WO2011037023A1 - Dispositif d'entraînement à moteur électrique pour véhicule - Google Patents

Dispositif d'entraînement à moteur électrique pour véhicule Download PDF

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Publication number
WO2011037023A1
WO2011037023A1 PCT/JP2010/065538 JP2010065538W WO2011037023A1 WO 2011037023 A1 WO2011037023 A1 WO 2011037023A1 JP 2010065538 W JP2010065538 W JP 2010065538W WO 2011037023 A1 WO2011037023 A1 WO 2011037023A1
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WO
WIPO (PCT)
Prior art keywords
shaft
electric motor
clutch
rotor
drive device
Prior art date
Application number
PCT/JP2010/065538
Other languages
English (en)
Japanese (ja)
Inventor
安井　誠
雪島　良
Original Assignee
Ntn株式会社
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Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2011037023A1 publication Critical patent/WO2011037023A1/fr

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    • 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
    • F16D28/00—Electrically-actuated clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
    • B60W10/00—Conjoint control of vehicle sub-units of different type or different function
    • B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
    • B60W10/11—Stepped gearings
    • B60W10/113—Stepped gearings with two input flow paths, e.g. double clutch transmission selection of one of the torque flow paths by the corresponding input clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • 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
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • 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
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/108—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members
    • F16D27/112—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members with flat friction surfaces, e.g. discs
    • 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
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/12—Clutch systems with a plurality of electro-magnetically-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H25/24—Elements essential to such mechanisms, e.g. screws, nuts
    • F16H25/2454—Brakes; Rotational locks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/42—Clutches or brakes
    • B60Y2400/428—Double clutch arrangements; Dual clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0607—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate
    • F16D2021/0615—Double clutch with torque input plate in-between the two clutches, i.e. having a central input plate the central input plate is supported by bearings in-between the two clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F16D2021/0646—Electrically actuated clutch with two clutch plates
    • 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
    • F16D2021/0684—Mechanically actuated clutches with two clutch plates
    • 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
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms
    • 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
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/20—Screw mechanisms
    • F16H2025/2062—Arrangements for driving the actuator
    • F16H2025/2075—Coaxial drive motors
    • F16H2025/2078—Coaxial drive motors the rotor being integrated with the nut or screw body
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • 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

Definitions

  • the present invention relates to a vehicle electric motor drive device that uses an electric motor as a drive source and decelerates the output of the electric motor to transmit it to wheels.
  • Patent Document 1 As a vehicle electric motor drive device used for a drive device of an electric vehicle and a hybrid vehicle, one described in Patent Document 1 has been known.
  • a first shaft and a second shaft rotated by an electric motor are arranged in parallel, and a first gear is provided on the first shaft.
  • a second gear meshing with the first gear is rotatably provided on the second shaft, and a first clutch is provided between the second gear and the second shaft.
  • a third gear having a larger diameter than the first gear is rotatably provided on the first shaft, and a fourth gear meshing with the third gear is provided on the second shaft so as not to rotate.
  • the second clutch is incorporated between the gear 3 and the first shaft, and the operation of the second clutch and the first clutch selectively switches the torque transmission path to reduce the rotation of the first shaft. Then, the signal is transmitted to the second shaft and output from the second shaft to the differential gear.
  • a 2-way overrunning clutch is adopted as the first clutch
  • a multi-plate friction clutch is adopted as the second clutch.
  • the first clutch is incorporated between the second shaft and the second gear
  • the second clutch is incorporated between the first shaft and the third gear. Therefore, there has been a problem that the electric motor driving device is enlarged and a large space must be secured for incorporation into the vehicle.
  • An object of the present invention is to reduce the size of an electric motor driving device for a vehicle so that a torque transmission path can be switched smoothly.
  • an electric motor a speed reduction unit that decelerates rotation output from the electric motor and transmits it to the wheel side, and an output from the electric motor is transmitted to the speed reduction unit.
  • an interrupting portion that cuts off, and the speed reduction portion includes a cylindrical outer rotating shaft disposed coaxially with the output shaft of the electric motor, and an inner rotating shaft inserted into the outer rotating shaft.
  • a first friction clutch that fastens the output shaft of the motor and the inner rotating shaft, and is engaged by a load of a pressing force that is also directed in the axial direction of the first shaft to connect the output shaft of the electric motor and the outer rotating shaft.
  • a first shift actuator for applying an axial pressing force to the first friction clutch, and a second shift actuator for applying an axial pressing force to the second friction clutch Each includes a motor, a rotor that is driven by the motor and rotates in the case, and a direct-acting actuator that is screw-engaged with the rotor and moves in the axial direction by the rotation of the rotor. Therefore, the first shift actuator and the second shift actuator are prevented from moving backward by the reaction force from the friction clutch side. Than it is adopted the configuration in which the position holding means for.
  • the first shaft has a two-shaft structure in which the inner rotation shaft is inserted inside the cylindrical outer rotation shaft, so that the first friction clutch and the second friction clutch are placed on the first shaft.
  • the friction clutch can be disposed opposite to the axial direction, and the electric motor drive device can be downsized.
  • friction clutches as clutches that connect the output shaft of the electric motor and the inner rotating shaft and clutches that connect the output shaft of the electric motor and the outer rotating shaft
  • each friction clutch is slipping while the input side The member and the output side member are coupled.
  • the friction clutch is coupled while synchronizing the input side member and the output side member, and smoothly switching between the low speed region and the high speed region by switching between the first friction clutch and the second friction clutch.
  • an elastic member is provided for each of the pressurizing system for applying the pressing force from the first shift actuator to the first friction clutch and the pressurizing system for applying the pressing force from the second shift actuator to the second friction clutch.
  • the first shift actuator that loads the first friction clutch with an axial pressing force and the second shift actuator that loads the second friction clutch with an axial pressing force are respectively supplied from the friction clutch side.
  • the rotor By providing a position holding means for preventing the rotor from rotating in the direction in which the presser moves backward due to the reaction force, the rotor is rotated by driving the motor, and the first friction clutch is driven by the forward movement of the presser;
  • the second friction clutch is engaged, the rotor can be prevented from rotating by the reaction force from the friction clutch side, and the pressing element can be stopped and held at the forward position. For this reason, even if it cuts off electricity with respect to a motor, the 1st friction clutch or the 2nd friction clutch can be held in an engagement state, and consumption of energy can be reduced.
  • the outer plate is incorporated in the case, is prevented from rotating in the case, and is movable in the axial direction, and is prevented from being rotated by the rotor, and is movable in the axial direction.
  • the inner plate and an elastic member that elastically contacts both the plates, and the rotor rotates in the direction in which the presser moves backward using the frictional resistance acting on the contact portion between the outer plate and the inner plate as a rotational resistance. It is possible to adopt one designed to prevent this from happening.
  • a one-way clutch that releases the coupling between the rotor and the inner plate when the rotor rotates between the inner plate and the rotor in the direction in which the presser advances. If it is installed, when the rotor is rotated in the direction in which the pusher advances by driving the motor, the one-way clutch will idle, and the frictional resistance acting on the contact portion between the outer plate and the inner plate will be the rotational resistance of the motor. Therefore, the motor can be rotated smoothly, and a small motor can be employed.
  • the rotation from the motor is transmitted to the rotor, and when the rotational force is applied from the presser to the rotor, the rotor and the case are coupled to lock the rotor.
  • a reverse input blocking type two-way clutch can be employed.
  • the first shaft has a double shaft structure in which the inner rotation shaft is inserted inside the cylindrical outer rotation shaft, and the inner rotation shaft and the output shaft of the electric motor are connected to each other. Since the first friction clutch and the second friction clutch that connects the outer rotating shaft and the output shaft of the electric motor are arranged on the first shaft, the electric motor drive device can be reduced in size.
  • the friction clutch is used to fasten the output shaft and the inner rotating shaft of the electric motor and the output shaft and the outer rotating shaft of the electric motor, so that each friction clutch is coupled while synchronizing the input side and the output side. Therefore, it is possible to smoothly switch between the low speed region and the high speed region by switching between the first friction clutch and the second friction clutch.
  • first shift actuator that loads the first friction clutch with an axial pressing force and the second shift actuator that loads the second friction clutch with an axial pressing force are respectively supplied from the friction clutch side.
  • position holding means for preventing the rotor from rotating in the direction in which the pressing element moves backward due to the reaction force By providing position holding means for preventing the rotor from rotating in the direction in which the pressing element moves backward due to the reaction force, the first shift actuator and the second shift actuator are moved at the position where each friction clutch is operated. Can be held. At that time, since power supply to the motor can be cut off, energy consumption can be reduced.
  • Sectional drawing which shows embodiment of the electric motor drive device for vehicles which concerns on this invention Sectional drawing which expands and shows the intermittent part and deceleration part of FIG. Sectional drawing which shows the actuator for shift of a gear change actuator Sectional drawing which shows the other example of the actuator for a shift Sectional drawing which shows the further another example of the actuator for a shift Sectional drawing which shows the further another example of the actuator for a shift Sectional drawing which shows the further another example of the actuator for a shift Sectional view along line VIII-VIII in FIG.
  • Sectional drawing which shows the example using the reverse input interruption
  • an electric motor driving apparatus 1 for a vehicle includes an electric motor 11, a speed reducing unit A that decelerates an output from the electric motor 11, and an output of the electric motor 11 that is a speed reducing unit A. And an intermittent portion B which is intermittently connected.
  • the electric motor 11 includes a motor casing 12, a stator 13 fixed to the inner periphery of the motor casing 12, a rotor 14 incorporated inside the stator 13, and rotated by energization of the stator 13, The output shaft 15 is inserted into the central portion and rotates integrally with the rotor 14.
  • the motor casing 12 is connected to one side surface of the housing 21 of the speed reduction part A and the intermittent part B.
  • a flanged joint shaft 16 is connected to the shaft end portion of the output shaft 15 of the electric motor 11, and the joint shaft 16 is disposed inside the housing 21 and is rotatable in the housing 21.
  • the housing 21 is provided with a reduction gear housing portion 22 and a clutch housing portion 23 at a position offset from the reduction gear housing portion 22 toward the electric motor 11 side.
  • the speed reducer A is composed of a parallel shaft constantly meshing gear speed reducer, and has a first shaft 31 and a second shaft 32 arranged in parallel to the first shaft 31.
  • the first shaft 31 has a biaxial structure of a cylindrical outer rotating shaft 31 a and an inner rotating shaft 31 b inserted inside the outer rotating shaft 31 a.
  • the output shaft 15 is coaxially arranged.
  • Each of the outer rotating shaft 31a and the inner rotating shaft 31b passes through the partition wall 24 of the speed reducer housing portion 22 and the clutch housing portion 23, and the outer rotating shaft 31a is rotatably supported by a bearing 33 provided in the penetrating portion. ing.
  • the inner rotary shaft 31b is longer than the outer rotary shaft 31a, both end portions thereof are located outside the outer rotary shaft 31a, and one end portion located in the reducer housing portion 22 A bearing 34 attached to the end wall is rotatably supported.
  • the other end portion of the inner rotary shaft 31 b is disposed in a bearing hole 17 formed on the shaft end surface of the joint shaft 16, and is rotatably supported by a bearing 35 incorporated in the bearing hole 17.
  • a first reduction gear train 36 is provided between the inner rotary shaft 31b and the second shaft 32, and a first reduction gear is provided between the outer rotary shaft 31a and the second shaft 32.
  • a second reduction gear train 37 having a reduction ratio smaller than that of the train 36 is provided.
  • a first input gear 36a is provided on the inner rotary shaft 31b, and a first output gear 36b that meshes with the first input gear 36a is provided on the second shaft 32.
  • a second input gear 37a is provided on the outer rotating shaft 31a, and a second output gear 37b meshing with the second input gear 37a is provided on the second shaft 32.
  • the second shaft 32 is provided with an output gear 38 that transmits the rotation of the second shaft 32 to a differential gear 40 incorporated in the reduction gear housing 22.
  • the differential gear 40 includes a ring gear 42 that meshes with the output gear 38 in a differential case 41 that is rotatably supported by the housing 21, and a pinion shaft 43 that has both ends rotatably supported by the differential case 41.
  • a pair of pinions 44 are attached, and a pair of side gears 45 is engaged with each of the pair of pinions 44, and an axle 46 is connected to each of the pair of side gears 45.
  • the intermittent portion B includes a first friction clutch 51 that fastens the output shaft 15 of the electric motor 11 and the inner rotary shaft 31b, and a second friction clutch 52 that fastens the output shaft 15 and the outer rotary shaft 31a.
  • the first friction clutch 51 and the second friction clutch 52 are incorporated in the clutch housing portion 23.
  • the first friction clutch 51 has a clutch housing 53 fixed to the flange 16 a of the joint shaft 16 connected to the output shaft 15 of the electric motor 11, and an outer peripheral portion is connected to the clutch housing 53.
  • the drive disk 54 that rotates integrally with the clutch housing 53 is rotatably supported by a bearing 55 fitted to the other end of the outer rotary shaft 31a.
  • a friction plate 56 is disposed oppositely, and the first friction plate 56 and a disk 57 attached to the other end of the inner rotary shaft 31b are connected via an elastic plate 58, and the first friction plate 56 and the drive disk 54 are connected.
  • the output shaft 15 and the inner rotary shaft 31b are fastened by contact with each other.
  • the second friction clutch 52 has an annular second friction plate 59 disposed opposite to the other side of the drive disk 54 in the axial direction, and is attached to the second friction plate 59 and the other end of the outer rotating shaft 31a.
  • the disc 60 is connected via an elastic plate 61, and the output shaft 15 and the outer rotary shaft 31a are fastened by contact between the second friction plate 59 and the drive disc 54.
  • the engagement and disengagement of the first friction clutch 51 are controlled by the first shift switching actuator 61.
  • the second friction clutch 52 is controlled to be engaged and disengaged by the second shift switching actuator 71.
  • the first shift switching actuator 61 fixes a guide cylinder 62 disposed coaxially with the first shaft 31 to the partition wall 24 and is slidably fitted to the outside of the guide cylinder 62.
  • An inner peripheral portion of an elastic member 65 formed of an annular disc spring is connected to one end portion of the combined first sleeve 63 via a bearing 64, and the radial center portion of the elastic member 65 is connected to the side surface of the clutch housing 53.
  • the outer peripheral portion is in contact with the provided annular projecting portion 66 and is connected to the outer peripheral portion of the first pressure disk 67 that is incorporated in the clutch housing 53 and faces the first friction plate 56 in the axial direction.
  • One end of a lever 68 is connected to the other end of the sleeve 63, the middle of the lever 68 is rotatably supported by a pin 69, and the other end of the lever 68 is removed from an opening 70 formed in the housing 21. It is located, and the first shift actuator X 1 to the other end of the lever 68 is configured to have opposed.
  • the first sleeve 63 that moves along the guide cylinder 62 by swinging the lever 68 around the pin 69 by the operation of the first shift actuator X 1 is provided in the elastic member 65.
  • the elastic member 65 is elastically deformed in a curved shape with the annular protruding portion 66 as a fulcrum, and the first pressure disk 67 is moved toward the drive disk 54 by the elastic force of the elastic member 65.
  • the first friction plate 56 is pressed against the drive disk 54.
  • the second shift switching actuator 71 has an inner peripheral portion of an elastic member 75 formed of an annular disc spring through a bearing 74 at one end portion of a second sleeve 73 slidably fitted inside the guide tube 62.
  • the outer peripheral portion of the elastic member 75 is connected to the outer peripheral portion of the second pressure disk 77 which is incorporated in the clutch housing 53 and faces the second friction plate 59 in the axial direction.
  • One end of a lever 78 is connected to the part, the middle of the lever 78 is rotatably supported by a pin 79, and the other end of the lever 78 is positioned outside through an opening 80 formed in the housing 21, It has a configuration in which the second shift actuator X 2 disposed opposite to the other end of the lever 78.
  • Figure 3 shows the actuator X 1 for the first shift.
  • the first shift actuator X 1 is disposed in the case 81 by connecting a shift motor 82 to a cylindrical case 81 supported on the outer periphery of the housing 21, and connected to a rotating shaft 83 of the motor 82.
  • the rotor 84 is rotatably supported by a bearing 85 incorporated in the case 81, and a female screw 86 is provided on the inner periphery of a cylindrical portion 84 a provided on the rotor 84, and the female screw 86 is provided on the outer periphery of the presser 87.
  • the formed male screw 88 is screw-engaged, and the presser 87 is moved in the axial direction by the rotation of the rotor 84.
  • a female screw 86 provided in the rotor 84 has formed the male thread 88 on the pushing element 87, as shown in FIG. 4, a male screw 88 provided in the rotor 84, An internal thread 86 may be formed on the inner periphery of the cylindrical portion 87 a formed on the pressing element 87.
  • each of the female screw 86 and the male screw 88 is a triangular screw or a trapezoidal screw.
  • the mating surfaces of the rotor 84 and the presser 87 are respectively shown.
  • a ball screw 89 in which a thread groove is formed and a ball is incorporated between the thread grooves may be used.
  • the lead angles of the female screw 86 and the male screw 88 are set to such a size that the pusher 87 is not pushed even when a static push load is applied to the pusher 87.
  • the position holding means 90 has a plurality of inner plates 92 as friction plates arranged alternately in the axial direction in the case 81 as well as a plurality of outer plates 91 as friction plates, and the outer plates 91 are attached to the case 81 by splines 93.
  • the inner plate 92 is prevented from rotating on the rotor 84 by the spline 94 and is movable in the axial direction, and both plates 91 and 92 are connected to the end of the case 81.
  • the rotor 84 rotates in a direction in which the pressing element 87 moves backward using the frictional resistance acting on the contact portion between the outer plate 91 and the inner plate 92 as a rotational resistance by elastic contact between the elastic members 95 incorporated between the plates. I try to prevent that.
  • FIG. 2 shows a state in which the first friction clutch 51 and the second friction clutch 52 are in the disengagement position.
  • the lever 68 swings around the pin 69, and the first sleeve 63 moves along the guide cylinder 62 in a direction away from the partition wall 24, thereby pressing the inner peripheral portion of the elastic member 65.
  • the elastic member 65 is elastically deformed so as to bend around the annular protrusion 66, and the first pressure disk 67 moves toward the drive disk 54 due to the elastic deformation, and the first friction clutch 51 has the first friction clutch 51.
  • the friction plate 56 is pressed against the drive disk 54 and frictionally engaged, and the first friction clutch 51 is engaged.
  • the output shaft 15 of the electric motor 11 and the inner rotating shaft 31b of the first shaft 31 are fastened, and the rotation of the output shaft 15 is transmitted to the inner rotating shaft 31b to rotate inward.
  • the shaft 31b rotates.
  • the rotation of the inner rotary shaft 31b is decelerated by the first reduction gear train 36 and transmitted to the second shaft 32.
  • the rotation of the second shaft 32 is transmitted to the differential gear 40 and the axle 46 rotates.
  • the vehicle travels at a low speed by being transmitted from the axle 46 to wheels (not shown).
  • the first friction clutch 51 when it is engaged, pushing force is loaded to the first shift actuator X 1 of the pushing element 87 by a reaction force or the like from the elastic member 65.
  • the rotor 84 is loaded with a rotational resistance by a frictional resistance acting on a contact portion between the outer plate 91 and the inner plate 92, and the female screw 86 and the male screw 88 are rotated by a load of a static pushing load. Since the lead angle is provided without any pressure, the pressing element 87 is reliably held at the operating position moved forward even if a dynamic vibration or the like is applied.
  • the first shift actuator X 1 of the motor 82 of the first gear shifting actuator 61 is rotated in the direction opposite the above, at the same time, the second gear shifting actuator 71 first 2 drives the shift actuator X 2 of the motor 82.
  • the first sleeve 63 moves toward the partition wall 24 to release the pressing of the elastic member 65, and the elastic member 65 is restored in shape as shown in FIG. For this reason, the first pressure disk 67 releases the pressure of the first friction plate 56, and the first friction clutch 51 is disengaged.
  • the lever 78 swings around the pin 79, the second sleeve 73 moves along the guide cylinder 62 in the direction away from the partition wall 24, and presses the inner peripheral portion of the elastic member 75.
  • the pressure disk 77 is moved toward the drive disk 54 by pressing from the elastic member 75, and the second friction plate 59 of the second friction clutch 52 is pressed against the drive disk 54 to be frictionally engaged, so that the second friction clutch 52 is engaged. Is engaged.
  • the rotation of the outer rotating shaft 31a is decelerated by the second reduction gear train 37 and transmitted to the second shaft 32.
  • the rotation of the second shaft 32 is transmitted to the differential gear 40 and the axle 46 rotates.
  • the vehicle is accelerated from the axle 46 and transmitted to wheels (not shown).
  • the first shaft 31 has a biaxial structure in which an inner rotary shaft 31b is inserted inside a cylindrical outer rotary shaft 31a, and the first shaft 31 is placed on the first shaft 31. Since two friction clutches, the first friction clutch 51 and the second friction clutch 52, are disposed, the clutch is disposed on each of the first shaft and the second shaft as in the conventional electric motor driving device described above. Compared to the above, it is possible to reduce the size of the electric motor drive device.
  • the friction clutches 51 and 52 as a clutch that couples the output shaft 15 of the electric motor 11 and the inner rotating shaft 31b and a clutch that couples the output shaft 15 of the electric motor 11 and the outer rotating shaft 31a,
  • the friction clutches 51 and 52 couple the output shaft 15 of the electric motor 11 to the inner rotating shaft 31b and the outer rotating shaft 31a while causing slippage.
  • the first friction clutch 51 is coupled while synchronizing the output shaft 15 and the inner rotation shaft 31b
  • the second friction clutch 52 is coupled while synchronizing the output shaft 15 and the outer rotation shaft 31a.
  • the axial displacements of the first sleeve 63 and the second sleeve 73 are obtained by incorporating elastic members 65 and 75 into the pressurizing system of the first shift switching actuator 61 and the second shift switching actuator 71. Even if changes slightly, the variation in the displacement amount can be absorbed by the elastic deformation of the elastic members 65 and 75. Therefore, a gentle pressing force can be applied to the first pressure disk 67 and the second pressure disk 77, and even if the first friction plate 56 and the second friction plate 59 are worn, the synchronization function is stabilized. Can be achieved.
  • the first respective shift actuator X 1 and the second shift actuator X 2 a motor 82, a rotor 84 rotated by the motor 82, the rotor 84.
  • a linear actuator that includes a pusher 87 that is screw-engaged with 84 and moves in the axial direction by the rotation of the rotor 84, the current control for the motor 82 and the lead of the screw are achieved. Since the fine axial displacement and load can be controlled, the synchronization function of the first friction clutch 51 and the second friction clutch 52 can be made smooth, and the shock at the time of switching can be further suppressed.
  • the holding means 90 is provided to prevent the rotor 84 from rotating in the direction in which the pressing element 87 moves backward due to the reaction force from the elastic members 65, 75, etc.
  • the energization to the motor 82 can be immediately cut off, thereby reducing energy consumption. Can do.
  • FIG. 7 and 8 showing still another example of the first shift actuator X 1.
  • This example is different from the first shift actuator X 1 shown in FIG. 5 in that a one-way clutch 96 is incorporated between the rotor 84 and the inner plate 92. Therefore, the first actuator X 1 same components and shift shown in FIG. 5, its description is omitted with the same reference numerals.
  • the one-way clutch 96 is provided with a plurality of cam surfaces 99 that form wedge spaces between the inner surface of the clutch outer ring 97 and the cylindrical outer surface 98 of the rotor 84 at intervals in the circumferential direction. 99 and a cylindrical one-way clutch incorporating a roller 100 between the cylindrical outer surface 98, the clutch outer ring 97 and the inner plate 92 are fitted by the spline 101, and the inner plate 92 is prevented from rotating around the clutch outer ring 97; It is movable in the axial direction.
  • the one-way clutch 96 releases the coupling between the rotor 84 and the inner plate 92 when the rotor 84 rotates in the direction in which the pressing element 87 advances.
  • the one-way clutch 96 that releases the coupling between the rotor 84 and the inner plate 92 is incorporated, the one-way clutch is used when the rotor 84 is rotated in the direction in which the pusher 87 moves forward by driving the motor 82. Since 96 releases the coupling between the rotor 84 and the inner plate 92, the frictional resistance acting on the contact portion between the outer plate 91 and the inner plate 92 does not become the rotational resistance of the motor 82, and the motor 82 can be smoothly rotated. And a small motor can be employed.
  • a sprag type one-way clutch may be employed instead of the roller type one-way clutch 96.
  • the position holding means 90 shown in FIGS. 9 and 10 transmits the rotation from the motor 82 to the rotor 84, and when a rotational force is applied from the presser 87 to the rotor 84, the rotor 84 and the case 81 are transmitted. And a reverse input blocking type two-way clutch 110 that locks the rotor 84.
  • the above-described two-way clutch 110 is provided with a cylindrical surface 112 on the inner periphery of the clutch outer ring 111 fixed to the inner peripheral surface of the case 81, and is incorporated inside the clutch outer ring 111 and is prevented from rotating around the rotor 84.
  • a plurality of cam surfaces 114 are formed on the outer periphery of 113 to form a wedge space with narrow ends in the circumferential direction between the cylindrical surface 112 and are connected to the rotating shaft 83 of the motor 82 to be clutched.
  • a pocket 116 is formed at a position facing each cam surface 114 in a cage 115 that rotates between opposing portions of the outer ring 111 and the clutch inner ring 113, and a roller 117 is incorporated in the pocket 116.
  • the roller 113 type is provided with engaging means 120 in the rotational direction between 113.
  • the engaging means 120 is formed in an end plate 113 a provided in the clutch inner ring 113 with an arc-shaped long hole 121 centering on the axis of the clutch inner ring 113, and the retainer 115 has an end plate of the clutch inner ring 113.
  • An end plate 115a that is axially opposed to 113a is provided, and a pin 122 disposed in the elongated hole 121 is projected from the end plate 115a, and between the end surfaces of the pin 122 and the elongated hole 121 that are opposed in the circumferential direction.
  • a play 123 in the rotation direction is provided.
  • the magnitude of the rotational direction of play 123 between the opposed end faces in the circumferential direction of the pin 122 and the elongated hole 121 and L 1, in a neutral position where the roller 117 is disposed in the wider portion of the wedge spaces, the roller 117 when the size of the circumferential direction of the pocket clearance 124 between the opposed end faces in the circumferential direction of the pocket 116 and the L 2 and playing 123 the rotational direction, it is dimensioned so that the relation of L 1 ⁇ L 2 is satisfied Yes.
  • the retainer 115 when the retainer 115 is rotated in the direction indicated by the arrow in FIG. 10I by driving the motor 82, the retainer 115 is interposed between the end surface of the long hole 121 and the pin 122. As shown in FIG. 10 (II), the pocket 116 rotates relative to the clutch inner ring 113 by an amount corresponding to the formed play 123 in the rotational direction, and contacts one end surface of the pocket 116 against the roller 117 held in the neutral position. Touch.
  • the pins 122 forming the engaging means 120 are in contact with or close to the end face of the long hole 121.
  • the motor 82 is driven to rotate the retainer 115 in the direction indicated by the arrow in FIG. Since the end surface of the pocket 116 presses the roller 117 by the rotation of the retainer 115, the roller 117 is disengaged, and when the roller 117 is returned to the neutral position, the pin 122 presses the end surface of the long hole 121.
  • the clutch inner ring 113 and the rotor 84 rotate in the same direction as the retainer 115 by the pressing, and the pressing element 87 moves backward by the screw engagement of the female screw 86 and the male screw 88.
  • the clutch inner ring 113 is provided with the long hole 121 and the cage 115 is provided with the pin 122, but the clutch inner ring 113 is provided with the pin and the cage 115 is provided with the long hole. You may do it.
  • the clutch outer ring 111 is provided with the cylindrical surface 112 and the clutch inner ring 113 is formed with the cam surface 114, but the clutch outer ring 111 is provided with a cam surface on the inner periphery thereof.
  • a cylindrical surface may be formed on the outer periphery of the inner ring 113.
  • one roller 117 is incorporated in the pocket 116 of the retainer 115.
  • a roller 117 may be incorporated, and an elastic member 118 may be incorporated between the rollers 117 so that each of the rollers 117 is urged in a direction to engage with the cylindrical surface 112 and the cam surface 114.
  • the pin 122 rotates within the range of the play 123 in the rotation direction formed between the end faces of the long hole 121, the rotation direction of the cage 115 out of the two rollers 117 incorporated in the pocket 116.
  • the roller 117 positioned on the subsequent side is pressed and moved to the neutral position on the end surface of the pocket 116.
  • a sprag type two-way clutch may be used instead of the roller type two-way clutch 110.
  • a Deceleration part B Intermittent part X 1 First shift actuator X 2 Second shift actuator 11 Electric motor 15 Output shaft 21 Housing 31 First shaft 31a Outer rotation shaft 31b Inner rotation shaft 32 Second shaft 36 First reduction gear train 37 Second reduction gear train 51 First friction clutch 52 Second friction clutch 65 Elastic member 75 Elastic member 81 Case 82 Motor 84 Rotor 84a Tube portion 86 Female screw 87 Presser 87a Tube portion 88 Male screw 89 Ball screw 90 Position holding means 91 Outer plate 92 Inner plate 95 Elastic member 96 One-way clutch 110 Two-way clutch 111 Clutch outer ring 112 Cylindrical surface 113 Clutch inner ring 114 Cam surface 115 Cage 116 Pocket 117 Roller 118 Elastic member 120 Engaging means 121 Long hole 1 2 Pin 123 rotational direction play 124 pocket clearance

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Transmission Devices (AREA)
  • Structure Of Transmissions (AREA)
  • Gear-Shifting Mechanisms (AREA)

Abstract

Dispositif d'entraînement à moteur électrique d'encombrement réduit, assurant un passage en douceur entre les rapports de couple. Un premier arbre (31) est monté co-axialement avec l'arbre de sortie (15) d'un moteur électrique (11) et un second arbre (32) est monté parallèlement au premier arbre (31). Le premier arbre (31) est constitué d'un arbre extérieur (31a) et d'un arbre intérieur (31b) logé dans l'arbre extérieur (31a). Un premier train d'engrenage de réduction (36) est disposé entre l'arbre intérieur (31b) et le second arbre (32), et un second train d'engrenage de réduction (37) ayant un rapport de réduction plus faible que le premier train d'engrenage (36) est disposé entre l'arbre extérieur (31a) et le second arbre (32). Un premier embrayage à friction (51) reliant l'arbre de sortie (15) à l'arbre intérieur (31b) par le biais d'un actionneur (X2) four le premier rapport et un second embrayage à friction (52) reliant l'arbre de sortie (15) et l'arbre extérieur (31a) par le biais d'un second actionneur (X2) pour le second rapport sont disposés sur le premier arbre (31), ce qui réduit l'encombrement du dispositif d'entraînement et autorise des passage en douceur entre les rapports de couple. L'actionneur (X1) pour le premier passage et l'actionneur (X2) pour le second passage sont dotés chacun de moyens de blocage de position (90) empêchant les éléments de serrage (87) qui serrent les embrayages de friction (51, 52) d'être repoussés vers l'arrière par les forces de réaction provenant desdits embrayages de friction.
PCT/JP2010/065538 2009-09-28 2010-09-09 Dispositif d'entraînement à moteur électrique pour véhicule WO2011037023A1 (fr)

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JP2009222747 2009-09-28
JP2009-222747 2009-09-28
JP2009267501A JP2011089632A (ja) 2009-09-28 2009-11-25 車両用電動モータ駆動装置
JP2009-267501 2009-11-25

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Cited By (8)

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CN104613136A (zh) * 2015-01-30 2015-05-13 陕西东铭车辆系统股份有限公司 带电磁双向离合器的两挡位变速电动车后桥减速器总成
WO2015169710A1 (fr) * 2014-05-06 2015-11-12 Ntn-Snr Roulements Actionneur électromécanique à vis à billes pour un embrayage
FR3020846A1 (fr) * 2014-05-06 2015-11-13 Ntn Snr Roulements Actionneur electromecanique a vis a billes pour un embrayage
WO2016001147A1 (fr) * 2014-07-02 2016-01-07 Stabilus Gmbh Ensemble d'entraînement et commande à clapets
CN105745421A (zh) * 2013-12-10 2016-07-06 丰田自动车株式会社 内燃机
CN110778673A (zh) * 2019-09-12 2020-02-11 浙江捷昌线性驱动科技股份有限公司 一种线性致动器的自锁装置和线性致动器
CN111016640A (zh) * 2019-12-31 2020-04-17 西南大学 超大载荷的紧凑型中央驱动式自适应电驱动总成
EP3833841B1 (fr) * 2018-08-08 2023-10-25 D+H Mechatronic AG Mécanisme d'entraînement à arbre ayant un dispositif automatique de blocage

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KR101274353B1 (ko) 2012-03-06 2013-06-13 주식회사 센트랄 클러치 디스크와 그 제조방법
JP5924140B2 (ja) * 2012-06-05 2016-05-25 日本精工株式会社 電気自動車用駆動装置
JP5737302B2 (ja) 2013-01-16 2015-06-17 トヨタ自動車株式会社 内燃機関
JP6028640B2 (ja) * 2013-03-21 2016-11-16 トヨタ自動車株式会社 可変圧縮比内燃機関
EP3071854A1 (fr) * 2013-11-18 2016-09-28 Schaeffler Technologies AG & Co. KG Support de couple d'un actionneur monté sur un carter d'embrayage/d'engrenages

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EP3081789A4 (fr) * 2013-12-10 2016-12-21 Toyota Motor Co Ltd Moteur à combustion interne
CN105745421B (zh) * 2013-12-10 2018-05-04 丰田自动车株式会社 内燃机
CN105745421A (zh) * 2013-12-10 2016-07-06 丰田自动车株式会社 内燃机
WO2015169710A1 (fr) * 2014-05-06 2015-11-12 Ntn-Snr Roulements Actionneur électromécanique à vis à billes pour un embrayage
FR3020846A1 (fr) * 2014-05-06 2015-11-13 Ntn Snr Roulements Actionneur electromecanique a vis a billes pour un embrayage
CN106662227A (zh) * 2014-07-02 2017-05-10 斯泰必鲁斯股份有限公司 驱动装置和阀门控制装置
WO2016001147A1 (fr) * 2014-07-02 2016-01-07 Stabilus Gmbh Ensemble d'entraînement et commande à clapets
US10273737B2 (en) 2014-07-02 2019-04-30 Stabilus Gmbh Drive arrangement and hatch control
CN104613136A (zh) * 2015-01-30 2015-05-13 陕西东铭车辆系统股份有限公司 带电磁双向离合器的两挡位变速电动车后桥减速器总成
CN104613136B (zh) * 2015-01-30 2017-06-16 陕西东铭车辆系统股份有限公司 带电磁双向离合器的两挡位变速电动车后桥减速器总成
EP3833841B1 (fr) * 2018-08-08 2023-10-25 D+H Mechatronic AG Mécanisme d'entraînement à arbre ayant un dispositif automatique de blocage
CN110778673A (zh) * 2019-09-12 2020-02-11 浙江捷昌线性驱动科技股份有限公司 一种线性致动器的自锁装置和线性致动器
CN110778673B (zh) * 2019-09-12 2023-05-26 浙江捷昌线性驱动科技股份有限公司 一种线性致动器的自锁装置和线性致动器
CN111016640A (zh) * 2019-12-31 2020-04-17 西南大学 超大载荷的紧凑型中央驱动式自适应电驱动总成

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