portion 2ai.
  • the hole A leaks from the balancing chamber 23. This leak allows the lubrication of the clutch 10 by means of radial holes arranged on the torque output element (4) (not shown).
  • the elastic return element 24 of the actuating system 20 of the input clutch 10 is located radially outside the balancing chamber 23.
  • the elastic return element 34 is disposed axially between the input web 15 and the piston 22 of the actuating system 10 of the input clutch.
  • the piston 22 has a curved outer radial end defining a bearing surface for exerting the axial force on the multidisc assembly, continuous or discontinuous in the example considered.
  • the piston 32 is arranged to transmit an axial force, exerted parallel to the longitudinal axis X, to the first clutch E1 via a first part upper collaborating with the friction elements of said first clutch E1, and its second lower part collaborating with a force generator to configure the first clutch E1 in one of the configurations detailed above.
  • the piston 32 includes external supports which extend axially towards the front AV in order to be able to press the end flange of the multidisk assembly of the first clutch E1 against a friction disc on the one hand , and against an external reaction means formed directly in the first torque output element 3 on the other hand.
  • the supports are discontinuous.
  • the piston 32 is axially movable, here from rear to front between a disengaged position and a engaged position which correspond respectively to the open and closed states of the first clutch E1.
  • the piston 32 of the first clutch E1 is disposed axially between the pressure chamber 31, located axially at the rear and the balancing chamber 33 located axially at the front.
  • the piston 32 takes the form of a corrugated sheet and is curved axially forwards AV at its outer radial end.
  • the external supports extend parallel to the longitudinal axis X towards the front AV and through openings arranged through the common input disc holder 5.
  • the piston 32 can be obtained by stamping.
  • the pressure chamber 31 of the actuation system 30 is arranged to receive a certain volume of hydraulic fluid under pressure in order to generate an axial force on the second part of the piston 32 and thus to configure the first clutch E1 in one of the configurations previously described.
  • the pressurized hydraulic fluid is advantageously conveyed by means of high pressure fluidic circulation conduits (not shown on the cutting plane) passing at least partially through the main hub 50 and opening radially into the pressure chamber 31 at a outer face of said main hub 50.
  • the pressure chamber 31 which generates the force of the piston 32 of the first clutch E1 is associated with a balancing chamber 33 arranged to receive a certain volume of hydraulic fluid.
  • the fluid, of the lubrication or cooling type is advantageously conveyed by means of low pressure fluidic circulation conduits (not shown on the cutting plane) passing through at least part of the hub. main 50 and opening radially into the balancing chamber 33 at an external face of said main hub 50.
  • the elastic return element 34 of the actuation system 30 of the first clutch E1 is located radially outside the balancing chamber 33 of the first clutch E1.
  • the elastic return element 34 is disposed axially between the input disc carrier common 5 to the clutches E1, E2 and the piston 32 of the actuation system 30 of the first clutch E1.
  • the second clutch E2 and the elastic return element 34 of the actuation system 30 of the first clutch E1 overlap radially.
  • the elastic return element 34 of the actuation system 30 of the first clutch E1 is a Belleville washer or is composed of helical springs.
  • the elastic return element 34 of the piston 32 is formed by a plurality of helical springs interposed axially between a rear wall of the balancing cover 35 and said piston 32.
  • the actuation system 40 is linked to the second clutch E2 by means of a piston 42.
  • the piston 42 is arranged to transmit a second axial force, exerted parallel to the longitudinal axis X, to the first second clutch E2 via a first upper part collaborating with the friction elements (flanges and friction discs) of said second clutch E2, and its second lower part collaborating with a force generator to configure the second clutch E2 in one of the configurations detailed above.
  • the piston 42 includes external supports which extend axially towards the rear AR. The supports come to bear on the end flange of the multi-disc assembly of the second clutch E2. In the example shown in Figure 1, the supports form a continuous crown.
  • the second piston 42 is axially movable, here from front to rear between a disengaged position and a engaged position which correspond respectively to the open and closed states of the second clutch E2.
  • the piston 32 of the first clutch E1 and the piston 42 of the second clutch E2 move axially in the opposite direction to pass for example from the disengaged position to the engaged position.
  • the pressure chambers 31, 41 of the present invention exert axially opposite actuation forces on said pistons 32, 42.
  • the actuation force of the piston 32 is directed axially forward while the force actuating piston 42 is directed axially rearward.
  • the piston 42 is controlled to clamp axially, in the engaged position, said multidisk assembly of the second clutch E2 against reaction means.
  • the reaction means are formed directly on the front periphery of the common input disc holder 5.
  • the elastic return element 44 of the actuation system 40 of the second clutch E2 is formed by a plurality of helical springs interposed axially between a front wall of a balancing cover 45 of the chamber d balancing 43 and said piston 42.
  • Holes B and C leak the balancing chambers E1 and E2 in order to lubricate and / or cool them.
  • the torque transmission device also comprises three bearings 71, 72, 73.
  • a first axial bearing 71 is interposed between the torque input element 2 and the output element 6 in order to withstand the axial forces of the torque input element 2 despite the different rotational speeds which can respectively rotate the input shaft and the first transmission shaft.
  • a second axial bearing 72 is axially interposed between the torque output element 6 defining the clutch output disc holder E1 and the torque output element 7 defining the clutch output disc holder E2 in order to be able to transmit an axial load between the two output disc carriers 22, 32 which can rotate at different speeds when the first and second clutches E1, E2 are configured in a different configuration
  • a third axial bearing 73 is interposed between the torque output element 7 of the clutch E2 and the main hub 50.
  • the bearings 71, 72, 73 are rolling bearings with a first and second disc between which a plurality of rolling bodies is disposed.
  • the device further comprises a rolling member 90, preferably a ball bearing, located radially between the internal wall 28 of the protective casing 27 and the torque input element 2, preferably between the internal wall 28 and the second axial portion 2a3, of the rear part 2a.
  • a rolling member 90 preferably a ball bearing
  • the rolling member 90 supports the torque input element 2 and is composed of an internal ring 90b in contact with the torque input element 2 in particular the front part 2b of the element torque input and an external ring 90a in contact with the protective casing 27, in particular with the internal wall 28 of the protective casing.
  • the second torque input element 5 comprises an electrical connection area 65 capable of being linked in rotation with a rotary electrical machine (not shown) around an axis parallel to the axis of rotation.
  • the electrical connection area 65 is here axially offset from the clutch 10.
  • the electrical connection area 65, the first output clutch E1 and the second output clutch E2 are stacked radially in proximity to the X axis.
  • the electric machine is so-called "off-line” because it is not concentric with the drive shaft but on a parallel shaft.
  • the electrical connection area 65 is able to cooperate directly with a pinion of the rotary electrical machine.
  • the electrical connection area 65 can be produced in the form of a crown capable of being meshed directly by a pinion or indirectly (belt, chain, etc.) of the rotary electrical machine (not visible).
  • the crown can have a helical toothing of complementary shape to the pinion of the rotary electric machine.

Abstract

Disclosed is a torque transmission device (1), in particular for a motor vehicle, comprising: - a first torque input element (2) rotating about an axis X, capable of being coupled to rotate with a crankshaft of a heat engine, comprising a rear portion (2a) and a front portion (2b), - a first torque output element (4), - an input clutch (10) selectively coupling, by friction, the torque input element (2) and torque output element (4), - an actuating system (20) associated with the input clutch (10) comprising a pressure chamber (21) and an axially movable piston (22), - a protective casing (27) designed to at least partially enclose the torque input element (2), the torque output element (4), the input clutch (10) and the actuating system (20), the casing (27) comprising an inner wall (28) extending axially around the axis X and a fluid passage network (80) designed to supply fluid to the actuating system (20), wherein said rear portion (2a) is arranged radially outside and inside the internal wall (28).

Description

Description Description
Titre de l'invention : Dispositif de transmission pour Title of the invention: Transmission device for
véhicule automobile motor vehicle
[La présente invention se rapporte au domaine des transmissions pour véhicules automobiles. Elle se rapporte notamment à un dispositif de transmission de couple destiné à être disposé dans la chaîne de traction d’un véhicule automobile, entre un moteur thermique et une boîte de vitesses. [The present invention relates to the field of transmissions for motor vehicles. It relates in particular to a torque transmission device intended to be placed in the traction chain of a motor vehicle, between a heat engine and a gearbox.
L’invention concerne plus précisément un dispositif de transmission de couple pour un véhicule automobile de type hybride dans lequel une machine électrique tournante est disposée dans la chaîne de traction. The invention relates more specifically to a torque transmission device for a hybrid type motor vehicle in which a rotating electric machine is arranged in the traction chain.
Dans l’état de la technique, il est connu des véhicules automobiles de type hybride comprenant un dispositif de transmission de couple disposé entre un moteur à combustion interne et une boîte de vitesses, une machine électrique tournante ainsi qu’un embrayage et un organe d’actionnement de cet embrayage permettant d’accoupler ou désaccoupler en rotation un vilebrequin du moteur à combustion interne à un rotor de la machine électrique tournante. Ainsi, il est possible de couper le moteur à combustion interne à chaque arrêt du véhicule et de le redémarrer grâce à la machine électrique tournante. La machine électrique tournante peut également constituer un frein électrique ou apporter un surplus d’énergie au moteur à combustion interne pour l’assister ou éviter que celui-ci ne cale. Lorsque le moteur à combustion interne est en fonctionnement, la machine électrique peut jouer le rôle d’un alternateur. La machine électrique tournante peut également assurer l’entraînement du véhicule indépendamment du moteur à combustion interne. In the prior art, hybrid type motor vehicles are known comprising a torque transmission device disposed between an internal combustion engine and a gearbox, a rotary electrical machine as well as a clutch and a drive member. actuation of this clutch for coupling or uncoupling in rotation a crankshaft of the internal combustion engine to a rotor of the rotary electric machine. Thus, it is possible to shut down the internal combustion engine at each stop of the vehicle and to restart it thanks to the rotating electric machine. The rotating electric machine can also constitute an electric brake or provide extra energy to the internal combustion engine to assist it or prevent it from stalling. When the internal combustion engine is running, the electric machine can act as an alternator. The rotating electric machine can also drive the vehicle independently of the internal combustion engine.
Une telle machine électrique tournante peut être en ligne avec le dispositif de transmission de couple, c'est-à-dire que l'axe de rotation du rotor de la machine éclectique tournante est confondu avec l’axe de rotation du dispositif de transmission de couple comme décrit dans le document FR 3 015 380. En variante, la machine électrique tournante peut être déportée par rapport au dispositif de transmission de couple, c'est-à-dire que l'axe de rotation du rotor de la machine éclectique tournante est décalé de l’axe de rotation du dispositif de transmission de couple. L’architecture des dispositifs de transmission de couple est de plus en plus compacte et il est parfois difficile de loger tous les composants. Ainsi, du fait de la présence de la machine électrique tournante, il est nécessaire du positionner l’embrayage d’entrée et l’organe d’actionnement associé du côté du moteur thermique, ce qui pose un certain nombre de problèmes et notamment l’alimentation en fluide de l’embrayage et de son organe d’actionnement. Such a rotary electrical machine can be in line with the torque transmission device, that is to say that the axis of rotation of the rotor of the rotary eclectic machine is coincident with the axis of rotation of the torque transmission device. torque as described in document FR 3 015 380. As a variant, the rotary electric machine can be offset relative to the torque transmission device, that is to say that the axis of rotation of the rotor of the rotary eclectic machine is offset from the axis of rotation of the torque transmission device. The architecture of the torque transmission devices is becoming more and more compact and it is sometimes difficult to house all the components. Thus, due to the presence of the rotary electrical machine, it is necessary to position the input clutch and the associated actuating member on the side of the heat engine, which poses a number of problems and in particular the supply of fluid to the clutch and its actuating member.
Dans les développements actuels d’hybridation (« hybridisation » en anglais) des véhicules automobiles, il est demandé de disposer de chaîne de transmission intégrant une source d’énergie électrique sans toutefois que cela n’impacte la compacité axiale et radiale, de ladite chaîne de transmission. Du fait de la présence d’un embrayage de type humide, il a fallu concevoir un dispositif de transmission de couple permettant d’alimenter en fluide l’embrayage sans modifier l’encombrement du dispositif de transmission de couple. Cette recherche de compacité est à la base de l’invention. In current developments in hybridization of motor vehicles, it is requested to have a transmission chain incorporating an electrical energy source without however this impacting the axial and radial compactness of said chain. of transmission. Due to the presence of a wet-type clutch, it was necessary to design a torque transmission device allowing the clutch to be supplied with fluid without modifying the size of the torque transmission device. This search for compactness is the basis of the invention.
Dans cette logique, le dispositif de transmission de couple entre le moteur thermique et la machine électrique décrit dans le document FR 3 015 380 n’est pas pleinement satisfaisant. En effet, il comprend, sur une même hauteur radiale, décalés axialement, les ressorts d’un amortisseur d’oscillations de torsion et les garnitures d’un embrayage à friction. L’actionneur d’embrayage lui aussi décalé axialement des garnitures de friction complète le dispositif. Cette succession axiale d’éléments de la chaîne de transmission ne répond pas aux attentes de compacité du marché actuel. In this logic, the torque transmission device between the heat engine and the electric machine described in the document FR 3 015 380 is not fully satisfactory. Indeed, it includes, on the same radial height, offset axially, the springs of a torsional oscillation damper and the linings of a friction clutch. The clutch actuator also offset axially from the friction linings completes the device. This axial succession of elements of the transmission chain does not meet the compactness expectations of the current market.
Il est également connu des dispositifs dans lesquels l’alimentation en fluide destiné au refroidissement et/ou l’actionnement des embrayages, notamment de l’embrayage d’entrée, se fait coté boite de vitesses, notamment au travers de l’un des arbres d’entrée de la boîte de vitesses, ce qui complexifie la fabrication de la boîte de vitesses. Devices are also known in which the supply of fluid intended for cooling and / or actuation of the clutches, in particular of the input clutch, is done on the gearbox side, in particular through one of the shafts input of the gearbox, which complicates the manufacture of the gearbox.
L’invention vise à améliorer la conception existante en bénéficiant d’un dispositif de transmission de couple permettant de concilier les exigences de compacité axiale et/ou radiale tout en garantissant une bonne alimentation de l’embrayage en fluide. The invention aims to improve the existing design by benefiting from a torque transmission device making it possible to reconcile the requirements of axial and / or radial compactness while guaranteeing a good supply of fluid to the clutch.
L’invention y parvient, selon l’un de ses aspects, grâce à un dispositif de transmission de couple, notamment pour véhicule automobile, comprenant : The invention achieves this, according to one of its aspects, thanks to a torque transmission device, in particular for a motor vehicle, comprising:
un premier élément d’entrée de couple en rotation autour d’un axe X, apte à être couplé en rotation à un vilebrequin d’un moteur thermique, comprenant une partie arrière et une partie avant, a first torque input element in rotation about an X axis, capable of being coupled in rotation to a crankshaft of a heat engine, comprising a rear part and a front part,
un premier élément de sortie de couple, a first torque output element,
un embrayage d’entrée accouplant sélectivement et par friction les éléments d’entrée de couple et de sortie de couple, an input clutch selectively and frictionally coupling the torque input and torque output elements,
un système d’actionnement associé à l’embrayage d’entrée comprenant une chambre de pression et un piston mobile axialement, un carter de protection agencé pour envelopper au moins partiellement l’élément d’entrée de couple, l’élément de sortie de couple, l’embrayage d’entrée et le système d’actionnement, ledit carter comportant une paroi interne s’étendant axialement autour de l’axe X et comprenant un réseau de passage d’un fluide agencé pour alimenter en fluide ledit système d’actionnement, an actuation system associated with the input clutch comprising a pressure chamber and an axially movable piston, a protective casing arranged to at least partially envelop the torque input element, the torque output element, the input clutch and the actuation system, said casing having an axially extending internal wall around the X axis and comprising a network for the passage of a fluid arranged to supply said actuation system with fluid,
dans lequel la partie arrière est ménagé radialement à l’extérieur et à l’intérieur de ladite paroi interne. in which the rear part is formed radially outside and inside said internal wall.
Grâce à cette architecture, l’ensemble des composants associé à l’embrayage d’entrée sont concentriques. En particulier, le fait qu’une partie arrière de l’élément d’entrée de couple soit disposé radialement à l’extérieur et intérieur de paroi interne permet à l’élément d’entrée de couple d’envelopper cette paroi, ce qui entraîne une réduction de l’encombrement axial. Thanks to this architecture, all of the components associated with the input clutch are concentric. In particular, the fact that a rear part of the torque entry element is arranged radially on the outside and inside of the internal wall allows the torque entry element to wrap this wall, which causes a reduction in axial dimensions.
Dans la suite de la description et les revendications, on utilisera à titre non limitatif et afin d'en faciliter la compréhension, les termes : In the following description and claims, the following terms will be used without limitation and in order to facilitate understanding:
- « avant » AV ou « arrière » AR selon la direction par rapport à une orientation axiale déterminée par l’axe X principal de rotation de la transmission du véhicule automobile « l’arrière » désignant la partie située à droite des figures, du côté de la transmission, et « l’avant » AV désignant la partie gauche des figures, du côté du moteur ; et - “front” AV or “rear” AR according to the direction relative to an axial orientation determined by the main axis X of rotation of the transmission of the motor vehicle “the rear” designating the part situated to the right of the figures, on the side of the transmission, and the "front" AV designating the left part of the figures, on the engine side; and
- « intérieur /interne » ou « extérieur / externe » par rapport à l’axe X et suivant une orientation radiale, orthogonale à ladite orientation axiale, « l’intérieur » désignant une partie proximale de l’axe longitudinal X et « l’extérieur » désignant une partie distale de l’axe longitudinal X. - "inside / inside" or "outside / outside" relative to the X axis and in a radial orientation, orthogonal to said axial orientation, "inside" designating a proximal part of the longitudinal axis X and "l ' exterior ”designating a distal part of the longitudinal axis X.
Selon un mode de réalisation, le carter de protection est composé d’une paroi radiale et d’une paroi interne, la paroi interne s’étendant axialement autour de l’axe X. Le carter présente une forme générale sensiblement en « L », la base du « L » étant située du côté de l’axe de rotation X. Ainsi, le réseau de passage de fluide comporte une première portion axiale située dans la paroi interne et une conduite amont d’orientation radiale située dans la paroi radiale du carter de protection et reliée à la première portion. According to one embodiment, the protective casing is composed of a radial wall and an internal wall, the internal wall extending axially around the axis X. The casing has a general shape substantially in "L" shape, the base of the "L" being located on the side of the axis of rotation X. Thus, the fluid passage network comprises a first axial portion located in the internal wall and an upstream radial orientation pipe located in the radial wall of the protective casing and connected to the first portion.
Selon un mode de réalisation, la conduite amont est ménagée dans une portion supérieure du carter, destinée à être disposée au-dessus de l’axe X. La conduite amont permet ainsi de conduire le fluide par gravité ou au moyen d’un appareil assurant l’écoulement du fluide, tel qu'une pompe ou un actionneur, vers la première portion. According to one embodiment, the upstream pipe is formed in an upper portion of the casing, intended to be disposed above the X axis. The upstream pipe thus makes it possible to conduct the fluid by gravity or by means of a device ensuring the flow of fluid, such as a pump or an actuator, to the first portion.
Le carter de protection peut être fixé au moteur à combustion interne par l’intermédiaire de moyens de fixation, par exemple de type vis ou rivet. En variante, le carter de protection peut être fixé sur le carter du moteur électrique de façon à assurer un bon positionnement de l’embraye. The protective casing can be fixed to the internal combustion engine by means of fixing means, for example of the screw or rivet type. Alternatively, the housing protection can be fixed on the casing of the electric motor so as to ensure proper positioning of the clutch.
Selon un mode de réalisation, le réseau de passage de fluide est issu de matière avec le carter de protection. En conséquence, le réseau de passage de fluide épouse la forme du carter de protection et présente une forme générale sensiblement en « L », la base du « L » étant située du côté de l’axe de rotation X. Par « issue de matière avec le carter », on entend au sens de la présente invention « formé d’un seul tenant avec le carter ». According to one embodiment, the fluid passage network is made of material with the protective casing. Consequently, the fluid passage network follows the shape of the protective casing and has a general shape substantially in an "L" shape, the base of the "L" being situated on the side of the axis of rotation X. By "coming from material with the casing "means in the sense of the present invention" formed integrally with the casing ".
Selon un mode de réalisation, la partie arrière de l’élément d’entrée de couple ménagé radialement à l’extérieur et à l’intérieur de ladite paroi interne du carter de protection comporte au moins un perçage traversant qui autorise le passage dudit fluide au travers de ladite partie de l’élément d’entrée de couple. Ainsi, grâce au(x) perçage(s) ménagé(s) dans la partie arrière de l’élément d’entrée de couple, ledit élément ne forme plus un obstacle à la circulation du fluide depuis le réseau de passage de fluide, ce qui permet de faciliter l’accès du fluide à certains éléments disposés à sa proximité, tels qu’une chambre de pression associée à un piston mobile axialement destiné à transmettre un effort d’actionnement du piston vers un ensemble multidisque de l’embrayage d’entrée, une chambre d’équilibrage située à l’opposé de la chambre de pression par rapport au piston, et/ou un roulement à aiguilles disposé entre l’élément d’entrée de couple et le moyeu d’un arbre plein de boite de vitesses. According to one embodiment, the rear part of the torque input element formed radially outside and inside said internal wall of the protective casing comprises at least one through hole which allows said fluid to pass through. across said part of the torque input element. Thus, thanks to the bore (s) made in the rear part of the torque input element, said element no longer forms an obstacle to the circulation of the fluid from the fluid passage network, this which facilitates the access of the fluid to certain elements arranged in its vicinity, such as a pressure chamber associated with an axially movable piston intended to transmit a force for actuation of the piston towards a multidisc assembly of the clutch inlet, a balancing chamber located opposite the pressure chamber with respect to the piston, and / or a needle bearing disposed between the torque input element and the hub of a shaft full of gearbox speeds.
Selon un mode de réalisation, le fluide est un fluide de refroidissement et/ou de lubrification. According to one embodiment, the fluid is a cooling and / or lubrication fluid.
Selon un mode de réalisation, le fluide est de l’huile, tel que de l’huile de boîte de vitesses According to one embodiment, the fluid is oil, such as gearbox oil
Selon un mode de réalisation, la partie arrière de l’élément d’entrée de couple est composée d’une première et deuxième portion axiale ainsi que d’une paroi radiale reliant la première portion axiale à la deuxième portion axiale. According to one embodiment, the rear part of the torque input element is composed of a first and second axial portion as well as a radial wall connecting the first axial portion to the second axial portion.
Selon un mode de réalisation, l’embrayage d’entrée, la première portion axiale, la paroi interne du carter de protection, et la deuxième portion axiale se succèdent radialement en rapprochement de l’axe X. Au sens de l’invention, la succession radiale se comprend en terme de distance radiale. Avantageusement, les différents éléments précités ne se chevauchent pas radialement, c'est-à-dire qu’ils sont successivement les uns sous les autres. According to one embodiment, the input clutch, the first axial portion, the internal wall of the protective casing, and the second axial portion succeed one another radially in approach to the axis X. Within the meaning of the invention, the radial succession is understood in terms of radial distance. Advantageously, the various aforementioned elements do not overlap radially, that is to say that they are successively one under the other.
Selon un mode de réalisation, i’au moins un perçage traverse radialement la première portion axiale, ladite portion étant située radialement à l’extérieur de la paroi interne de manière à autoriser le passage du fluide radialement à travers la première portion axiale. Selon un mode de réalisation, le dispositif comprend en outre un organe de roulement situé radialement entre la paroi interne du carter de protection et l’élément d’entrée de couple. Avantageusement, l’organe de roulement supporte l’élément d’entrée de couple et est composé d’une bague interne en contact avec l’élément d’entré de couple notamment la partie avant de l’élément d’entrée de couple et d’une bague externe en contact avec le carter de protection, notamment avec la paroi interne du carter de protection. According to one embodiment, at least one bore passes radially through the first axial portion, said portion being located radially outside the internal wall so as to allow the passage of the fluid radially through the first axial portion. According to one embodiment, the device further comprises a rolling member located radially between the internal wall of the protective casing and the torque input element. Advantageously, the rolling member supports the torque input element and is composed of an internal ring in contact with the torque input element, in particular the front part of the torque input element and d '' an outer ring in contact with the protective casing, in particular with the internal wall of the protective casing.
Selon un mode de réalisation, le dispositif comprend en outre un premier embrayage de sortie en rotation autour de l’axe X, accouplant sélectivement et par friction un deuxième élément d’entrée de couple apte à être couplé audit premier élément de sortie de couple et un deuxième élément de sortie de couple apte à être couplé en rotation à un premier arbre d’entré d’une boite de vitesses. According to one embodiment, the device further comprises a first output clutch rotating around the axis X, selectively and frictionally coupling a second torque input element capable of being coupled to said first torque output element and a second torque output element capable of being coupled in rotation to a first input shaft of a gearbox.
Selon un mode de réalisation, le dispositif comprend en outre un deuxième embrayage de sortie en rotation autour de l’axe X, accouplant sélectivement et par friction ledit deuxième élément d’entrée de couple et un troisième élément de sortie de couple apte à être couplé en rotation à un deuxième arbre d’entré d’une boite de vitesses, le premier et deuxième embrayage de sortie étant empilés radialement. According to one embodiment, the device further comprises a second output clutch rotating around the axis X, selectively and frictionally coupling said second torque input element and a third torque output element capable of being coupled in rotation to a second input shaft of a gearbox, the first and second output clutch being stacked radially.
Au sens de la présente demande, le premier embrayage de sortie est celui situé radialement à l’extérieur, c'est-à-dire le plus loin de l’axe de rotation X du dispositif. Le deuxième embrayage de sortie étant celui situé radialement à l’intérieur, c'est-à-dire le plus proche de l’axe de rotation du dispositif. Within the meaning of the present application, the first output clutch is that located radially on the outside, that is to say the furthest from the axis of rotation X of the device. The second output clutch is the one located radially inside, that is to say the one closest to the axis of rotation of the device.
Avantageusement, le deuxième élément d’entrée de couple correspond au porte- disque d’entrée d’un mécanisme à double embrayage comprenant le premier et deuxième embrayage de sortie. Advantageously, the second torque input element corresponds to the input disc holder of a double clutch mechanism comprising the first and second output clutch.
Selon un aspect de l’invention, le piston de chaque organe d’actionnement de l’embrayage peut être contrôlé par un capteur interne de position venant contrôler l’embrayage ou par mesure de la pression hydraulique lors de la fermeture de l’embrayage ou par mesure du volume de fluide injecté ou par mesure d’une grandeur de déplacement dans le moteur électrique ou par mesure d’une grandeur d’effort ou par une mesure de courant consommé dans le moteur électrique. According to one aspect of the invention, the piston of each clutch actuating member can be controlled by an internal position sensor which controls the clutch or by measuring the hydraulic pressure when the clutch is closed or by measuring the volume of fluid injected or by measuring a displacement quantity in the electric motor or by measuring a force quantity or by measuring the current consumed in the electric motor.
Selon un mode de réalisation, le deuxième élément d’entrée de couple comprend une zone de connexion électrique apte à être lié en rotation avec une machine électrique tournante autour d’un axe parallèle à l’axe de rotation X. Selon un aspect de l’invention, la zone de connexion électrique est décalée axialement de l’embrayage d’entrée et/ou des embrayages de sortie. La machine électrique est alors dite « off-line ». According to one embodiment, the second torque input element comprises an electrical connection zone capable of being linked in rotation with an electric machine rotating about an axis parallel to the axis of rotation X. According to one aspect of the invention, the electrical connection zone is axially offset from the input clutch and / or the output clutches. The electric machine is then called "off-line".
La zone de connexion électrique peut être soudée, rivetée ou venir d’un seul tenant avec le deuxième élément d’entrée de couple. The electrical connection area can be welded, riveted or come in one piece with the second torque input element.
Cette disposition permet de positionner la machine électrique en fonction de l’espace disponible dans la chaîne de traction du véhicule. Cette disposition permet notamment de ne pas avoir à disposer la machine électrique axialement à la suite des embrayages, ce qui serait négatif pour la compacité axiale. Cette disposition permet notamment de ne pas avoir à disposer la machine électrique radialement au-delà des embrayages, ce qui serait négatif pour la compacité radiale. This arrangement makes it possible to position the electric machine as a function of the space available in the vehicle's traction chain. This arrangement makes it possible in particular not to have to place the electric machine axially following the clutches, which would be negative for the axial compactness. This arrangement makes it possible in particular not to have to place the electric machine radially beyond the clutches, which would be negative for the radial compactness.
Selon un aspect additionnel de l’invention, la zone de connexion électrique du deuxième élément d’entrée de couple comprend une couronne apte à être engrenée directement par un pignon de la machine électrique tournante. According to an additional aspect of the invention, the electrical connection zone of the second torque input element comprises a crown capable of being meshed directly by a pinion of the rotary electric machine.
Selon une autre caractéristique de l’invention, la couronne présente une denture hélicoïdale de forme complémentaire au pignon de la machine électrique tournante. According to another characteristic of the invention, the crown has a helical toothing of complementary shape to the pinion of the rotary electric machine.
De manière alternative, une chaîne ou une courroie peut être utilisée pour relier la machine électrique tournante à la zone de connexion électrique. Alternatively, a chain or belt can be used to connect the rotating electrical machine to the electrical connection area.
En variante, on peut prévoir que le deuxième élément d’entrée de couple définit un support de rotor d’une machine électrique en rotation autour de l’axe de rotation. La machine électrique est alors « in-line ». As a variant, it is possible to provide for the second torque input element to define a rotor support for an electric machine rotating around the axis of rotation. The electric machine is then "in-line".
Selon l’invention, les embrayages, à savoir l’embrayage d’entrée et le premier et deuxième embrayage de sortie peuvent être de type multidisque. Dans le cadre de l’invention, un ensemble multidisque est un ensemble comprenant au moins un disque de friction solidaire en rotation de l’un des porte-disque d’entrée et de sortie, au moins deux plateaux respectivement disposés de part et d’autre de chaque disque de friction, solidaires en rotation de l’autre des porte-disque d’entrée et de sortie et des garnitures de friction disposées entre les plateaux et un disque de friction, les embrayages décrivant une position débrayée et une position embrayée dans laquelle lesdits plateaux et le disque de friction pincent les garnitures de friction de manière à transmettre un couple entre un porte-disque d’entrée et un porte- disque de sortie. According to the invention, the clutches, namely the input clutch and the first and second output clutch, can be of the multi-disc type. In the context of the invention, a multidisk assembly is an assembly comprising at least one friction disc integral in rotation with one of the input and output disc carriers, at least two plates respectively arranged on the side and other of each friction disc, integral in rotation with the other of the inlet and outlet disc holders and friction linings arranged between the plates and a friction disc, the clutches describing a disengaged position and a engaged position in which said plates and the friction disc pinch the friction linings so as to transmit a torque between an input disc holder and an output disc holder.
De préférence, l’embrayage comporte entre deux et sept disques de friction, de préférence quatre disques de friction. Selon une caractéristique de l’invention, les embrayages d’entrée et de sortie sont humides. Les embrayages étant contenus dans au moins une chambre étanche remplie d’un fluide, notamment de l’huile. Au sens de la présente demande, un embrayage humide est un embrayage qui est adapté pour fonctionner dans un bain d’huile. Preferably, the clutch comprises between two and seven friction discs, preferably four friction discs. According to a characteristic of the invention, the input and output clutches are wet. The clutches being contained in at least one sealed chamber filled with a fluid, in particular oil. For the purposes of the present application, a wet clutch is a clutch which is suitable for operating in an oil bath.
Selon un mode de réalisation, la zone de connexion électrique, le premier embrayage de sortie et le deuxième embrayage de sortie sont empilés radialement en rapprochement de l’axe X. According to one embodiment, the electrical connection zone, the first output clutch and the second output clutch are stacked radially in proximity to the axis X.
L’invention sera mieux comprise, et d'autres buts, détails, caractéristiques et avantages de celle-ci apparaîtront plus clairement au cours de la description suivante d’un mode de réalisation particulier de l’invention, donné uniquement à titre illustratif et non limitatif, en référence à la figure annexée. The invention will be better understood, and other objects, details, characteristics and advantages thereof will appear more clearly during the following description of a particular embodiment of the invention, given solely by way of illustration and not limiting, with reference to the appended figure.
[Figure 1] représente une vue en coupe axiale d’un du dispositif de transmission de couple selon un mode de réalisation de l’invention. [Figure 1] shows an axial sectional view of one of the torque transmission device according to an embodiment of the invention.
En relation avec la figure 1 , on observe un dispositif de transmission de couple 1 comprenant : In relation to FIG. 1, there is a torque transmission device 1 comprising:
- un premier élément d’entrée de couple 2 en rotation autour d’un axe X, apte à être couplé en rotation à un vilebrequin d’un moteur thermique (non représenté), - a first torque input element 2 rotating around an axis X, capable of being coupled in rotation to a crankshaft of a heat engine (not shown),
- un premier élément de sortie de couple 4, - a first torque output element 4,
- un deuxième élément de sortie de couple 6, apte à être couplé en rotation à un premier arbre d’entrée d’une boîte de vitesses 6a, - a second torque output element 6, capable of being coupled in rotation to a first input shaft of a gearbox 6a,
- un troisième élément de sortie de couple 7, apte à être couplé en rotation à un deuxième arbre d’entrée d’une boîte de vitesses 7a et - a third torque output element 7, capable of being coupled in rotation to a second input shaft of a gearbox 7a and
- un deuxième élément d’entrée de couple 5, apte à être couplé en rotation au premier élément de sortie de couple 4 et agencé entre l’élément d’entrée de couple 2 et les deuxième et troisième éléments de sortie de couple 6, 7 au sens de la présente invention. - A second torque input element 5, adapted to be coupled in rotation to the first torque output element 4 and arranged between the torque input element 2 and the second and third torque output elements 6, 7 within the meaning of the present invention.
Dans l’exemple considéré, le troisième élément de sortie 7 est disposé en parallèle du deuxième élément de sortie 6 au sens de la transmission de couple. Chacun de ces éléments tourne autour d’un axe de rotation X du dispositif. In the example considered, the third output element 7 is arranged in parallel with the second output element 6 in the direction of the torque transmission. Each of these elements rotates around an axis of rotation X of the device.
Le deuxième et troisième élément de sortie 6, 7 comprennent des interfaces de sortie dont la périphérie interne est cannelée et apte à coopérer, respectivement avec un premier et un deuxième arbre de boite de vitesses. The second and third output elements 6, 7 comprise output interfaces whose internal periphery is grooved and able to cooperate, respectively with a first and a second gearbox shaft.
Un dispositif d’amortisseur de torsion (non représenté) peut être positionné entre le vilebrequin du moteur thermique et l’élément d’entrée de couple 2. Dans l’exemple considéré, le dispositif comprend en outre un embrayage d’entrée 10 accouplant sélectivement et par friction l’élément d’entré de couple 2 et le premier élément de sortie de couple 4 au sens de la transmission de couple. Ainsi, l’embrayage d’entrée 10 comprend : A torsion damper device (not shown) can be positioned between the crankshaft of the heat engine and the torque input element 2. In the example considered, the device also comprises an input clutch 10 which selectively and frictionally couples the torque input element 2 and the first torque output element 4 in the direction of the torque transmission. Thus, the input clutch 10 comprises:
- un porte-disque d’entrée 11 solidaire en rotation du premier élément d’entrée de couple 2 par l’intermédiaire d’un voile d’entrée 15, - an input disc holder 11 integral in rotation with the first torque input element 2 by means of an input web 15,
- un porte-disque de sortie 12 solidaire en rotation du premier élément de sortie 4, et an output disc holder 12 integral in rotation with the first output element 4, and
- un ensemble multidisque 13 comprenant plusieurs disques de friction, ici trois, solidaires en rotation du porte-disque de sortie 12, plusieurs plateaux respectivement disposés de part et d’autre de chaque disque de friction, solidaires en rotation du porte-disque d’entrée 11 et des garnitures de friction disposées entre les plateaux et un disque de friction, fixées de chaque côté des disques de friction, l’embrayage 10 décrivant une position débrayée et une position embrayée dans laquelle lesdits plateaux et le disque de friction pincent les garnitures de friction de manière à transmettre un couple entre le porte-disque d’entrée et le porte-disque de sortie. - A multi-disc assembly 13 comprising several friction discs, here three, integral in rotation with the outlet disc holder 12, several plates respectively arranged on either side of each friction disc, integral in rotation with the disc holder inlet 11 and friction linings arranged between the plates and a friction disc, fixed on each side of the friction discs, the clutch 10 describing a disengaged position and a engaged position in which said plates and the friction disc pinch the linings friction so as to transmit a torque between the input disc holder and the output disc holder.
Chaque porte-disque 1 1 , 12 synchronise en rotation l’ensemble des plateaux et l’ensemble des disques de friction. Chaque portes-disque 11 , 12 comporte une jupe cylindrique sur lesquelles sont montées les plateaux et les disques de friction. Each disc holder 1 1, 12 synchronizes in rotation all of the plates and all of the friction discs. Each disc holder 11, 12 has a cylindrical skirt on which the plates and the friction discs are mounted.
Les disques de friction de l’ensemble multidisque 13 coopèrent avec la jupe cylindrique du porte-disque de sortie 12 selon leur périphérie radialement intérieure par cannelures. Les disques de friction sont donc radialement à l’extérieur de la jupe cylindrique. The friction discs of the multidisc assembly 13 cooperate with the cylindrical skirt of the outlet disc holder 12 along their radially inner periphery by splines. The friction discs are therefore radially outside the cylindrical skirt.
Les plateaux de l’ensemble multidisque 13 coopèrent avec la jupe cylindrique du porte-disque de d’entrée 1 1 selon leur périphérie radialement extérieure par cannelures. Les plateaux sont donc radialement à l’intérieur de la jupe cylindrique. The plates of the multidisc assembly 13 cooperate with the cylindrical skirt of the input disc carrier 1 1 along their radially outer periphery by splines. The plates are therefore radially inside the cylindrical skirt.
L’élément d’entrée de couple 2 permet l’agencement d’un système d’actionnement 20 associé à l’embrayage d’entrée 10. The torque input element 2 allows the arrangement of an actuation system 20 associated with the input clutch 10.
Dans l’exemple considéré, le dispositif 1 comprend également un premier embrayage de sortie E1 accouplant sélectivement et par friction le deuxième élément d’entrée de couple 5 et le deuxième élément de sortie de couple 6. Ainsi, le premier embrayage de sortie E1 comprend : In the example considered, the device 1 also comprises a first output clutch E1 selectively and frictionally coupling the second torque input element 5 and the second torque output element 6. Thus, the first output clutch E1 comprises :
- un porte-disque d’entrée 121 , solidaire en rotation du premier élément de sortie 4 et en conséquence du premier élément d’entrée de couple 2, - an input disc holder 121, integral in rotation with the first output element 4 and consequently with the first torque input element 2,
- un porte-disque de sortie 122 solidaire en rotation du deuxième élément de sortie 6 et, - un ensemble multidisque 123 comprenant plusieurs disques de friction, ici quatre, solidaires en rotation du porte-disque de sortie 122, plusieurs plateaux respectivement disposés de part et d’autre de chaque disque de friction, solidaires en rotation du porte-disque d’entrée 121 et des garnitures de friction disposées entre les plateaux et un disque de friction, fixées de chaque côté des disques de friction, l’embrayage E1 décrivant une position débrayée et une position embrayée dans laquelle lesdits plateaux et le disque de friction pincent les garnitures de friction de manière à transmettre un couple entre le porte-disque d’entrée et le porte-disque de sortie. an output disc holder 122 integral in rotation with the second output element 6 and, - A multi-disc assembly 123 comprising several friction discs, here four, integral in rotation with the outlet disc holder 122, several plates respectively arranged on either side of each friction disc, integral in rotation with the disc holder inlet 121 and friction linings arranged between the plates and a friction disc, fixed on each side of the friction discs, the clutch E1 describing a disengaged position and a engaged position in which said plates and the friction disc pinch the linings friction so as to transmit a torque between the input disc holder and the output disc holder.
Dans l’exemple considéré, le dispositif 1 comprend en outre un deuxième embrayage de sortie E2, accouplant sélectivement et par friction le deuxième élément d’entrée de couple 5 et le troisième élément de sortie de couple 7. Ainsi, le premier embrayage de sortie E2 comprend : In the example considered, the device 1 also comprises a second output clutch E2, selectively and frictionally coupling the second torque input element 5 and the third torque output element 7. Thus, the first output clutch E2 includes:
- un porte-disque d’entrée 131 solidaire en rotation du premier élément de sortie 4 et en conséquence du premier élément d’entrée de couple 2, - an input disc holder 131 integral in rotation with the first output element 4 and consequently with the first torque input element 2,
- un porte-disque de sortie 132 solidaire en rotation du troisième élément de sortie 7 et, an output disc holder 132 integral in rotation with the third output element 7 and,
- un ensemble multidisque 133 comprenant plusieurs disques de friction, ici cinq. - A multi-disc assembly 133 comprising several friction discs, here five.
L’ensemble multidisque 133 présente les mêmes caractéristiques techniques que l’ensemble multidisque de l’embrayage E1. The 133 multi-disc assembly has the same technical characteristics as the E1 clutch multi-disc assembly.
De manière commune aux trois embrayages 10, E1 et E2, les garnitures peuvent être fixées sur les disques de friction, notamment par collage, notamment par rivetage, notamment par surmoulage. En variante, les garnitures sont fixées sur les plateaux. Commonly to the three clutches 10, E1 and E2, the linings can be fixed to the friction discs, in particular by gluing, in particular by riveting, in particular by overmolding. As a variant, the linings are fixed to the plates.
Chaque porte-disque 11 , 12, 121 , 122, 131 , 132 peut synchroniser en rotation l’ensemble des plateaux ou l’ensemble des disques de friction. Each disc holder 11, 12, 121, 122, 131, 132 can synchronize in rotation all of the plates or all of the friction discs.
Selon un aspect de l’invention, les plateaux peuvent être solidaires en rotation du porte-disque d’entrée 1 1 , 121 , 131 et les disques de friction peuvent être solidaires du porte- disque de sortie 12, 122, 132. En variante, les plateaux peuvent être solidaires en rotation du porte-disque de sortie 12, 122, 132. Les disques peuvent être solidaires en rotation du porte- disque d’entrée 1 1 , 21 , 31. According to one aspect of the invention, the plates can be secured in rotation to the input disc holder 1 1, 121, 131 and the friction discs can be secured to the outlet disc holder 12, 122, 132. As a variant , the plates can be integral in rotation with the output disc holder 12, 122, 132. The discs can be secured in rotation with the input disc holder 1 1, 21, 31.
Les embrayages sont de type humide et comportent entre deux et sept disques de friction, de préférence quatre disques de friction. De tels embrayages multi-disques permettent de limiter la hauteur radiale de limiter l’étendue axiale. Les embrayages de sortie E1 , E2 peuvent être agencés pour ne pas être simultanément dans la même configuration embrayée. En revanche, ils peuvent simultanément être configurés dans leur position débrayée. The clutches are wet type and have between two and seven friction discs, preferably four friction discs. Such multi-disc clutches make it possible to limit the radial height and limit the axial extent. The output clutches E1, E2 can be arranged so as not to be simultaneously in the same clutch configuration. However, they can simultaneously be configured in their disengaged position.
Le dispositif 1 comprend en outre un carter de protection 27 agencé pour envelopper au moins partiellement l’élément d’entrée de couple 2, l’élément de sortie de couple 4 l’embrayage d’entrée 10 et le système d’actionnement 20. The device 1 further comprises a protective casing 27 arranged to at least partially envelop the torque input element 2, the torque output element 4 the input clutch 10 and the actuation system 20.
Le carter 27 est composé d’une paroi radiale 26 et d’une paroi interne 28 s’étendant axialement autour de l’axe X et présente une forme générale sensiblement en « L », la base du « L » étant située du côté de l’axe de rotation X. Le carter comprend un réseau de passage d’un fluide 80 agencé pour alimenter en fluide ledit système d’actionnement 20. Ainsi, le réseau de passage de fluide 80 comporte une première portion axiale 81 située dans la paroi interne et une conduite amont 82 d’orientation radiale située dans la paroi radiale 26 du carter de protection reliée à la première portion 81. The casing 27 is composed of a radial wall 26 and an internal wall 28 extending axially around the axis X and has a general shape substantially in "L" shape, the base of the "L" being located on the side of the axis of rotation X. The casing comprises a network for the passage of a fluid 80 arranged to supply fluid to said actuation system 20. Thus, the network for the passage of fluid 80 comprises a first axial portion 81 situated in the wall internal and an upstream pipe 82 of radial orientation situated in the radial wall 26 of the protective casing connected to the first portion 81.
La conduite amont 82 est ménagée dans une portion supérieure du carter, destinée à être disposée au-dessus de l’axe X. La conduite amont 82 permet ainsi de conduire le fluide par gravité ou au moyen d’un appareil assurant l’écoulement du fluide, tel qu'une pompe ou un actionneur, vers la première portion 81. The upstream pipe 82 is formed in an upper portion of the casing, intended to be disposed above the X axis. The upstream pipe 82 thus makes it possible to conduct the fluid by gravity or by means of a device ensuring the flow of the fluid, such as a pump or an actuator, to the first portion 81.
L’élément d’entrée de couple 2 est constitué d’une partie arrière 2a et d’une partie avant 2b. Dans le cadre de la présente invention, la partie arrière 2a de l’élément d’entrée de couple 2 est ménagé radialement à l’extérieur et à l’intérieur de ladite paroi interne 28. En d’autres termes, la paroi interne 28 est entourée radialement de part et d’autre par la partie arrière 2a. Cette architecture permet de diminuer la dimension axiale du dispositif 1. The torque input element 2 consists of a rear part 2a and a front part 2b. In the context of the present invention, the rear part 2a of the torque input element 2 is formed radially outside and inside said internal wall 28. In other words, the internal wall 28 is surrounded radially on both sides by the rear part 2a. This architecture makes it possible to reduce the axial dimension of the device 1.
La partie arrière 2a de l’élément d’entrée de couple 2 est composée d’une première et deuxième portion axiale 2ai , 2a3 ainsi que d’une paroi radiale 2a2 reliant la première portion axiale à la deuxième portion axiale. The rear part 2a of the torque input element 2 is composed of a first and second axial portion 2ai, 2a3 as well as a radial wall 2a2 connecting the first axial portion to the second axial portion.
Dans l’exemple considéré, l’embrayage d’entrée 10, la première portion axiale 2ai , la paroi interne 28 du carter de protection 27, et la deuxième portion axiale 2a3 se succèdent radialement en rapprochement de l’axe X. Ainsi c’est la première portion axiale 2ai qui est ménagée radialement à l’extérieur de la paroi interne 28 et c’est la deuxième portion axiale 2a3 qui est ménagée radialement à l’intérieur de la paroi interne 28. In the example considered, the input clutch 10, the first axial portion 2ai, the internal wall 28 of the protective casing 27, and the second axial portion 2a 3 succeed one another radially in proximity to the axis X. Thus c 'is the first axial portion 2ai which is formed radially outside the internal wall 28 and it is the second axial portion 2a3 which is formed radially inside the internal wall 28.
L’étanchéité du carter 27 est assuré au moyen d’une série de joints d’étanchéité. Plus particulièrement, un joint d’étanchéité 29 est disposé radialement entre la paroi interne 28 et la deuxième portion axiale 2a3. Selon un autre mode de réalisation, le joint 29 peut être intégré au roulement 90 ou se situer en avant du roulement. Les joints d’étanchéités utilisés dans le cadre de la présente invention peuvent être des joints d’étanchéité dynamiques à lèvres. The casing 27 is sealed by means of a series of seals. More particularly, a seal 29 is arranged radially between the internal wall 28 and the second axial portion 2a 3 . According to another embodiment, the seal 29 can be integrated at bearing 90 or be located in front of the bearing. The seals used in the context of the present invention can be dynamic lip seals.
Avantageusement, le carter 27 peut-être fixé au moteur à combustion interne ou au moteur de la machine électrique par l’intermédiaire de moyens de fixation, par exemple de type vis ou rivet visibles. Advantageously, the casing 27 can be fixed to the internal combustion engine or to the engine of the electric machine by means of fixing means, for example of the visible screw or rivet type.
Par ailleurs, la partie arrière 2a de l’élément d’entrée de couple 2 comporte au moins un perçage traversant qui autorise le passage du fluide de refroidissement et/ou de lubrification au travers de ladite paroi arrière 2a. En particulier, la partie arrière 2a comporte au moins deux perçages 83 traversant radialement la première portion axiale 2ai , ladite portion étant située radialement à l’extérieur de la paroi interne 28 de manière à autoriser le passage du fluide radialement à travers la première portion axiale 2ai . En particulier, les perçages traversant 83 permettent d’amener le fluide dans le système d’actionnement 20. Furthermore, the rear part 2a of the torque input element 2 comprises at least one through hole which allows the passage of the cooling and / or lubrication fluid through said rear wall 2a. In particular, the rear part 2a comprises at least two bores 83 passing radially through the first axial portion 2ai, said portion being located radially outside the internal wall 28 so as to allow the passage of the fluid radially through the first axial portion 2ai. In particular, the through holes 83 allow the fluid to be brought into the actuation system 20.
Le dispositif comprend en outre, un moyeu principal 50 d’axe de rotation X. Le deuxième élément d’entrée de couple 5 (également appelée porte-disque d’entrée commun 5 aux embrayages de sortie E1 et E2) est solidairement fixement par soudure au moyeu principal 50. The device further comprises a main hub 50 of axis of rotation X. The second torque input element 5 (also called input disk holder 5 common to the output clutches E1 and E2) is fixedly fixed by welding to main hub 50.
Ainsi, le moyeu principal 50 supporte le premier et deuxième embrayage de sortie E1 , E2 par l’intermédiaire du porte-disque d’entrée commun 5. Le moyeu principal 50 est donc couplé en rotation à l’élément d’entrée de couple 2. Lorsque l’élément d’entrée de couple 2 est couplé à un arbre moteur entraîné en rotation par le vilebrequin d’un moteur, tel que décrit précédemment, et que l’embrayage 10 est fermé, alors le moyeu principal 50 est animé d’un mouvement de rotation analogue à celui de l’arbre moteur. Thus, the main hub 50 supports the first and second output clutch E1, E2 via the common input disc carrier 5. The main hub 50 is therefore coupled in rotation to the torque input element 2 When the torque input element 2 is coupled to an engine shaft driven in rotation by the crankshaft of an engine, as described above, and the clutch 10 is closed, then the main hub 50 is driven by 'a rotation movement similar to that of the motor shaft.
Comme illustré sur la figure 1 , le premier embrayage de sortie E1 est disposé radialement au-dessus du deuxième embrayage de sortie E2. As illustrated in FIG. 1, the first output clutch E1 is arranged radially above the second output clutch E2.
De préférence, l’embrayage d’entrée 10, le premier embrayage E1 et le deuxième embrayage E2 (ci-après « les embrayages ») sont à l’état ouvert, encore dit « normalement ouvert », et sont actionnés sélectivement en fonctionnement par un dispositif de commande (non représenté) pour passer de l’état ouvert à l’état fermé. Preferably, the input clutch 10, the first clutch E1 and the second clutch E2 (hereinafter "the clutches") are in the open state, also called "normally open", and are selectively actuated in operation by a control device (not shown) for passing from the open state to the closed state.
Les embrayages sont chacun commandés par un système d’actionnement 20, 30, 40 qui seront décrits ultérieurement. Chaque système d’actionnement 20, 30, 40 est agencé pour pouvoir configurer les embrayages dans une configuration quelconque comprise entre la configuration embrayée et la configuration débrayée. The clutches are each controlled by an actuation system 20, 30, 40 which will be described later. Each actuation system 20, 30, 40 is arranged to be able to configure the clutches in any configuration between the clutch configuration and the disengaged configuration.
Pour commander sélectivement le changement d’état des embrayages, le dispositif de commande gère l’alimentation en huile. Le dispositif de commande est raccordé au carter de protection 27 qui comprend le réseau de passage de fluide 80 ainsi qu’au moyeu principal 50 qui comporte des canaux non visibles sur les plans de coupe de la figure 1. To selectively control the change of state of the clutches, the control device manages the oil supply. The control device is connected to the housing of protection 27 which includes the fluid passage network 80 as well as to the main hub 50 which comprises channels not visible on the section planes of FIG. 1.
Chaque système d’actionnement 20, 30, 40 comprend : Each actuation system 20, 30, 40 includes:
- une chambre de pression 21 , 31 , 41 agencée pour recevoir un fluide pressurisé, a pressure chamber 21, 31, 41 arranged to receive a pressurized fluid,
- un piston 22, 32, 42 mobile axialement à l’intérieur de la chambre de pression 21 ,- a piston 22, 32, 42 movable axially inside the pressure chamber 21,
31 , 41 , 31, 41,
- une chambre d’équilibrage 23, 33, 43 située à l’opposé de la chambre de pression - a balancing chamber 23, 33, 43 located opposite the pressure chamber
21 , 31 , 41 par rapport au piston 22, 32, 42. 21, 31, 41 relative to the piston 22, 32, 42.
Chaque système d’actionnement 20, 30, 40 comprend en outre un élément de rappel élastique 24, 34, 44, agencé pour générer un effort axial s’opposant au déplacement du piston Each actuation system 20, 30, 40 further comprises an elastic return element 24, 34, 44, arranged to generate an axial force opposing the movement of the piston
22, 32, 42 correspondant pour embrayer l’embrayage 10, E1 , E2 correspondant. Ceci permet de rappeler automatiquement le piston 22, 32, 42 en position débrayée, correspondant à un état ouvert de l’embrayage. Dans cette position, le piston 22, 32, 42 libère axialement l’ensemble multidisque correspondant qui ne transmet alors plus de couple en direction du premier élément de sortie de couple 4, du premier arbre d’entrée 6a d’une boite de vitesse ou du deuxième arbre d’entrée 7a d’une boite de vitesses. 22, 32, 42 corresponding to engage the clutch 10, E1, E2 corresponding. This automatically recalls the piston 22, 32, 42 in the disengaged position, corresponding to an open state of the clutch. In this position, the piston 22, 32, 42 axially releases the corresponding multidisk assembly which then no longer transmits torque in the direction of the first torque output element 4, of the first input shaft 6a of a gearbox or of the second input shaft 7a of a gearbox.
D’une manière générale, le piston 22 est agencé pour transmettre un premier effort axial, exercé parallèlement à l’axe longitudinal X, à l’embrayage d’entrée 10 par l’intermédiaire d’une partie supérieure collaborant avec les éléments de friction (flasques 13 et disques de friction 14) dudit embrayage d’entrée 10, et d’une partie inférieure collaborant avec un générateur d’effort pour configurer l’embrayage d’entrée 10 dans l’une des configurations détaillées précédemment. Au niveau de sa partie supérieure, le piston 22 comprend des appuis extérieurs 61 qui s’étendent axialement vers l’avant AV pour pouvoir presser la flasque 13 d’extrémité de l’ensemble multidisque 12 de l’embrayage d’entrée 10 contre un disque de friction 14 d’une part, et contre un moyen de réaction extérieur formé directement dans le premier élément de sortie de couple 4 d’autre part. Dans l’exemple représenté sur la figure 1 , les appuis 61 sont discontinus. In general, the piston 22 is arranged to transmit a first axial force, exerted parallel to the longitudinal axis X, to the input clutch 10 via an upper part collaborating with the friction elements (flanges 13 and friction discs 14) of said input clutch 10, and of a lower part collaborating with a force generator to configure the input clutch 10 in one of the configurations detailed above. At its upper part, the piston 22 includes external supports 61 which extend axially towards the front AV in order to be able to press the end flange 13 of the multidisk assembly 12 of the input clutch 10 against a friction disc 14 on the one hand, and against an external reaction means formed directly in the first torque output element 4 on the other hand. In the example shown in Figure 1, the supports 61 are discontinuous.
Le piston 22 est mobile axialement, ici de l’arrière vers l’avant entre une position débrayée et une position embrayée qui correspondent respectivement aux états ouvert et fermé de l’embrayage d’entrée 10. Le piston 22 de l’embrayage d’entrée 10 est disposé axialement entre la chambre de pression 21 , située axialement à l’arrière et la chambre d’équilibrage 23 située axialement à l’avant. The piston 22 is axially movable, here from rear to front between a disengaged position and a engaged position which correspond respectively to the open and closed states of the input clutch 10. The piston 22 of the clutch inlet 10 is disposed axially between the pressure chamber 21, located axially at the rear and the balancing chamber 23 located axially at the front.
Le piston 22 prend la forme d’une tôle ondulée et est incurvée axialement vers l’avant AV à son extrémité radiale extérieure. Les appuis 61 extérieurs s’étendent parallèlement à l’axe longitudinal X vers l’avant AV et au travers d’ouvertures aménagées à travers le voile d’entrée 15. The piston 22 takes the form of a corrugated sheet and is curved axially forwards AV at its outer radial end. The external supports 61 extend parallel to the longitudinal axis X towards the front AV and through openings arranged through the entry web 15.
À titre d’exemple non limitatif, le piston 22 peut être obtenu par emboutissage. By way of nonlimiting example, the piston 22 can be obtained by stamping.
La chambre de pression 21 du système d’actionnement 20 de l’embrayage d’entrée 10 est agencée pour recevoir un certain volume de fluide hydraulique sous pression afin de générer un effort axial sur la partie inférieure du piston 22 et de configurer ainsi l’embrayage d’entrée 10 dans l’une des configurations décrites précédemment. Le fluide hydraulique pressurisé est avantageusement acheminé par l’intermédiaire du réseau de passage de fluide 80 (conduites 81 et 82 telles représentées sur le plan de coupe) puis par au moins un perçage traversant au moins en partie l’élément d’entrée de couple 2, en particulier la première portion axiale 2ai , et débouchant radialement dans la chambre de pression 21 au niveau d’une face extérieure de ladite portion axiale 2ai . The pressure chamber 21 of the actuation system 20 of the input clutch 10 is arranged to receive a certain volume of hydraulic fluid under pressure in order to generate an axial force on the lower part of the piston 22 and thus to configure the input clutch 10 in one of the configurations described above. The pressurized hydraulic fluid is advantageously routed via the fluid passage network 80 (pipes 81 and 82 as shown on the cutting plane) then by at least one bore passing at least in part through the torque input element. 2, in particular the first axial portion 2ai, and opening radially into the pressure chamber 21 at an external face of said axial portion 2ai.
La chambre de pression 21 qui génère l’effort du piston 22 de l’embrayage d’entrée 10 est associée à une chambre d’équilibrage 23 agencée pour recevoir un certain volume de fluide hydraulique. Le fluide, du type de lubrification ou de refroidissement est avantageusement acheminé par l’intermédiaire de conduits de circulation fluidiques basse pression (non représentées sur le plan de coupe) puis par au moins un perçage traversant au moins en partie l’élément d’entrée de couple 2, en particulier la première portion axiale 2ai , et débouchant radialement dans la chambre d’équilibrage 23 au niveau d’une face extérieure de ladite portion axiale 2ai . The pressure chamber 21 which generates the force of the piston 22 of the input clutch 10 is associated with a balancing chamber 23 arranged to receive a certain volume of hydraulic fluid. The fluid, of the lubrication or cooling type, is advantageously conveyed by means of low pressure fluidic circulation conduits (not shown on the cutting plane) then by at least one bore passing at least partially through the inlet element. of torque 2, in particular the first axial portion 2ai, and opening radially into the balancing chamber 23 at an external face of said axial portion 2ai.
On notera que l’étanchéité de la chambre de pression 21 et de la chambre d’équilibrage 23 du système d’actionnement 20 est garantie par la présence de joints d’étanchéité. It will be noted that the sealing of the pressure chamber 21 and of the balancing chamber 23 of the actuation system 20 is guaranteed by the presence of seals.
Le trou A assure une fuite de la chambre d’équilibrage 23. Cette fuite permet la lubrification de l’embrayage 10 par l’intermédiaire de trous radiaux disposés sur l’élément de sortie de couple (4) (non représentés). The hole A leaks from the balancing chamber 23. This leak allows the lubrication of the clutch 10 by means of radial holes arranged on the torque output element (4) (not shown).
L’élément de rappel élastique 24 du système d’actionnement 20 de l’embrayage d’entrée 10 est situé radialement à l’extérieur de la chambre d’équilibrage 23. En particulier, l’élément de rappel élastique 34 est disposé axialement entre le voile d’entrée 15 et le piston 22 du système d’actionnement 10 de l’embrayage d’entrée. The elastic return element 24 of the actuating system 20 of the input clutch 10 is located radially outside the balancing chamber 23. In particular, the elastic return element 34 is disposed axially between the input web 15 and the piston 22 of the actuating system 10 of the input clutch.
Le piston 22 présente une extrémité radiale extérieure recourbée définissant une surface d’appui pour exercer l’effort axial sur l’ensemble multidisque, continue ou discontinue dans l’exemple considéré. De manière analogue au fonctionnement du piston 22 de l’embrayage d’entrée 10, le piston 32 est agencé pour transmettre un effort axial, exercé parallèlement à l’axe longitudinal X, au premier embrayage E1 par l’intermédiaire d’une première partie supérieure collaborant avec les éléments de friction dudit premier embrayage E1 , et de sa deuxième partie inférieure collaborant avec un générateur d’effort pour configurer le premier embrayage E1 dans l’une des configurations détaillées précédemment. Au niveau de sa première partie, le piston 32 comprend des appuis extérieurs qui s’étendent axialement vers l’avant AV pour pouvoir presser la flasque d’extrémité de l’ensemble multidisque du premier embrayage E1 contre un disque de friction d’une part, et contre un moyen de réaction extérieur formé directement dans le premier élément de sortie de couple 3 d’autre part. Dans l’exemple représenté sur la figure 1 les appuis sont discontinus. The piston 22 has a curved outer radial end defining a bearing surface for exerting the axial force on the multidisc assembly, continuous or discontinuous in the example considered. Similarly to the operation of the piston 22 of the input clutch 10, the piston 32 is arranged to transmit an axial force, exerted parallel to the longitudinal axis X, to the first clutch E1 via a first part upper collaborating with the friction elements of said first clutch E1, and its second lower part collaborating with a force generator to configure the first clutch E1 in one of the configurations detailed above. At its first part, the piston 32 includes external supports which extend axially towards the front AV in order to be able to press the end flange of the multidisk assembly of the first clutch E1 against a friction disc on the one hand , and against an external reaction means formed directly in the first torque output element 3 on the other hand. In the example shown in Figure 1 the supports are discontinuous.
Le piston 32 est mobile axialement, ici de l’arrière vers l’avant entre une position débrayée et une position embrayée qui correspondent respectivement aux états ouvert et fermé du premier embrayage E1. Le piston 32 du premier embrayage E1 est disposé axialement entre la chambre de pression 31 , située axialement à l’arrière et la chambre d’équilibrage 33 située axialement à l’avant. The piston 32 is axially movable, here from rear to front between a disengaged position and a engaged position which correspond respectively to the open and closed states of the first clutch E1. The piston 32 of the first clutch E1 is disposed axially between the pressure chamber 31, located axially at the rear and the balancing chamber 33 located axially at the front.
Le piston 32 prend la forme d’une tôle ondulée et est incurvée axialement vers l’avant AV à son extrémité radiale extérieure. Les appuis extérieurs s’étendent parallèlement à l’axe longitudinal X vers l’avant AV et au travers d’ouvertures aménagées à travers le porte-disques d’entrée commun 5. The piston 32 takes the form of a corrugated sheet and is curved axially forwards AV at its outer radial end. The external supports extend parallel to the longitudinal axis X towards the front AV and through openings arranged through the common input disc holder 5.
À titre d’exemple non limitatif, le piston 32 peut être obtenu par emboutissage. By way of nonlimiting example, the piston 32 can be obtained by stamping.
La chambre de pression 31 du système d’actionnement 30 est agencée pour recevoir un certain volume de fluide hydraulique sous pression afin de générer un effort axial sur la deuxième partie du piston 32 et de configurer ainsi le premier embrayage E1 dans l’une des configurations décrites précédemment. Le fluide hydraulique pressurisé est avantageusement acheminé par l’intermédiaire de conduits de circulation fluidiques haute pression (non représentées sur le plan de coupe) traversant au moins en partie le moyeu principal 50 et débouchant radialement dans la chambre de pression 31 au niveau d’une face extérieure dudit moyeu principal 50. The pressure chamber 31 of the actuation system 30 is arranged to receive a certain volume of hydraulic fluid under pressure in order to generate an axial force on the second part of the piston 32 and thus to configure the first clutch E1 in one of the configurations previously described. The pressurized hydraulic fluid is advantageously conveyed by means of high pressure fluidic circulation conduits (not shown on the cutting plane) passing at least partially through the main hub 50 and opening radially into the pressure chamber 31 at a outer face of said main hub 50.
La chambre de pression 31 qui génère l’effort du piston 32 du premier embrayage E1 est associée à une chambre d’équilibrage 33 agencée pour recevoir un certain volume de fluide hydraulique. Le fluide, du type de lubrification ou de refroidissement est avantageusement acheminé par l’intermédiaire de conduits de circulation fluidiques basse pression (non représentées sur le plan de coupe) traversant au moins en partie le moyeu principal 50 et débouchant radialement dans la chambre d’équilibrage 33 au niveau d’une face extérieure dudit moyeu principal 50. The pressure chamber 31 which generates the force of the piston 32 of the first clutch E1 is associated with a balancing chamber 33 arranged to receive a certain volume of hydraulic fluid. The fluid, of the lubrication or cooling type, is advantageously conveyed by means of low pressure fluidic circulation conduits (not shown on the cutting plane) passing through at least part of the hub. main 50 and opening radially into the balancing chamber 33 at an external face of said main hub 50.
On notera que l’étanchéité de la chambre de pression 31 et de la chambre d’équilibrage 33 du système d’actionnement 30 est garantie par la présence de joints d’étanchéité. It will be noted that the sealing of the pressure chamber 31 and of the balancing chamber 33 of the actuation system 30 is guaranteed by the presence of seals.
L’élément de rappel élastique 34 du système d’actionnement 30 du premier embrayage E1 est situé radialement à l’extérieur de la chambre d’équilibrage 33 du premier embrayage E1. En particulier, l’élément de rappel élastique 34 est disposé axialement entre le porte-disque d’entrée commun 5 aux embrayages E1 , E2 et le piston 32 du système d’actionnement 30 du premier embrayage E1. The elastic return element 34 of the actuation system 30 of the first clutch E1 is located radially outside the balancing chamber 33 of the first clutch E1. In particular, the elastic return element 34 is disposed axially between the input disc carrier common 5 to the clutches E1, E2 and the piston 32 of the actuation system 30 of the first clutch E1.
Dans l’exemple considéré, le deuxième embrayage E2 et l’élément de rappel élastique 34 du système d’actionnement 30 du premier embrayage E1 se superposent radialement. In the example considered, the second clutch E2 and the elastic return element 34 of the actuation system 30 of the first clutch E1 overlap radially.
Avantageusement, l’élément de rappel élastique 34 du système d’actionnement 30 du premier embrayage E1 est une rondelle Belleville ou est composé de ressorts hélicoïdaux. Comme illustré sur la figure 1 , l’élément de rappel élastique 34 du piston 32 est formé par une pluralité de ressorts hélicoïdaux intercalés axialement entre une paroi arrière du couvercle d’équilibrage 35 et ledit piston 32. Advantageously, the elastic return element 34 of the actuation system 30 of the first clutch E1 is a Belleville washer or is composed of helical springs. As illustrated in FIG. 1, the elastic return element 34 of the piston 32 is formed by a plurality of helical springs interposed axially between a rear wall of the balancing cover 35 and said piston 32.
Le système d’actionnement 40 est lié au second embrayage E2 par l’intermédiaire d’un piston 42. D’une manière analogue au fonctionnement des pistons 22, 32 décrit précédemment, le piston 42 est agencé pour transmettre un deuxième effort axial, exercé parallèlement à l’axe longitudinal X, au premier deuxième embrayage E2 par l’intermédiaire d’une première partie supérieure collaborant avec les éléments de friction (flasques et disques de friction) dudit deuxième embrayage E2, et de sa deuxième partie inférieure collaborant avec un générateur d’effort pour configurer le deuxième embrayage E2 dans l’une des configurations détaillées précédemment. Au niveau de sa première partie, le piston 42 comprend des appuis extérieurs qui s’étendent axialement vers l’arrière AR. Les appuis viennent en appui sur le flasque d’extrémité de l’ensemble multidisque du deuxième embrayage E2. Dans l’exemple représenté sur la figure 1 , les appuis forment une couronne continue. The actuation system 40 is linked to the second clutch E2 by means of a piston 42. In a similar manner to the operation of the pistons 22, 32 described above, the piston 42 is arranged to transmit a second axial force, exerted parallel to the longitudinal axis X, to the first second clutch E2 via a first upper part collaborating with the friction elements (flanges and friction discs) of said second clutch E2, and its second lower part collaborating with a force generator to configure the second clutch E2 in one of the configurations detailed above. At its first part, the piston 42 includes external supports which extend axially towards the rear AR. The supports come to bear on the end flange of the multi-disc assembly of the second clutch E2. In the example shown in Figure 1, the supports form a continuous crown.
Le deuxième piston 42 est mobile axialement, ici de l’avant vers l’arrière entre une position débrayée et une position embrayée qui correspondent respectivement aux états ouvert et fermé du deuxième embrayage E2. Dans l’exemple considéré, le piston 32 du premier embrayage E1 et le piston 42 du deuxième embrayage E2 se déplacent axialement en sens opposé pour passer par exemple de la position débrayée à la position embrayée. En effet, les chambres de pression 31 , 41 de la présente invention exercent des forces d’actionnement axialement opposées sur lesdits pistons 32, 42. En particulier la force d’actionnement du piston 32 est dirigée axialement vers l’avant tandis que la force d’actionnement du piston 42 est dirigée axialement vers l’arrière. The second piston 42 is axially movable, here from front to rear between a disengaged position and a engaged position which correspond respectively to the open and closed states of the second clutch E2. In the example considered, the piston 32 of the first clutch E1 and the piston 42 of the second clutch E2 move axially in the opposite direction to pass for example from the disengaged position to the engaged position. Indeed, the pressure chambers 31, 41 of the present invention exert axially opposite actuation forces on said pistons 32, 42. In particular, the actuation force of the piston 32 is directed axially forward while the force actuating piston 42 is directed axially rearward.
Le piston 42 est commandé pour venir serrer axialement, en position embrayée, ledit ensemble multidisque du deuxième embrayage E2 contre des moyens de réaction. Les moyens de réaction sont formés directement sur la périphérie avant du porte-disque d’entrée commun 5. The piston 42 is controlled to clamp axially, in the engaged position, said multidisk assembly of the second clutch E2 against reaction means. The reaction means are formed directly on the front periphery of the common input disc holder 5.
Comme illustré sur la figure 1 , l’élément de rappel élastique 44 du système d’actionnement 40 du deuxième embrayage E2 est formé par une pluralité de ressorts hélicoïdaux intercalés axialement entre une paroi avant d’un couvercle d’équilibrage 45 de la chambre d’équilibrage 43 et ledit piston 42. As illustrated in FIG. 1, the elastic return element 44 of the actuation system 40 of the second clutch E2 is formed by a plurality of helical springs interposed axially between a front wall of a balancing cover 45 of the chamber d balancing 43 and said piston 42.
Les trous B et C assurent une fuite des chambres d’équilibrage E1 et E2 afin de lubrifier et/ou refroidir ces derniers. Holes B and C leak the balancing chambers E1 and E2 in order to lubricate and / or cool them.
Dans l’exemple considéré, le dispositif de transmission de couple comprend en outre trois paliers 71 , 72, 73. In the example considered, the torque transmission device also comprises three bearings 71, 72, 73.
Un premier palier axial 71 est interposé entre l’élément d’entrée de couple 2 et l’élément de sortie 6 afin de supporter les efforts axiaux de l’élément d’entrée de couple 2 malgré les vitesses de rotation différentes auxquelles peuvent respectivement tourner l’arbre d’entrée et le premier arbre de transmission. A first axial bearing 71 is interposed between the torque input element 2 and the output element 6 in order to withstand the axial forces of the torque input element 2 despite the different rotational speeds which can respectively rotate the input shaft and the first transmission shaft.
Un deuxième palier axial 72 est intercalé axialement entre l’élément de sortie de couple 6 définissant le porte-disque de sortie de l’embrayage E1 et l’élément de sortie de couple 7 définissant le porte-disque de sortie de l’embrayage E2 afin de pouvoir transmettre une charge axiale entre les deux porte-disques de sortie 22, 32 qui peuvent tourner à des vitesses différentes lorsque les premier et deuxième embrayages E1 , E2 sont configurés dans une configuration différente A second axial bearing 72 is axially interposed between the torque output element 6 defining the clutch output disc holder E1 and the torque output element 7 defining the clutch output disc holder E2 in order to be able to transmit an axial load between the two output disc carriers 22, 32 which can rotate at different speeds when the first and second clutches E1, E2 are configured in a different configuration
Enfin un troisième palier axial 73 est interposé entre l’élément de sortie de couple 7 de l’embrayage E2 et le moyeu principal 50. Finally, a third axial bearing 73 is interposed between the torque output element 7 of the clutch E2 and the main hub 50.
Avantageusement, les paliers 71 , 72, 73 sont des paliers à roulement avec un premier et deuxième disque entre lesquels est disposée une pluralité de corps de roulement. Advantageously, the bearings 71, 72, 73 are rolling bearings with a first and second disc between which a plurality of rolling bodies is disposed.
Le dispositif comprend en outre un organe de roulement 90, de préférence un roulement à billes, situé radialement entre la paroi interne 28 du carter de protection 27 et l’élément d’entrée de couple 2, de préférence entre la paroi interne 28 et la deuxième portion axiale 2a3, de la partie arrière 2a. The device further comprises a rolling member 90, preferably a ball bearing, located radially between the internal wall 28 of the protective casing 27 and the torque input element 2, preferably between the internal wall 28 and the second axial portion 2a3, of the rear part 2a.
Avantageusement, l’organe de roulement 90 supporte l’élément d’entrée de couple 2 et est composé d’une bague interne 90b en contact avec l’élément d’entré de couple 2 notamment la partie avant 2b de l’élément d’entrée de couple et d’une bague externe 90a en contact avec le carter de protection 27, notamment avec la paroi interne 28 du carter de protection. Advantageously, the rolling member 90 supports the torque input element 2 and is composed of an internal ring 90b in contact with the torque input element 2 in particular the front part 2b of the element torque input and an external ring 90a in contact with the protective casing 27, in particular with the internal wall 28 of the protective casing.
Dans l’exemple considéré le deuxième élément d’entrée de couple 5 comprend une zone de connexion électrique 65 apte à être liée en rotation avec une machine électrique tournante (non représentée) autour d’un axe parallèle à l’axe de rotation. In the example considered, the second torque input element 5 comprises an electrical connection area 65 capable of being linked in rotation with a rotary electrical machine (not shown) around an axis parallel to the axis of rotation.
La zone de connexion électrique 65 est ici décalée axialement de l’embrayage 10. La zone de connexion électrique 65, le premier embrayage de sortie E1 et le deuxième embrayage de sortie E2 sont empilés radialement en rapprochement de l’axe X La machine électrique est dite « off-line » car elle n’est pas concentrique à l’arbre de transmission mais sur un arbre parallèle. La zone de connexion électrique 65 est apte à coopérer directement avec un pignon de la machine électrique tournante. The electrical connection area 65 is here axially offset from the clutch 10. The electrical connection area 65, the first output clutch E1 and the second output clutch E2 are stacked radially in proximity to the X axis. The electric machine is so-called "off-line" because it is not concentric with the drive shaft but on a parallel shaft. The electrical connection area 65 is able to cooperate directly with a pinion of the rotary electrical machine.
La zone de connexion électrique 65 peut être réalisée sous la forme d’une couronne apte à être engrenée directement par un pignon ou indirectement (courroie, chaîne...) de la machine électrique tournante (non visible). La couronne peut présenter une denture hélicoïdale de forme complémentaire au pignon de la machine électrique tournante. The electrical connection area 65 can be produced in the form of a crown capable of being meshed directly by a pinion or indirectly (belt, chain, etc.) of the rotary electrical machine (not visible). The crown can have a helical toothing of complementary shape to the pinion of the rotary electric machine.
Bien que l'invention ait été décrite en liaison avec plusieurs modes de réalisation particuliers, il est bien évident qu'elle n'y est nullement limitée et qu'elle comprend tous les équivalents techniques des moyens décrits ainsi que leurs combinaisons si celles-ci entrent dans le cadre de l'invention. Although the invention has been described in connection with several particular embodiments, it is obvious that it is in no way limited thereto and that it includes all the technical equivalents of the means described as well as their combinations if these fall within the scope of the invention.
Dans les revendications, tout signe de référence entre parenthèses ne saurait être interprété comme une limitation de la revendication. In the claims, any reference sign in parentheses cannot be interpreted as a limitation of the claim.

Claims

Revendications Claims
[Revendication 1] [Dispositif (1) de transmission de couple, notamment pour véhicule automobile, comprenant : [Claim 1] [Torque transmission device (1), in particular for a motor vehicle, comprising:
- un premier élément d’entrée de couple (2) en rotation autour d’un axe X, apte à être couplé en rotation à un vilebrequin d’un moteur thermique, comprenant une partie arrière (2a) et une partie avant (2b), - a first torque input element (2) rotating around an axis X, capable of being coupled in rotation to a crankshaft of a heat engine, comprising a rear part (2a) and a front part (2b) ,
- un premier élément de sortie de couple (4), - a first torque output element (4),
- un embrayage d’entrée (10) accouplant sélectivement et par friction les éléments d’entrée de couple (2) et de sortie de couple (4), - an input clutch (10) selectively and frictionally coupling the torque input (2) and torque output (4) elements,
- un premier embrayage de sortie (E1) en rotation autour de l’axe X, accouplant sélectivement et par friction un deuxième élément d’entrée de couple (5) apte à être couplé audit premier élément de sortie de couple (4) et un deuxième élément de sortie de couple (6) apte à être couplé en rotation à un premier arbre d’entré d’une boite de vitesses, - a first output clutch (E1) rotating around the X axis, selectively and frictionally coupling a second torque input element (5) capable of being coupled to said first torque output element (4) and a second torque output element (6) capable of being coupled in rotation to a first input shaft of a gearbox,
- un deuxième embrayage de sortie (E2) en rotation autour de l’axe X, accouplant sélectivement et par friction ledit deuxième élément d’entrée de couple (5) et un troisième élément de sortie de couple (7) apte à être couplé en rotation à un deuxième arbre d’entré d’une boite de vitesses, le premier et deuxième embrayage de sortie (E1 , E2) étant empilés radialement - a second output clutch (E2) rotating around the X axis, selectively and frictionally coupling said second torque input element (5) and a third torque output element (7) capable of being coupled in rotation to a second input shaft of a gearbox, the first and second output clutch (E1, E2) being stacked radially
- un système d’actionnement (20) associé à l’embrayage d’entrée (10) comprenant une chambre de pression (21) et un piston (22) mobile axialement, - an actuation system (20) associated with the input clutch (10) comprising a pressure chamber (21) and an axially movable piston (22),
- un carter de protection (27) agencé pour envelopper au moins partiellement l’élément d’entrée de couple (2), l’élément de sortie de couple (4), l’embrayage d’entrée (10) et le système d’actionnement (20), ledit carter (27) comportant une paroi interne (28) s’étendant axialement autour de l’axe X et un réseau de passage d’un fluide (80) agencé pour alimenter en fluide ledit système d’actionnement (20) - a protective casing (27) arranged to at least partially envelop the torque input element (2), the torque output element (4), the input clutch (10) and the system of actuation (20), said casing (27) comprising an internal wall (28) extending axially around the axis X and a fluid passage network (80) arranged to supply fluid to said actuation system (20)
caractérisé en ce que ladite partie arrière (2a) est ménagé radialement à l’extérieur et à l’intérieur de ladite paroi interne (28). characterized in that said rear part (2a) is formed radially outside and inside said internal wall (28).
[Revendication 2] Dispositif (1) de transmission de couple selon l’une quelconque des revendications précédentes, caractérisé en ce que ladite partie arrière (2a) de l’élément d’entrée de couple (2) comporte au moins un perçage (81) traversant qui autorise le passage dudit fluide au travers de ladite partie arrière (2a). [Claim 2] Torque transmission device (1) according to any one of the preceding claims, characterized in that said rear part (2a) of the torque input element (2) comprises at least one bore (81 ) through which allows the passage of said fluid through said rear portion (2a).
[Revendication 3] Dispositif (1) de transmission de couple selon la revendication 1 ou 2, caractérisé en ce que la partie arrière (2a) de l’élément d’entrée de couple (2) est composée d’une première et deuxième portion axiale (2ai, 2a3) ainsi que d’une paroi radiale (2a2) reliant la première portion axiale à la deuxième portion axiale. [Claim 3] Torque transmission device (1) according to claim 1 or 2, characterized in that the rear part (2a) of the torque input element (2) is composed of a first and second axial portion (2ai, 2a 3 ) as well as a radial wall (2a 2 ) connecting the first axial portion to the second axial portion.
[Revendication 4] Dispositif (1) de transmission de couple selon la revendication précédente, caractérisé en ce que l’embrayage d’entrée (10), la première portion axiale (2ai), la paroi interne (28) du carter de protection (27), et la deuxième portion axiale (283) se succèdent radialement en rapprochement de l’axe X. [Claim 4] Device (1) for transmitting torque according to the preceding claim, characterized in that the input clutch (10), the first axial portion (2ai), the internal wall (28) of the protective casing ( 27), and the second axial portion (28 3 ) succeed one another radially in approach to the axis X.
[Revendication 5] Dispositif (1) de transmission de couple selon la revendication 3 ou 4, caractérisé en ce que l’au moins un perçage (81) traverse radialement la première portion axiale (2ai), ladite portion étant située radialement à l’extérieur de la paroi interne (28) de manière à autoriser le passage du fluide radialement à travers la première portion axiale (2ai). [Claim 5] Torque transmission device (1) according to claim 3 or 4, characterized in that the at least one bore (81) passes radially through the first axial portion (2ai), said portion being located radially to the outside of the internal wall (28) so as to allow the passage of the fluid radially through the first axial portion (2ai).
[Revendication 6] Dispositif (1) de transmission de couple selon l’une quelconque des revendications précédentes, caractérisé en ce qu’il comprend en outre un organe de roulement (90) situé radialement entre la paroi interne (28) du carter de protection (27) et l’élément d’entrée de couple (2). [Claim 6] Torque transmission device (1) according to any one of the preceding claims, characterized in that it further comprises a rolling member (90) located radially between the internal wall (28) of the protective casing (27) and the torque input element (2).
[Revendication 7] Dispositif (1) de transmission de couple selon la revendication 1 , caractérisé en ce que ledit deuxième élément d’entrée de couple (5) comprend une zone de connexion électrique (65) apte à être lié en rotation avec une machine électrique tournante autour d’un axe parallèle à l’axe de rotation X. [Claim 7] Torque transmission device (1) according to claim 1, characterized in that said second torque input element (5) comprises an electrical connection zone (65) capable of being linked in rotation with a machine electric rotating around an axis parallel to the axis of rotation X.
[Revendication 8] Dispositif (1) de transmission de couple selon la revendication 7, caractérisé en ce que la zone de connexion électrique (65), le premier embrayage de sortie (E1) et le deuxième embrayage de sortie (E2) sont empilés radialement en rapprochement de l’axe X. ) [Claim 8] Torque transmission device (1) according to claim 7, characterized in that the electrical connection zone (65), the first output clutch (E1) and the second output clutch (E2) are stacked radially near the X axis.)
PCT/EP2019/085782 2018-12-20 2019-12-17 Transmission device for a motor vehicle WO2020127370A1 (en)

Priority Applications (2)

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EP19832332.1A EP3899300A1 (en) 2018-12-20 2019-12-17 Transmission device for a motor vehicle
CN201980090635.6A CN113366236A (en) 2018-12-20 2019-12-17 Transmission for a motor vehicle

Applications Claiming Priority (2)

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FR1873598A FR3090768B1 (en) 2018-12-20 2018-12-20 Motor vehicle transmission device
FR1873598 2018-12-20

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CN113366236A (en) 2021-09-07
EP3899300A1 (en) 2021-10-27
FR3090768A1 (en) 2020-06-26
FR3090768B1 (en) 2022-01-21

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