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WO2018093108A1 - Triple embrayage et actionneur correspondant - Google Patents

Triple embrayage et actionneur correspondant Download PDF

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Publication number
WO2018093108A1
WO2018093108A1 PCT/KR2017/012841 KR2017012841W WO2018093108A1 WO 2018093108 A1 WO2018093108 A1 WO 2018093108A1 KR 2017012841 W KR2017012841 W KR 2017012841W WO 2018093108 A1 WO2018093108 A1 WO 2018093108A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
housing
piston
clutch housing
motor
Prior art date
Application number
PCT/KR2017/012841
Other languages
English (en)
Korean (ko)
Inventor
박동훈
Original Assignee
씨스톤 테크놀로지스(주)
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 씨스톤 테크놀로지스(주) filed Critical 씨스톤 테크놀로지스(주)
Priority to US16/332,486 priority Critical patent/US20210277958A1/en
Priority to CN201780062073.5A priority patent/CN109790880B/zh
Priority to EP17870970.5A priority patent/EP3543556B1/fr
Priority claimed from KR1020170151219A external-priority patent/KR101940043B1/ko
Publication of WO2018093108A1 publication Critical patent/WO2018093108A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • 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
    • 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 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 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 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts

Definitions

  • the present invention relates to a triple clutch and an actuator thereof, and more particularly to a triple clutch and an actuator applicable to a dual clutch transmission of a hybrid vehicle.
  • DCT dual clutch transmission
  • an electric vehicle (EV) or a hybrid electric vehicle (HEV) that uses electric energy as an eco-friendly vehicle may be used.
  • a hybrid vehicle is a vehicle that uses two or more power sources. it means.
  • an engine and a motor are used as power sources of a hybrid vehicle, and the motor is directly connected to the transmission and the engine is connected to the transmission through an engine clutch.
  • the transmission used in the hybrid vehicle is DCT, all three clutches must be arranged before and after the motor, thereby causing a problem in that the transmission length is long.
  • the present invention is to provide a triple clutch that can realize a compact transmission structure by efficiently disposing three clutches used in the dual clutch transmission of the hybrid vehicle.
  • the present invention is to provide an actuator capable of effectively operating the triple clutch.
  • Triple clutch includes an input shaft for receiving the rotational power of the engine;
  • a motor including a motor housing, a stator fixedly mounted to an outer circumferential surface of the motor housing, and a rotor rotatably disposed inside a radius of the stator;
  • a clutch housing operatively connected to the rotor, rotating together with the rotor, receiving a rotational power of the motor, and forming a clutch space therein;
  • a first clutch for selectively transmitting rotational power of the clutch housing to a first output shaft;
  • a second clutch for selectively transmitting rotational power of the clutch housing to a second output shaft;
  • a third clutch for selectively transmitting rotational power of the input shaft to the clutch housing, wherein the first, second and third clutches may be disposed in the clutch space.
  • the first, second and third clutches may include first, second and third disc packs, respectively, and at least a portion of the first, second and third disc packs may be disposed within the length of the rotor in the axial direction.
  • the first and second clutches may be arranged side by side in the axial direction, and the third clutch may be disposed inside a radius of the first and second clutches.
  • the first clutch includes a first disk pack for selectively connecting the first output shaft and the clutch housing by axial force, a drum configured to selectively apply axial force to the first disk pack, and the second clutch includes an axial force.
  • a second disk pack for selectively connecting the second output shaft and the clutch housing, wherein the drum is operatively connected to the clutch housing to continuously receive rotational power of the clutch housing,
  • the pack may optionally be adapted to operatively connect the second output shaft and the drum.
  • the motor housing extends in the axial direction and has a motor housing outer periphery to which the stator is fixedly attached to an inner circumferential surface thereof, a motor housing connecting portion extending radially inward at the front end of the motor housing outer peripheral portion, and an axial rearward at the inner end of the motor housing connecting portion.
  • a motor housing inner circumference extending to the side, wherein the clutch housing extends in an axial direction and is radially inward at a front end of the clutch housing outer circumference, the clutch housing outer circumference of which the rotor is fixedly attached to an outer circumference thereof, and from the motor housing connection portion. It may include a clutch housing connecting portion spaced apart in the axial direction, and an inner peripheral portion of the clutch housing extending in the axial direction from the inner end of the clutch housing connecting portion and radially spaced apart from the inner portion of the motor housing.
  • the first clutch may include a first actuating hub operatively connected to the first output shaft; A first disc pack mounted between the outer peripheral portion of the clutch housing and the first actuating hub to selectively connect the clutch housing and the first actuating hub by axial force; A drum operatively connected to an inner circumferential surface of the clutch housing outer circumference and adapted to axially move and selectively apply axial force to the first disk pack; And a first pressure plate adapted to apply axial force to the drum.
  • the second clutch comprises a second actuating hub operatively connected to the second output shaft; A second disc pack mounted between the drum and the second actuating hub to selectively connect the drum and the second actuating hub by axial force; And a second pressure plate moving in an axial direction and selectively applying an axial force to the second disc pack.
  • the first pressure plate is mounted on the inner circumferential surface of the drum to be movable in the axial direction together with the drum, and the second pressure plate is splined to the inner circumferential surface of the drum to move in the axial direction independently of the drum. Can be.
  • the first pressure plate may be disposed axially backward of the second pressure plate.
  • the third clutch comprises a third actuating hub operatively connected to the input shaft; A third disc pack mounted between the third actuating hub and the clutch housing inner circumference to selectively connect the clutch housing and the third actuating hub by axial force; And a third pressure plate moving in the axial direction and selectively applying an axial force to the third disk pack.
  • the third pressure plate may be configured to exert an axial force on the third disk pack through the clutch housing connecting portion.
  • Triple clutch is the input shaft for receiving the rotational power of the engine;
  • a motor including a motor housing, a stator fixedly mounted to an outer circumferential surface of the motor housing, and a rotor rotatably disposed inside a radius of the stator;
  • a clutch housing operatively connected to the rotor, rotating together with the rotor, receiving a rotational power of the motor, and forming a clutch space therein;
  • a first clutch for selectively transmitting rotational power of the clutch housing to a first output shaft;
  • a second clutch for selectively transmitting rotational power of the clutch housing to a second output shaft;
  • a third clutch for selectively transmitting rotational power of the input shaft to the clutch housing, wherein the first, second and third clutches include first, second and third disc packs, respectively. At least a portion of the 3 disc pack may be disposed within the length of the rotor in the axial direction.
  • the clutch housing comprises a first support for axially supporting the first clutch, wherein the first, second and third clutches each comprise first, second and third actuation hubs and the second actuation hub. And a second actuating hub extension extending axially rearward, wherein the axial force applied to the first clutch is transmitted to the clutch housing and supported by a first support bearing disposed axially between the clutch housing and the motor housing.
  • the axial force applied to the second clutch is transmitted to and supported by the second support bearing through a snap ring mounted on the second operating hub extension, and the axial force applied to the third clutch is mounted on the inner circumferential surface of the clutch housing. It can be transmitted to the clutch housing through the snap ring and supported by a third support bearing disposed on the axial rear side between the clutch housing and the motor housing.
  • the clutch housing includes a first support for axially supporting the first clutch, the first, second and third clutches each including first, second and third actuating hubs, the second actuating hub being A first support bearing coupled to the second output shaft by a spline coupling and a snap ring mounted on the second output shaft, and the axial force applied to the first clutch is transmitted to the clutch housing and disposed axially between the clutch housing and the motor housing.
  • Axial force applied to the second clutch is transmitted to the second output hub by a snap ring mounted on the second output shaft and transmitted to the second support bearing mounted on the output shaft.
  • the axial force applied to the third clutch is transmitted to the clutch housing through a snap ring mounted on the inner circumferential surface of the clutch housing, and is arranged in the axial rear side between the clutch housing and the motor housing. It can be supported by a support bearing.
  • An actuator according to another embodiment of the present invention may be applied to a triple clutch according to embodiments of the present invention.
  • the actuator is configured to transmit the axial force to the first clutch, the second clutch or the third clutch, respectively.
  • the actuator includes a first piston that transmits the axial force to the first clutch, a second piston that transmits the axial force to the second clutch, and a third piston that transmits the axial force to the third clutch, wherein the first piston and the third piston
  • the two pistons may be provided in the actuator housing, and the third piston may be mounted in the motor housing.
  • the first piston and the second piston are separated by a partition wall disposed therebetween, and an outer circumferential surface of the second piston may be located radially outward from an inner circumferential surface of the first piston.
  • the partition wall is mounted to the actuator housing, extending in the axial front side, the partition mounting portion that the outer end of the second piston slidably contact; A partition connecting part extending radially inward from the partition mounting part; And a partition extension part extending from the inner end of the partition connection part to the front side in the axial direction and in which the inner circumferential surface of the first piston is slidably contacted.
  • a first support plate is mounted on the barrier rib extension to the front side of the first piston, and a first return spring is mounted between the first support plate and the front surface of the first piston, and a second return is connected between the front surface of the second piston and the partition connection part.
  • the spring can be mounted.
  • the motor housing extends in the axial direction and has a motor housing outer periphery to which the stator is fixedly attached to an inner circumferential surface thereof, a motor housing connecting portion extending radially inward at the front end of the motor housing outer peripheral portion, and an axial rearward at the inner end of the motor housing connecting portion. And a motor housing inner periphery extending to the side, wherein the motor housing connecting portions are radially spaced apart from each other, and further include first and second protrusions extending in an axial rearward direction, and the third piston includes the first and second protrusions. It can be mounted in the space between the protrusions.
  • a second support plate may be mounted on an inner circumferential surface of the first protrusion, and a third return spring may be mounted between the second support plate and the rear surface of the third piston.
  • FIG. 1 is a cross-sectional view of a triple clutch according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view of a triple clutch according to another embodiment of the present invention.
  • FIG. 3 is a schematic diagram showing the arrangement of three clutches in a triple clutch according to an embodiment of the present invention.
  • front means “side”, “part”, or “end” close to the input axis
  • rear means "rear”, “rear”, “rear” ',' Or 'back end' indicates 'side', 'part' or 'end' far from the input axis.
  • the triple clutch according to the embodiment of the present invention can be used, for example, in a hybrid vehicle using DCT.
  • Hybrid vehicle refers to a vehicle that runs using two or more power sources.
  • a hybrid vehicle using an engine and a motor as a power source is illustrated.
  • the dual clutch transmission In the dual clutch transmission, a plurality of input gears are distributed in two transmission input shafts, and a plurality of output gears each of which is engaged with the plurality of input gears is distributed in two transmission output shafts.
  • the dual clutch transmission also includes a plurality of synchronizer mechanisms, wherein the plurality of synchronizer mechanisms are selectively operated to connect one of the plurality of output gears and one of the two transmission output shafts.
  • the dual clutch is adapted to transmit the power of a power source (eg, engine and motor) to either of the two transmission output shafts.
  • a dry or wet clutch may be used as the double clutch.
  • the input shaft and the first and second output shafts in this specification and claims are related to the flow of power in terms of triple clutches. That is, the input shaft refers to an axis for inputting the rotational power of the engine to the triple clutch, it may be a crank shaft of the engine or a separate shaft connected thereto, and the output shaft refers to an axis for outputting the rotational power from the triple clutch. Can be.
  • the two members are 'operatively connected' means that they are connected to transmit the rotational power of one member to the other member, means such as welding, bolts, rivets, spline coupling, gear coupling, etc. It means that through the two members are rotatably connected with each other.
  • FIG. 1 is a cross-sectional view of a triple clutch according to an embodiment of the present invention.
  • the triple clutch 1 selectively receives rotational power of the input shaft 2, and receives rotational power of the input shaft 2 and / or the motor 20. It is for selectively transmitting to the first output shaft 4 or the second output shaft (6).
  • the triple clutch 1 includes an input shaft 2, a motor 20, a clutch housing 40, a first clutch 11, a second clutch 12, a third clutch 13, and actuators 15A and 15B. ).
  • the first clutch 11, the second clutch 12, the third clutch 13, and the actuators 15A and 15B are disposed inside the transmission housing.
  • the transmission housing is formed in a generally cylindrical shape having a space therein.
  • the input shaft 2, the first output shaft 4 and the second output shaft 6 are arranged in the center of the transmission housing.
  • either one of the first output shaft 4 and the second output shaft 6 is associated with the implementation of the hole means (for example, 1st stage, 3rd stage, 5th stage, 7th stage, etc.), and the first output shaft (4) or the other of the second output shaft 6 relates to the implementation of mating means (e.g., two, four, six, eight, etc.). That is, the rotational power of the input shaft 2 and / or the motor 20 is selectively applied to the first output shaft 4 or the second output shaft 6 through the operation of the first clutch 11 or the second clutch 12. By transmitting the alternating hole means and mating means are made to shift.
  • the engine mode driving mode running only by the power of the engine
  • hybrid mode power and motor of the engine
  • the driving mode of driving with the power of may be implemented, and when the third clutch 13 does not operate, the electric vehicle mode (the driving mode of driving with the power of the motor) may be implemented.
  • the input shaft 2 is for inputting rotational power of a power source (for example, an engine) to the triple clutch 1, and may be a crank shaft or a separate shaft connected thereto.
  • a power source for example, an engine
  • the input shaft 2 is illustrated as an axis connected to the crank shaft through the torsional damper 10, but is not limited thereto.
  • An input shaft spline 3 is formed on the input shaft 2 to be operatively connected to the crank shaft or to the torsional damper 10 connected thereto.
  • the first output shaft 4 and the second output shaft 6 may each be two input shafts provided in the dual clutch transmission.
  • the second output shaft 6 is formed as a hollow shaft, and the first output shaft 4 is disposed inside the second output shaft 6 without rotation interference with the second output shaft 6. Further, the front end of the first output shaft 4 protrudes from the front end of the second output shaft 6 to the axial front side and extends to the end of the input shaft 2.
  • a bearing 222 is disposed between the end of the input shaft 2 and the front end of the first output shaft 4 to facilitate relative rotation of the input shaft 2 and the first output shaft 4.
  • Spline 5 or gear teeth are formed on the outer peripheral surface of the front end of the first output shaft 4
  • splines 7 or gear teeth are formed on the outer peripheral surface of the front end of the second output shaft 6, but the present invention is not limited thereto. .
  • the torsional damper 10 is to attenuate the torsional vibration of the rotational power transmitted from the crankshaft, and the output of the torsional damper 10 is transmitted to the input shaft 2.
  • the motor 20 includes a motor housing 21, a stator 32, and a rotor 34.
  • the motor housing 21 may be part of the transmission housing or may be manufactured separately from the transmission housing and coupled to the transmission housing.
  • the motor housing 21 includes a motor housing outer peripheral portion 22, a motor housing connecting portion 24, and a motor housing inner peripheral portion 30.
  • the motor housing outer periphery 22 extends from the front side to the rear side in the axial direction.
  • the motor housing connecting portion 24 extends radially inward at the front end of the motor housing outer peripheral portion 22.
  • the motor housing connecting portion 24 further includes first and second protrusions 26 and 28 spaced apart from each other in the radial direction and extending laterally in the axial direction.
  • the motor housing inner peripheral portion 30 extends from the inner end of the motor housing connecting portion 24 to the axial rear side.
  • the motor housing step portion 31 is formed on the outer circumferential surface of the motor housing inner circumferential portion 30.
  • the motor housing inner peripheral portion 30 is spaced radially outward from the input shaft 2, and bearings 212 and 220 are mounted between the inner peripheral surface of the motor housing inner peripheral portion 30 and the outer peripheral surface of the input shaft 2. This facilitates the relative rotation of the motor housing 21 and the input shaft (2).
  • a sealing member 200 may be mounted between the inner circumferential surface of the inner circumference of the motor housing 30 and the outer circumferential surface of the input shaft 2 to the front side of the bearing 212 to prevent the oil supplied to the triple clutch from leaking out. Can be.
  • the motor housing 21 forms a mounting space of the stator 32, the rotor 34 and the clutches.
  • the shape of the motor housing 21 can be determined by those skilled in the art according to design intention, and is not limited to the shape shown in the present specification and drawings.
  • the stator 32 is fixedly mounted to the inner circumferential surface of the motor housing outer circumferential portion 22.
  • the stator 32 is electrically connected to an inverter (not shown) to receive an electrical signal. Accordingly, the stator 32 forms a magnetic field therein.
  • the rotor 34 is spaced apart from the inside of the stator 32 and is formed in a cylindrical shape. When the electrical signal is input to the stator 32, the rotor 34 is rotated.
  • the clutch housing 40 forms a clutch space in which the first, second, and third clutches 11, 12, and 13 are disposed, and is operatively connected to the rotor to rotate together with the rotor to rotate the motor 20. Get power.
  • the first, second and third clutches 11, 12 and 13 are arranged in a clutch space, in particular a space within the length L of the rotor 34 in the axial direction, thereby providing a compact structure.
  • the clutch housing 40 includes a clutch housing outer peripheral portion 42, a clutch housing connecting portion 44, and a clutch housing inner peripheral portion 48.
  • the clutch housing outer circumferential portion 42 extends from the front side to the rear side in the axial direction, and its outer circumferential surface is fixedly attached to the inner circumferential surface of the rotor 34. Therefore, when the rotor 34 rotates, the clutch housing 40 also rotates together.
  • the clutch housing connecting portion 44 extends radially inward at the front end of the clutch housing outer peripheral portion 42 and is spaced axially rearward from the motor housing connecting portion 24. At the set positions of the clutch housing connecting portion 44, a first support portion 45 protruding in the rearward direction in the axial direction and a through hole 46 drilled in the axial direction may be formed.
  • the clutch housing inner peripheral portion 48 extends in the axial direction at the inner end of the clutch housing connecting portion 44 and is spaced radially outward from the motor housing inner peripheral portion 30.
  • the first clutch housing stepped portion 50 facing the motor housing stepped portion 31 is formed at the front side of the inner circumferential surface of the clutch housing inner circumferential portion 48.
  • a first support bearing 214 is mounted between the motor housing step portion 31 and the first clutch housing step portion 50.
  • a second clutch housing step portion 52 is formed at the rear side of the inner circumferential surface of the inner circumferential portion 48 of the clutch housing.
  • the shape of the clutch housing 40 can be determined by those skilled in the art according to design intention, it is not limited to the shape shown in the specification and drawings.
  • the first clutch 11 is disposed radially outward and axially forward in the clutch space.
  • the first clutch 11 is for selectively transmitting rotational power of the input shaft 2 and / or the motor 20 to the first output shaft 4, and includes a first disk pack 66 and a first operating hub ( 68), drum 72 and first pressure plate 110.
  • the first disc pack 66 is disposed between the clutch housing 40 and the first actuating hub 68 to selectively transmit rotational power of the clutch housing 40 to the first actuating hub 68.
  • the first support part 45 formed on the clutch housing connecting part 44 supports the first disc pack 66 in the axial direction so that the first disc pack 66 may be frictionally coupled.
  • the first disk pack 66 includes a first separator plate 60, a first friction disk 62, and a first separating spring 64. Although not limited thereto, the first separating spring 64 may be deleted as necessary.
  • the plurality of first separate plates 60 are splined to the inner circumferential surface of the clutch housing outer circumferential portion 42.
  • the plurality of first friction disks 62 are splined to the outer circumferential surface of the first actuating hub 68 and are alternately arranged with the plurality of first separator plates 60.
  • At least one first separating spring 64 is disposed between adjacent first separate plates 60 outside the radius of the first friction disk 62 to provide axial elastic force to the first separate plate 60. do.
  • the first separating spring 64 maintains a gap between the first separate plates 60 when the first clutch 11 is not engaged, thereby reducing drag torque and simultaneously releasing the first clutch 11. To make it smooth.
  • the first separating spring 64 may act as a return spring to release the first clutch 11.
  • the first actuating hub 68 transmits the rotational power of the clutch housing 40 transmitted through the first disc pack 66 to the first output shaft 4.
  • Splines 70 or gear teeth are formed on the inner circumferential surface of the first actuating hub 68 so that power can be transmitted by engaging with the splines 5 or gear teeth of the first output shaft 4.
  • a bearing 217 is interposed between the radially inner portion of the first actuating hub 68 and the rear end of the input shaft 2 to facilitate relative rotation of the first actuating hub 68 and the input shaft 2. Support the first actuating hub 68 in the axial direction.
  • the drum 72 is formed in a cylindrical shape, and is coupled to the inner circumferential surface of the clutch housing outer peripheral portion 42 so as to be movable in the axial direction through spline coupling or the like, and rotates together with the clutch housing 40 to rotate the clutch housing 40. Receives rotational power of).
  • the drum 72 is disposed at the rear side of the first disc pack 66 and extends in the axial rear side.
  • a first pressing part 74 is formed at the front end of the drum 72 to transmit the axial force to the first disc pack 66.
  • the first pressure plate 110 is coupled to the rear side of the drum 72.
  • the outer end of the first pressure plate 110 is splined to the inner circumferential surface of the drum 72, and the front and rear sides of the outer end of the first pressure plate 110 of the drum 72 are separated from each other.
  • Each of the snap rings 16 fixedly mounted on the inner circumferential surface is disposed such that the first pressure plate 110 and the drum 72 can move together in the axial direction.
  • the coupling of the first pressure plate 110 and the drum 72 is not limited thereto.
  • a first accommodating part 112 is formed at an inner end of the first pressure plate 110 to accommodate the first application bearing 114.
  • the shape of the first pressure plate 110 may be determined by those skilled in the art according to design intention, and is not limited to the shape shown in the specification and drawings.
  • the second clutch 12 is disposed radially outward and axially rearward in the clutch space.
  • the second clutch 12 is for selectively transmitting rotational power of the input shaft 2 and / or the motor 20 to the second output shaft 6, and includes a second disk pack 86 and a second operating hub ( 88, and a second pressure plate 116.
  • the second disc pack 86 is disposed between the drum 72 and the second actuating hub 88 to selectively transmit rotational power of the drum 72 to the second actuating hub 88.
  • the second disc pack 86 is disposed between the first pressing part 74 and the first pressure plate 110 in the axial direction.
  • the second disk pack 86 includes a second separator plate 80, a second friction disk 82, and a second separating spring 84. Although not limited thereto, the second separating spring 84 may be deleted as necessary.
  • the plurality of second separate plates 80 are splined to the outer circumferential surface of the second actuating hub 88.
  • the plurality of second friction disks 82 are splined to the inner circumferential surface of the drum 72 and are alternately disposed with the plurality of second separator plates 80.
  • At least one second separating spring 84 is disposed between adjacent second separate plates 80 inside the radius of the second friction disk 82 to provide axial elastic force to the second separate plate 80. do.
  • the second separating spring 84 maintains the gap between the second separate plates 80 when the second clutch 12 is not engaged, thereby reducing drag torque and smoothly releasing the second clutch 12. .
  • the second separating spring 84 may act as a return spring to release the second clutch 12.
  • the second actuating hub 88 transmits the rotational power of the drum 72 transmitted through the second disc pack 86 to the second output shaft 6.
  • a second actuating hub extension 89 extends axially to the rear side. At least a portion of the second actuating hub extension 89 may be radially spaced apart from the second output shaft 6.
  • a spline 92 or a gear tooth is formed on the front inner circumferential surface of the second operation hub extension 89 so as to transmit rotational power by combining with the spline 7 or gear tooth of the second output shaft 6. have.
  • a bearing 219 is interposed between the radially inner portion of the second actuating hub 88 and the radially inner portion of the first actuating hub 68 so that the second actuating hub 88 and the first actuating hub 68 are opposed to each other. While smoothly rotating, the second actuating hub 88 is supported in the axial direction.
  • the second support portion 90 extends radially outwardly in front of the outer circumferential surface of the second actuating hub 88.
  • the second support part 90 supports the second disc pack 86 in the axial direction. Therefore, when the second pressure plate 116 moves to the left in the figure, the second support portion 90 supports the axial force on the second separate plate 80 and the second friction disk 82.
  • the second pressure plate 116 optionally frictionally couples the second disc pack 86 to selectively transmit rotational power of the drum 72 to the second actuating hub 88.
  • the second pressure plate 116 is splined to the inner circumferential surface of the drum 72 on the rear side of the second disk pack 86 to be movable in the axial direction.
  • a second pressing part 118 for pressing the second disc pack 86 may be formed in the radially outer portion of the second pressure plate 116.
  • a second accommodating part 120 is formed at a radially inner end of the second pressure plate 116, and the second accommodating part 120 is configured to accommodate the second application bearing 122. .
  • the second pressure plate 116 is disposed at the axial front side of the first pressure plate 110.
  • the shape of the second pressure plate 116 may be determined by those skilled in the art according to design intention, and is not limited to the shape shown in the specification and the drawings.
  • the third clutch 13 is disposed in the radially inner side and the axially front side of the first disc pack 66 in the clutch space.
  • the third clutch 13 is for selectively transmitting the rotational power of the input shaft 2 to the clutch housing 40, the third operating hub 108, the third disk pack 106, and the third pressure plate (194).
  • the third actuating hub 108 is operatively connected to the input shaft 2 by welding or the like, rotates with the input shaft 2, and receives rotational power of the input shaft 2.
  • the third disc pack 106 is disposed between the third actuating hub 108 and the clutch housing inner peripheral portion 48 to selectively transmit the rotational power of the input shaft 2 to the clutch housing 40.
  • the third disk pack 106 includes a third separate plate 100, a third friction disk 102 and a third separating spring 104. Although not limited thereto, the third separating spring 104 may be deleted as necessary.
  • the plurality of third separate plates 100 are splined to the outer circumferential surface of the inner circumferential portion 48 of the clutch housing.
  • the plurality of third friction disks 102 are splined to the inner circumferential surface of the third actuating hub 108 and are alternately disposed with the plurality of third separate plates 100.
  • At least one third separating spring 104 is disposed between neighboring third separate plates 100 inside the radius of the third friction disk 102 to provide an axial elastic force to the third separate plate 100. do.
  • the third separating spring 104 maintains the gap between the third separate plates 100 when the third clutch 13 is not engaged, thereby reducing drag torque and smoothly releasing the third clutch 13. .
  • the third separating spring 104 may act as a return spring to release the third clutch 13.
  • a snap ring 23 is mounted on the rear clutch housing inner peripheral portion 48 of the third disc pack 106 to support the third disc pack 106 in the axial direction.
  • the snap ring 23 supports the axial force on the third separate plate 100 and the third friction disk 102.
  • the third pressure plate 194 selectively frictionally couples the third disc pack 106 to selectively transmit rotational power of the input shaft 2 to the clutch housing 40.
  • the third pressure plate 194 extends through the through hole 46 from the outside of the clutch housing 40 to the third disk pack 106.
  • a third pressing unit 196 is formed at the rear end of the third pressure plate 194.
  • the third pressing unit 196 may apply an axial force to the third separator plate 100 to frictionally couple the third separator plate 100 and the third friction disk 102.
  • a third accommodating part 198 is formed at the front end of the third pressure plate 194, and the third accommodating part 198 is configured to accommodate the third application bearing 192.
  • the shape of the third pressure plate 194 may be determined by those skilled in the art according to design intention, and is not limited to the shape shown in the present specification and drawings.
  • the actuators 15A and 15B provide the actuation force (axial force) to the triple clutch 1, and include the first and second actuators 15A and the third actuator 15B.
  • the first and second actuators 15A are configured to operate the first and second clutches 11 and 12 and include an actuator housing 130.
  • the actuator housing 130 is formed in a thick disk shape, and may be integrally formed with the transmission housing or separately manufactured and attached to the transmission housing.
  • the inner diameter portion of the actuator housing 130 is recessed toward the rear in the axial direction to form a piston space in which the first and second pistons 140 and 160 are mounted.
  • first and second clutch housing protrusions 132 and 134 extending in the axial front side are formed in the radially outer side and the radially inner side of the piston space.
  • the second clutch housing protrusion 134 is radially spaced apart from the second actuating hub extension 89.
  • a second support bearing 218 is mounted between the rear end of the inner circumferential surface of the actuator housing 130 and the rear end of the second actuating hub extension 89.
  • a snap ring 18 is mounted on an outer circumferential surface of the second actuating hub extension 89.
  • the first piston 140, the partition wall 150, and the second piston 160 are mounted in the piston space.
  • the first piston 140 is to provide axial force to the first pressure plate 110 through the first application bearing 114
  • the second piston 160 is through the second application bearing 122 To provide axial force to the second pressure plate 116.
  • the first piston 140 is disposed in the radial space between the inner circumferential surface of the first clutch housing protrusion 132 and the partition wall 150.
  • the first application bearing 114 is mounted between the front surface of the first piston 140 and the first accommodation portion 112.
  • the second piston 160 is disposed in the radial space between the partition wall 150 and the second clutch housing protrusion 134.
  • a second piston inner circumferential portion 162 extends in the axial front side at an inner end of the second piston 160, and is disposed between the front end of the second piston inner circumferential portion 162 and the second accommodating portion 120.
  • the second application bearing 122 is mounted.
  • the partition wall 150 is disposed between the first piston 140 and the second piston 160 to independently control the operation of the first piston 140 and the operation of the second piston 160.
  • the partition wall 150 includes a partition mounting part 152, a partition wall connecting part 154, and a partition wall extending part 156.
  • the partition mounting portion 152 is formed in the axial direction and is mounted on the inner circumferential surface of the first clutch housing protrusion 132 by a press-fit method.
  • the partition connecting portion 154 extends radially inward from a front end of the partition mounting portion 152.
  • the partition extension part 156 extends from the inner end of the partition connection part 154 toward the axial front side.
  • a first support plate 148 is mounted on the front end of the partition extension part 156, and a first return spring 146 is mounted between the first support plate 148 and the front surface of the first piston 140. It provides an elastic force to one piston (140).
  • the partition ring extension 156 is equipped with a snap ring 19.
  • a second return spring 166 is mounted between the front surface of the second piston 160 and the partition wall connecting portion 154 to provide elastic force to the second piston 160.
  • the outer circumferential surface of the first piston 140 is in close contact with the inner circumferential surface of the first clutch housing protrusion 132, and the inner circumferential surface of the first piston 140 is in close contact with the outer circumferential surface of the partition extension part 156 so as to contact the first piston.
  • the first piston chamber 144 is formed between the rear surface of the 140 and the partition wall connecting portion 154.
  • a stopper 142 protruding radially outward is formed at the front end of the outer circumferential surface of the first piston 140 to limit the distance that the first piston 140 can move to the axial rear side.
  • the outer circumferential surface of the second piston 160 is in close contact with the inner circumferential surface of the partition mounting part 152, and the inner circumferential surface of the second piston 160 is in close contact with the outer circumferential surface of the second clutch housing protrusion 134 so that the second piston 160 is closed.
  • a second piston chamber 164 is formed between the rear surface of the actuator and the actuator housing 130.
  • the first piston 140 is operatively connected to the first application bearing 114 to move to the front in the axial direction by the operating hydraulic pressure supplied to the first piston chamber 144 and the first application bearing An axial force is applied to the 114.
  • An axial force is applied to the 114.
  • Sealing members 206 and 208 may be mounted between the outer circumferential surfaces of 156, respectively.
  • the second piston inner circumferential portion 162 extends in the axial front side and is operatively connected to the second application bearing 122. Therefore, the second piston 160 is moved forward in the axial direction by the hydraulic pressure supplied to the second piston chamber 164 to apply the axial force to the second application bearing 122.
  • the sealing members 210 and 211 may be mounted between the outer circumferential surfaces of the sealing members 210 and 211.
  • the outer circumferential surface D 2O of the second piston 160 is located radially outward from the inner circumferential surface D 1i of the first piston 140 through the shape of the partition wall 150 (see FIG. 3). Therefore, while independently controlling the operation of the first and second pistons 140 and 160 through the partition wall 150, the hydraulic actuation area (hydraulic area) of the first and second pistons 140 and 160 is increased to reduce the pressure. A large operating force can be obtained in space. This makes it possible to design an actuator that can achieve a compact and large operating force.
  • a first supply flow path 170 configured to supply operating hydraulic pressure to the first piston chamber 144 and a second supply flow path configured to supply operating hydraulic pressure to the second piston chamber 164. 172 is formed.
  • the first supply flow path 170 is in fluid communication with the first piston chamber 144, and the second supply flow path 172 is in fluid communication with the second piston chamber 164.
  • a cooling passage 174 is formed in the actuator housing 130 to supply oil for cooling and lubrication to the interior of the triple clutch 1.
  • the third actuator 15B further includes a third piston 180.
  • the third piston 180 is for providing axial force to the third pressure plate 194 through the third application bearing 192.
  • the third piston 180 is disposed in the radial space between the first and second protrusions 26 and 28 of the motor housing 21.
  • the rear surface of the third piston 180 extends radially inward to form a third piston extension 182, and a third accommodation portion of the third piston extension 182 and the third pressure plate 194. Between the 198, the third application bearing 192 is mounted.
  • the outer circumferential surface of the third piston 180 is in close contact with the inner circumferential surface of the first protrusion 26, and the inner circumferential surface of the third piston 180 is in close contact with the outer circumferential surface of the second protrusion 28 so that the front surface of the third piston 180 and the motor are close to each other.
  • a third piston chamber 184 is formed between the housing connecting portions 24.
  • Sealing members 202 and 204 are mounted between the outer circumferential surfaces, respectively.
  • a second support plate 188 is mounted on the rear surface of the first protrusion 26, and a third return spring 186 is mounted between the rear surface of the third piston 180 and the second support plate 188 to provide a third support plate 188. It provides elastic force to the piston 180.
  • a snap ring 14 is mounted to the first protrusion 26 to support the second support plate 188 in the axial direction.
  • a third supply flow passage 190 is formed inside the motor housing 21 to supply the hydraulic pressure to the third piston chamber 184, and the third supply flow passage 190 is formed in the third piston chamber 184. Fluidly communicates with
  • the third actuator 15B may be integrally formed with the motor housing 21 or may be manufactured separately and attached to the motor housing 21.
  • a third support bearing 216 is mounted between the second clutch housing stepped portion 52 and the rear end of the motor housing inner peripheral portion 30.
  • a snap ring 17 is mounted to the inner circumferential portion 30 of the motor housing.
  • the power of the crankshaft (or engine) is input directly to the input shaft 2 or after the torsional vibration is attenuated via the torsional damper 10.
  • the rotational power of the input shaft 2 is transmitted to the third actuating hub 108, but is not transmitted to the clutch housing 40 if the third clutch 13 is not operated.
  • the third pressure plate 194 moves to the left side in the drawing by the elastic force of the third separating spring 104.
  • the third piston 180 may be formed by the elastic force of the third separating spring 104 transmitted to the third piston 180 through the third application bearing 192 and the elastic force of the third return spring 186. Moves to the left in the figure. Accordingly, the discharge of the operating hydraulic pressure supplied to the third piston chamber 184 is smoothly performed, and the third clutch 13 is released. Accordingly, an operating mode (eg, electric vehicle mode) using only the power of the motor may be implemented.
  • the rotational power of the motor 20 is transmitted to the clutch housing 40 mounted on the rotor 34.
  • rotational power of the clutch housing 40 is also transmitted to the drum 72.
  • the first piston 140 moves to the left in the drawing and the first application bearing 114 is shown in the drawing. To the left.
  • the first pressure plate 110 is moved to the left side in the drawing by the first application bearing 114, and the drum 72 is pushed to the left in the drawing, so that the drum 72 has the first disc pack ( Axial force).
  • the first separate plate 60 and the first friction disk 62 are frictionally coupled, and the rotational power of the clutch housing 40 (ie, the input shaft 2 and / or the motor () through the first actuating hub 68). Rotational power of 20) is output to the first output shaft 4.
  • the drum 72 is moved axially to the left in the drawing, but since the second pressure plate 116 and the second friction disk 82 are splined to the drum 72, the second pressure plate ( 116 and the second friction disk 82 do not move in the axial direction.
  • the second separating spring 84 disposed between the neighboring second separator plates 80 maintains the gap between the second separator plates 80.
  • the second clutch 12 remains in a non-engaged state.
  • the second piston 160 is moved to the left in the drawing and the second application bearing 122 is left to the drawing. Will be pushed.
  • the second pressure plate 116 is moved axially to the left in the drawing by the second application bearing 122 and exerts an axial force on the second disk pack 86.
  • the second separate plate 80 and the second friction disk 82 are frictionally coupled, and the rotational power of the drum 72 via the second actuating hub 88 (ie, the input shaft 2 and / or the motor).
  • the rotational power of 20 is output to the second output shaft 6.
  • the axial force (force pushing to the left in the drawing) applied to the first clutch 11 is transmitted to the clutch housing 40 through the first support part 45, and this axial force is supported by the first support bearing 214. do.
  • the axial force (the pushing force to the left in the drawing) applied to the second clutch 12 is transmitted to the second actuating hub 88 through the second support 90, and is mounted to the second actuating hub extension 89. It is transmitted to and supported by the second support bearing 218 through the snap ring 18.
  • the axial force (force pushing to the right in the drawing) applied to the third clutch 13 is transmitted to the clutch housing 40 through the snap ring 23 mounted on the inner circumference 48 of the clutch housing, and this axial force is applied to the third clutch 13. It is supported by three support bearings 216. As such, by distributing three supporting bearings for supporting the axial force applied to the three clutches in the axial direction as much as possible, the stability and durability of the operation of the triple clutch 1 can be maximized.
  • FIG. 2 is a cross-sectional view of a triple clutch according to another embodiment of the present invention.
  • the triple clutch according to another embodiment of the present invention is substantially similar to the entirety of the triple clutch according to the embodiment of the present invention except for some components. Therefore, only some configurations that differ will be described.
  • a spline coupling between the second operation hub 88 and the second output shaft 6 and a snap ring 230 are disposed on the spline coupling portion.
  • the axial force applied to the two clutches 12 is transmitted to the second output shaft 6 through the snap ring 230.
  • a second support bearing 218 is mounted on the second output shaft 6 instead of the second actuating hub extension 89. That is, the second support bearing 218 is disposed between the outer circumferential surface of the second output shaft 6 and the inner circumferential surface of the rear end of the actuator housing 130 to support the axial force applied to the second clutch 12.
  • the second actuating hub extension 89 can be deleted, thereby implementing a triple clutch 1 having a simpler structure.
  • the triple clutch according to another embodiment of the present invention is the same as the triple clutch according to the embodiment of the present invention, description thereof will be omitted.
  • the first, second, and third clutches 11, 12, and 13 have the clutch housing 40, in particular the axial direction of the rotor 34 of the motor 20. Since it is arrange
  • At least a part of the first, second and third disc packs 66, 86 and 106 may be disposed in the space in the length L of the rotor 34 in the axial direction.
  • at least a part of the first, second, and third disk packs 66, 86, and 106 may include all, or first, components of the first, second, and third disk packs 66, 86, and 106.
  • it refers to a portion of the components that comprise the disc pack of the other one of two, three disc pack (66, 86, 106). That is, all or part of the components constituting the first disk pack 66, all or part of the components constituting the second disk pack 86, and components constituting the third disk pack 106.
  • the present invention is not limited to the above embodiments, and easily changed and equalized by those skilled in the art from the embodiments of the present invention. It includes all changes to the extent deemed acceptable.

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

Abstract

Un mode de réalisation de la présente invention concerne un triple embrayage comprenant : un arbre d'entrée permettant de recevoir la puissance de rotation d'un moteur ; un moteur électrique comprenant un carter de moteur électrique, un stator monté fixe sur la surface circonférentielle externe du carter de moteur électrique, et un rotor disposé rotatif à l'intérieur du rayon du stator ; un boîtier d'embrayage fonctionnellement relié au rotor, tournant conjointement avec le rotor et recevant la puissance rotative du moteur électrique, et comprenant un espace d'embrayage formé dans le carter d'embrayage ; un premier embrayage transférant sélectivement la puissance de rotation du carter d'embrayage à un premier arbre de sortie ; un deuxième embrayage transférant sélectivement la puissance de rotation du carter d'embrayage à un second arbre de sortie ; et un troisième embrayage transférant sélectivement la puissance de rotation de l'arbre d'entrée au carter d'embrayage, les premier, deuxième et troisième embrayages pouvant tous être disposés à l'intérieur de l'espace d'embrayage.
PCT/KR2017/012841 2016-11-15 2017-11-14 Triple embrayage et actionneur correspondant WO2018093108A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US16/332,486 US20210277958A1 (en) 2016-11-15 2017-11-14 Triple clutch and actuator thereof
CN201780062073.5A CN109790880B (zh) 2016-11-15 2017-11-14 三重离合器及其致动器
EP17870970.5A EP3543556B1 (fr) 2016-11-15 2017-11-14 Triple embrayage et actionneur correspondant

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
KR20160151653 2016-11-15
KR10-2016-0151653 2016-11-15
KR1020170151219A KR101940043B1 (ko) 2016-11-15 2017-11-14 트리플 클러치 및 그 액츄에이터
KR10-2017-0151219 2017-11-14

Publications (1)

Publication Number Publication Date
WO2018093108A1 true WO2018093108A1 (fr) 2018-05-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2017/012841 WO2018093108A1 (fr) 2016-11-15 2017-11-14 Triple embrayage et actionneur correspondant

Country Status (1)

Country Link
WO (1) WO2018093108A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112334348A (zh) * 2018-06-05 2021-02-05 法雷奥离合器公司 用于混合动力车辆的传动装置
CN113015860A (zh) * 2018-11-12 2021-06-22 戴姆勒股份公司 混动双离合变速器
US20220055472A1 (en) * 2019-02-25 2022-02-24 Texa Dynamics S.R.L. Electric motor and clutch
US11541861B2 (en) 2019-04-30 2023-01-03 Borgwarner Inc. Transmission system for use in a vehicle

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KR20050115639A (ko) * 2004-06-04 2005-12-08 현대자동차주식회사 하이브리드 전기 자동차용 듀얼 클러치 변속기 및 모드별제어방법
US20070214903A1 (en) * 2006-03-16 2007-09-20 Magna Powertrain Usa, Inc. Three Clutch Powershift Transmission
JP2009107388A (ja) * 2007-10-26 2009-05-21 Aisin Aw Co Ltd ハイブリッド駆動装置
JP5195513B2 (ja) * 2009-02-27 2013-05-08 日産自動車株式会社 車両のクラッチユニット
KR20160035326A (ko) * 2014-09-23 2016-03-31 현대자동차주식회사 하이브리드 차량용 변속장치
KR20160073234A (ko) * 2014-12-16 2016-06-24 현대자동차주식회사 하이브리드 차량용 구동장치

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KR20050115639A (ko) * 2004-06-04 2005-12-08 현대자동차주식회사 하이브리드 전기 자동차용 듀얼 클러치 변속기 및 모드별제어방법
US20070214903A1 (en) * 2006-03-16 2007-09-20 Magna Powertrain Usa, Inc. Three Clutch Powershift Transmission
JP2009107388A (ja) * 2007-10-26 2009-05-21 Aisin Aw Co Ltd ハイブリッド駆動装置
JP5195513B2 (ja) * 2009-02-27 2013-05-08 日産自動車株式会社 車両のクラッチユニット
KR20160035326A (ko) * 2014-09-23 2016-03-31 현대자동차주식회사 하이브리드 차량용 변속장치
KR20160073234A (ko) * 2014-12-16 2016-06-24 현대자동차주식회사 하이브리드 차량용 구동장치

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112334348A (zh) * 2018-06-05 2021-02-05 法雷奥离合器公司 用于混合动力车辆的传动装置
CN113015860A (zh) * 2018-11-12 2021-06-22 戴姆勒股份公司 混动双离合变速器
US20220055472A1 (en) * 2019-02-25 2022-02-24 Texa Dynamics S.R.L. Electric motor and clutch
US11541861B2 (en) 2019-04-30 2023-01-03 Borgwarner Inc. Transmission system for use in a vehicle

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