WO2015060209A1 - Dispositif de commande de transmission pour transmission à variation continue - Google Patents

Dispositif de commande de transmission pour transmission à variation continue Download PDF

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Publication number
WO2015060209A1
WO2015060209A1 PCT/JP2014/077667 JP2014077667W WO2015060209A1 WO 2015060209 A1 WO2015060209 A1 WO 2015060209A1 JP 2014077667 W JP2014077667 W JP 2014077667W WO 2015060209 A1 WO2015060209 A1 WO 2015060209A1
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WO
WIPO (PCT)
Prior art keywords
reverse
transmission
torque
feed shaft
shaft
Prior art date
Application number
PCT/JP2014/077667
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English (en)
Japanese (ja)
Inventor
彬 伊地知
元樹 田淵
一哉 荒川
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トヨタ自動車株式会社
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Filing date
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Application filed by トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
Publication of WO2015060209A1 publication Critical patent/WO2015060209A1/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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/04—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism
    • F16H63/06—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions
    • F16H63/062—Final output mechanisms therefor; Actuating means for the final output mechanisms a single final output mechanism being moved by a single final actuating mechanism the final output mechanism having an indefinite number of positions electric or electro-mechanical actuating means
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/021—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings toothed gearing combined with continuous variable friction gearing
    • F16H2037/026—CVT layouts with particular features of reversing gear, e.g. to achieve compact arrangement
    • 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
    • F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
    • F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
    • F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
    • F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
    • F16H9/16—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts
    • F16H9/18—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members using two pulleys, both built-up out of adjustable conical parts only one flange of each pulley being adjustable

Definitions

  • the present invention relates to a device for controlling a continuously variable transmission, and more particularly to a device for controlling a shift in a continuously variable transmission of a type in which a driving force is transmitted by a belt such as a dry belt.
  • a drive pulley and a driven pulley around which a belt is wound are configured by a fixed sheave fixed in the axial direction and a movable sheave that can move in the axial direction so as to approach and separate from the fixed sheave.
  • a feed screw mechanism is connected to these movable sheaves, and the torque of the transmission motor is converted into an axial stroke force by the feed screw mechanism, and the movable sheave is moved in the axial direction by the stroke force.
  • a forward switching mechanism that is switched between a forward position, a neutral position, and a reverse position is provided, and this forward switching mechanism is connected to the output side of the driven pulley. Accordingly, when the forward switching mechanism is set to the neutral position, the connection between the continuously variable transmission and the drive wheels is cut off, so that the pulley of the continuously variable transmission can be used even when the vehicle is stopped and the drive wheels are stopped. Can be rotated. That is, it is possible to set a gear ratio suitable for starting by changing the gear ratio in a stopped state.
  • Japanese Patent Application Laid-Open No. 11-159596 describes a continuously variable transmission that can facilitate re-start even during sudden braking.
  • a forward / reverse switching mechanism having a clutch mechanism is provided on the output shaft. Since the transmission mechanism is in an idle state by opening the clutch mechanism, the transmission gear ratio can be changed to that used at the time of start.
  • JP-A-8-145095 a clutch stator and a brake stator each having a built-in coil are arranged on both sides of an armature connected to an output shaft, and these coils are selectively excited by exciting them.
  • a device is described that is configured to selectively connect an output shaft to a clutch and a brake.
  • Japanese Patent Application Laid-Open No. 2007-303618 discloses that a movable sheave in a driving pulley and a movable sheave in a driven pulley are respectively moved back and forth by a ball screw mechanism, and these ball screw mechanisms are used as one motor.
  • a belt-type continuously variable transmission configured to be driven by is described.
  • Japanese Patent No. 4413310 discloses a motor for changing a gear ratio, a drive unit for moving a movable sheave constituting a pulley in the axial direction, and transmission of torque output by the motor to the drive unit. And a clutch mechanism for switching between them.
  • the actuators associated with the continuously variable transmission are at least two actuators, that is, a gear shifting motor and a forward / backward switching actuator.
  • the apparatus may be increased in size. This is because the continuously variable transmission described in the above-mentioned Japanese Patent Application Laid-Open No. 2003-130157 is added to the above-mentioned Japanese Patent Application Laid-Open No. 11-159596, Japanese Patent Application Laid-Open No. 8-14595, or Japanese Patent Application Laid-Open No. 2007-303618. This is the same even when the devices described in Japanese Patent Publication No. 4413310 are combined, and it is necessary to develop a new technique for downsizing the device.
  • the present invention has been made under the above-described technical background, and is capable of downsizing the overall configuration even when the shift control and the forward / reverse switching control are electrically performed. It is an object of the present invention to provide a transmission control device for a transmission.
  • the present invention outputs a torque to a drive unit and a transmission unit that continuously changes a transmission ratio by changing a width of a belt winding groove in a pulley around which a belt is wound.
  • a transmission control device for a continuously variable transmission that includes a forward / reverse switching unit that switches a rotation direction of an output shaft to be moved between a forward direction and a reverse direction, the operation force that changes the speed ratio and the forward / reverse switching unit are switched.
  • a power transmission switching mechanism that selectively couples the actuator to the transmission unit and the forward / reverse switching unit.
  • the power transmission switching mechanism connects the actuator to the forward / reverse switching unit in an on state supplied with energy, and connects the actuator to the transmission unit in an off state where supply of energy is cut off. It can be configured as follows.
  • the forward / reverse switching unit is set to a forward state where the rotation direction of the output shaft is a forward direction, a reverse state where the rotation direction of the output shaft is a reverse direction, and a neutral state where transmission of torque is cut off. And may be arranged connected to the output side of the transmission unit.
  • the actuator according to the present invention includes an electric motor, and the speed change portion is an axial thrust that changes the width of the belt winding groove with the torque transmitted from the electric motor via the power transmission switching mechanism.
  • the forward / reverse switching portion linearly moves back and forth by the torque transmitted from the electric motor via the power transmission switching mechanism and is accompanied by the linear forward and backward movement. It can be set as the structure provided with the selection shift mechanism which selectively sets a forward drive state and a reverse drive state by rotating.
  • the pulley changes the width of the belt winding groove by moving toward and away from the fixed sheave that is held so as to rotate without moving in the axial direction.
  • the movable sheave that rotates together with the fixed sheave, the thrust generating mechanism includes a pair of screw members that are fitted to each other via screws, and one screw member is integrated with the movable sheave. And is connected to the movable sheave so as to move in the axial direction, and the other screw member is fixed so as not to move in the axial direction, and the torque of the electric motor is
  • the screw members may be configured such that each screw member is rotated relative to the screw member to generate an axial thrust.
  • the forward / reverse switching unit does not transmit the forward torque to the output shaft at the neutral position, and linearly moves from the neutral position to the forward position to thereby increase the forward torque.
  • a forward torque transmitting member that is transmitted to the output shaft, and a forward torque transmitting member that is shifted in a direction perpendicular to the linear movement direction of the forward torque transmitting member, and in the neutral position, torque in the reverse direction is applied to the output shaft.
  • the select / shift mechanism has a first position corresponding to the neutral position by the torque transmitted through the power transmission switching mechanism.
  • the second position corresponding to one of the forward position and the reverse position aligned in a straight line with the first position across the first position, and the other of the forward position and the reverse position Linearly moves back and forth to a third position corresponding to the position of the first position, and rotates about its central axis while moving from the first position to each of the second position and the third position.
  • the protrusion which is engaged with the other member so as to linearly press either member and rotates together with the feed shaft when the feed shaft moves from the first position to the third position. It can be set as the structure provided with the connection reversal member which a part engages and presses said other member in the direction opposite to the linear moving direction of this protrusion part.
  • the select / shift mechanism includes an engaging portion having a non-circular cross section formed at both ends of the feed shaft, and the projecting portion of the forward torque transmitting member and the reverse torque transmitting member. After engaging with one of the members, one of the engaging portions is fitted to stop the rotation of the feed shaft and move in the axial direction, and the projecting portion is engaged with the connection reversing member. A second fitting part that engages the other engaging part to stop the rotation of the feed shaft and moves it in the axial direction, and is fitted to the feed shaft so as to be capable of relative rotation. A cylindrical member that moves back and forth, and a cam portion that is provided between the feed shaft and the cylindrical member and rotates the feed shaft by a predetermined angle when the cylindrical member moves in the axial direction. Can do.
  • the power transmission switching mechanism transmits a first engagement portion that engages the transmission portion to transmit the operation force, and transmits the operation force to the forward / reverse switching portion.
  • an electromagnetic clutch in which the second engagement portion engages when the first engagement portion is engaged by electromagnetic force and no electromagnetic force is applied. Can be included.
  • the continuously variable transmission clamps the belt according to the torque to be transmitted and the primary pulley to which the torque is inputted from a predetermined driving force source and the width of the belt winding groove is changed.
  • a secondary pulley to which a clamping pressure is applied, and the forward / reverse switching unit may be disposed in a path for transmitting torque from the secondary pulley to the output shaft.
  • the operating force for changing the gear ratio set by the transmission unit and the operating force for switching the forward / reverse switching unit to the forward state or the reverse state are output from one actuator.
  • the power transmission switching mechanism transmits the operating force of the actuator to the shifting unit, and the gear ratio is changed.
  • the forward state is set or the reverse state is set
  • the operating force of the actuator is transmitted to the forward / reverse switching unit by the power transmission switching mechanism. Therefore, according to the present invention, there is no need to provide separate actuators for the shift control and the forward / reverse switching control, the number of actuators can be reduced, and the overall configuration of the apparatus can be reduced in size or simplified. .
  • the shift control is performed more frequently than the forward / reverse switching frequency. Energy efficiency can be improved by reducing energy.
  • off-fail failure in which energy cannot be supplied to the power transmission switching mechanism occurs, it is possible to shift gears. Therefore, when the shift control device according to the present invention is mounted on a vehicle, it is turned off. -It is possible to perform evacuation during a failure.
  • the speed change control device can be Even if the vehicle suddenly stops and the gear ratio does not increase beyond the predetermined gear ratio, the gear ratio is increased to a gear ratio suitable for re-starting by rotating the transmission after stopping. Can be made.
  • the actuator according to the present invention may be an actuator of a type that linearly moves back and forth to generate axial thrust or an actuator of a type that rotates to generate torque, and when a motor that generates torque is employed as the actuator,
  • the transmission unit can be provided with a thrust generating mechanism that converts torque into axial thrust, and the forward / reverse switching unit linearly moves back and forth and rotates along with the linear forward and backward movements to perform a selection operation. It can be set as the structure provided with the select shift mechanism which performs shift operation.
  • the thrust generating mechanism can be constituted by a so-called feed screw mechanism.
  • the select / shift mechanism is configured such that when the fork member linearly moves from the neutral position, the fork member rotates around an axis parallel to the linear movement direction to move the forward torque transmission member or the reverse torque. It can be set as the structure which engages with a transmission member and a fork member moves those transmission members to an axial direction after that. With this configuration, the forward / reverse switching unit or the select / shift mechanism can be made small with a small number of components.
  • FIG. 5 is an arrangement diagram showing relative positions of a driven shaft, an output shaft, and a reverse idle shaft in one specific example of the present invention. It is a flowchart for demonstrating the belt return control performed by one specific example of this invention.
  • the transmission unit 1 has a driving pulley 2 and a driven pulley 3 in the same manner as conventionally known. And a belt 4 wound around these pulleys 2 and 3.
  • the pulleys 2 and 3 and the belt 4 may be made of metal, or may be a so-called dry type having a large friction coefficient with a contact surface made of synthetic resin.
  • the present invention is particularly effective for a continuously variable transmission having a dry belt.
  • the drive pulley 2 includes a fixed sheave 6 that is integrated with the drive shaft 5 and does not move in the axial direction, and a movable sheave 7 that is attached to the drive shaft 5 so as to approach and separate from the fixed sheave 6.
  • the driven pulley 3 is integrated with a driven shaft 8 that is parallel to the drive shaft 5 and is fixed to the driven shaft 8 so as to approach and separate from the fixed sheave 9 that does not move in the axial direction.
  • the movable sheave 10 is attached.
  • the mutually facing surfaces of the fixed sheaves 6 and 9 and the movable sheaves 7 and 10 in the pulleys 2 and 3 are formed in a tapered shape.
  • the width of the belt winding grooves 11 and 12 around which the belt 4 is wound and the radius around which the belt 4 is wound are continuously changed.
  • the movable sheave 10 (7) is pressed toward the fixed sheave 9 (6) so as to set a target transmission torque capacity.
  • the target gear ratio is set by changing the width of the belt winding groove 11 of the driving pulley 2, and the thrust for pressing the movable sheave 10 in the driven pulley 3 is controlled to be the target.
  • the transmission torque capacity is set.
  • the movable sheave 7 is formed with a boss portion 13 extending on the back side (the side opposite to the fixed sheave 6).
  • a first screw member 14 is attached to the boss portion 13 via a bearing 15 so as to be relatively rotatable and integrated in the axial direction.
  • a second screw member 16 screwed into the first screw member 14 is attached to a fixing portion 17 such as a transmission housing.
  • One end portion of the drive shaft 5 is rotatably supported by the fixed portion 17 via a bearing 18.
  • These screw members 14 and 16 are formed in a cylindrical shape, a female screw is formed on the inner peripheral surface of one screw member 14 (16), and the other is inserted inside the screw member 14 (16).
  • a transmission gear 19 is integrated with the first screw member 14 attached to the movable sheave 7.
  • the transmission gear 19 is for transmitting torque, which is a transmission operation force, to the first screw member 14.
  • Each of the screw members 14 and 16 is a conventionally known feed screw mechanism and constitutes a thrust generating mechanism 20 in the present invention.
  • the movable sheave 10 in the driven pulley 3 is pressed against the fixed sheave 9 by the torque cam 21 and the spring 22. It is configured.
  • This so-called pressing mechanism is configured in the same manner as conventionally known.
  • the cam shaft 23 is fitted on the outer peripheral side of the driven shaft 8 so as to be relatively rotatable and not moved in the axial direction.
  • the cam shaft 23 protrudes toward the back surface of the movable sheave 10.
  • a cylindrical cam 24 is integrated.
  • the cylindrical cam 24 has a smooth wavy (wave-like) cam surface whose end face toward the back surface of the movable sheave 10 protrudes and recedes in the axial direction, or a cam surface that is continuous with a flat surface folded. Cylinder.
  • a cam follower 25 is pressed against the cam surface so as to be in direct contact, or is pressed through a rolling element such as a ball or a roller.
  • the cam follower 25 is integrated with the movable sheave 10 so as to protrude toward the back side of the movable sheave 10.
  • the cam follower 25 only needs to be configured so as to generate an axial thrust by the torque acting between the cylindrical cam 24.
  • the cam follower 25 is a cylindrical member whose end surface has the same shape as the cam surface. Alternatively, it may be a plurality of shaft-shaped members whose front ends are abutted against the cam surface.
  • a spring 22 is disposed between the back surface of the movable sheave 10 and the cam shaft 23. The movable sheave 10 is pressed toward the fixed sheave 9 by the elastic force of the spring 22.
  • the belt 4 is tensioned to cause the belt winding grooves 11, 12 to be spread. That is, the movable sheave 10 in the driven pulley 3 is pushed toward the cylindrical cam 24 side. As a result, the cam surface of the cam follower 25 is pressed directly or indirectly against the cam surface of the cylindrical cam 24. In this state, when a torque that relatively rotates the driven pulley 3 and the cam shaft 23 acts, an axial thrust corresponding to the torque, that is, a belt clamping pressure is generated by the action of the cam surface.
  • the drive pulley 2 described above is an input element of the transmission unit 1, and the drive shaft 5 is connected to the drive force source 27 via the start clutch 26.
  • the driving force source 27 is constituted by an internal combustion engine such as a gasoline engine, an electric motor, or a hybrid drive device combining these.
  • the starting clutch 26 is a friction clutch that transmits and shuts off torque between the driving force source 27 and the driving shaft 5 and can be constituted by a wet clutch or a dry clutch. In the example shown in FIG. 1, a dry clutch is employed as the starting clutch 26, and the starting clutch 26 is connected to a driving force source 27 via a damper 28.
  • the starting clutch 26 has the same configuration as a conventionally known dry clutch for vehicles, and the driving and driven friction plates are brought into contact with each other by a diaphragm spring, and the diaphragm spring is bent by a release mechanism. Thus, the contact pressure between the friction plates is reduced.
  • the release mechanism is configured to press the inner peripheral end of the diaphragm spring in the axial direction by a lever member, and a clutch actuator 29 for operating the lever member is provided.
  • the actuator 29 is mainly for moving the end of the lever member on the power point side back and forth, and therefore can be constituted by an electric or hydraulic linear cylinder or motor. In the example shown in FIG. 1, an electric motor is employed as the clutch actuator.
  • the driven pulley 3 described above is an output element of the transmission unit 1, and torque is transmitted from the driven shaft 8 to the output shaft 31 via the torque cam 21, the cam shaft 23, and the forward / reverse switching mechanism 30 described above, and the output thereof Torque is transmitted from the shaft 31 to the left and right drive wheels 33 via a differential gear 32 that is a final reduction gear.
  • the speed change control device performs a change operation of the forward / reverse switching mechanism 30 and a speed change operation for changing the groove width of the belt winding groove 11 of the drive pulley 2 by an operating force output by a single actuator.
  • the actuator can be constituted by an electric or hydraulic linear cylinder or motor, and in the example shown in FIG. 1, the electric motor 34 is used as the actuator.
  • the motor 34 is connected to a power transmission switching mechanism 35, and is configured to transmit operating force from the power transmission switching mechanism 35 to the transmission unit 1 and the forward / reverse switching mechanism 30 described above.
  • the power transmission switching mechanism 35 is a mechanism for switching and transmitting torque output from the motor 34 to at least two locations.
  • the power transmission switching mechanism 35 includes a two-way clutch 36. ing.
  • An example of the two-way clutch 36 is schematically shown in FIG.
  • a rotor 38 that protrudes in the radial direction is attached to a motor shaft 37 that outputs torque of the motor 34 in a state of being prevented from rotating by a key, a spline, or the like, and a first armature 39 and a first armature 39 are attached to both sides of the rotor 38.
  • 2 armatures 40 are arranged.
  • These armatures 39 and 40 are members that function as friction plates that are attracted by a magnetic force and are pressed against a predetermined object to transmit torque, and are formed in a ring shape, for example.
  • the armatures 39 and 40 are connected by rods (or pins) 41 that penetrate the rotor 38 in the axial direction and are longer than the thickness of the rotor 38.
  • the rod 41 and the armatures 39 and 40 can be connected by means such as bolting or caulking.
  • the rod 41 is loosely fitted to the rotor 38, so that each armature 39, 40 can be moved back and forth between a position attracted to the side surface of the rotor 38 and a position away from the side surface of the rotor 38. Has been.
  • a spring 42 that presses the armature 39 away from the side surface of the rotor 38 is disposed between the armature 39 on one side (left side in FIG. 2) and the side surface of the rotor 38.
  • the spring 42 is preferably a wave spring, but may be another elastic body such as a plurality of coil springs.
  • a first drive plate 43 facing the first armature 39 and a second drive plate 44 facing the second armature 40 are rotatably attached to the motor shaft 37.
  • the first drive plate 43 is for outputting an operating force to the transmission unit 1, and an example thereof is a drive gear 46 for shifting that is fitted to the motor shaft 37 via a bearing 45. It is a disc part.
  • the second drive plate 44 is for outputting an operating force to the forward / reverse switching mechanism 30, and is an output gear that is rotatably fitted to the tip of the motor shaft 37 via a bearing 47.
  • 48 is a flange portion formed integrally with 48.
  • the second armature 40 is located on the opposite side of the second drive plate 44 (FIG. 2). Then, the electromagnetic coil 49 is arranged on the right side.
  • the drive plates 43 and 44 and the rotor 38 are made of a nonmagnetic material and attract the armatures 39 and 40 to the electromagnetic coil 49 side by the magnetic force generated by the electromagnetic coil 49. . Therefore, in the normal state (non-operating state) in which the electromagnetic coil 49 shown in FIG.
  • a reduction gear mechanism 51 for transmitting torque from the drive gear 46 to the transmission gear 19 is provided.
  • the reduction gear mechanism 51 includes three counter shafts 52, 53, and 54.
  • the first counter shaft 52 is provided with a large-diameter gear 55 that meshes with the drive gear 46 and a smaller-diameter gear 56.
  • the second countershaft 53 is provided with a large-diameter gear 57 that meshes with a small-diameter gear 56 in the first countershaft 52 and a smaller-diameter gear 58.
  • the third countershaft 54 is provided with a large-diameter gear 59 that meshes with a small-diameter gear 58 in the second countershaft 53 and a drive gear 60 that has a smaller diameter and a longer axial length.
  • the drive gear 60 is engaged with the transmission gear 19 described above.
  • a specific configuration of the power transmission switching mechanism 35, the reduction gear mechanism 51, and the thrust generating mechanism 20 described above is shown in a sectional view in FIG.
  • a power transmission switching mechanism 35 is constituted by two electromagnetic clutches 35A and 35B provided in parallel, and the shift clutch 35A is engaged in a non-energized state to transmit torque. Further, the forward / reverse switching clutch 35B is configured to be released in a non-energized state and to block transmission of torque.
  • a forward drive gear 61 and a reverse drive gear 62 are attached to the cam shaft 23 described above.
  • a forward driven gear 63 meshed with the forward drive gear 61 is fitted to the output shaft 31 so as to be relatively rotatable.
  • a synchronizer 64 is provided for connecting the forward driven gear 63 and the output shaft 31 so as to transmit torque.
  • the synchronizer 64 has the same configuration as that widely used in conventional vehicle transmissions, and its specific configuration is shown in a sectional view in FIG.
  • a hub sleeve 66 that moves back and forth in the axial direction and rotates together with the hub 65 is spline-fitted to the outer peripheral portion of the hub 65 integral with the output shaft 31.
  • a spline portion 67 on the forward driven gear 63 side is disposed at a position having the same outer diameter as the hub 65 and adjacent to the hub 65.
  • a synchronizer ring 68 is disposed between the hub 65 and the boss portion of the forward driven gear 63 on the inner peripheral side of the hub sleeve 66.
  • a reverse driven gear 69 is integrally formed on the outer peripheral portion of the hub sleeve 66.
  • the hub sleeve 66 is arranged so that the reverse driven gear 69 is positioned on the outer peripheral side of the reverse drive gear 62 on the cam shaft 23 described above. Therefore, when the hub sleeve 66 is moved in the left direction in FIG.
  • the hub sleeve 66 is spline-fitted to the spline portion 67 on the forward driven gear 63 side.
  • the forward driven gear 63 and the output shaft 31 are connected.
  • An output gear 70 is provided on the output shaft 31 so as to rotate integrally.
  • the output gear 70 meshes with the ring gear 71 in the differential gear 32 described above. Therefore, when the forward driven gear 63 and the output shaft 31 are connected by the synchronizer 64, the differential from the cam shaft 23 through the forward drive gear 61 and the forward driven gear 63 meshed with the forward drive gear 61, the output shaft 31 and the output gear 70. Torque is transmitted to the gear 32 and the vehicle travels forward.
  • a reverse idle gear 72 is provided that moves to a position where the mesh is disengaged.
  • the specific configuration is shown in a partial cross-sectional view in FIG. 5, and is parallel to these shafts 23 and 31 at a position deviated from a plane passing through the central axis of the cam shaft 23 and the central axis of the output shaft 31.
  • a reverse idle shaft 73 is disposed on the left side.
  • the reverse idle gear 72 is attached to the reverse idle shaft 73 so as to be rotatable and movable in the axial direction.
  • the reverse idle gear 72 moves to a position where the reverse idle gear 72 is engaged with the reverse drive gear 62 in a state where the hub sleeve 66 is in a so-called neutral position where the hub sleeve 66 is not engaged with the spline portion 67 on the forward driven gear 63 side,
  • the gear 72 meshes with the reverse driven gear 69. Therefore, since the reverse idle gear 72 is interposed between the reverse drive gear 62 on the cam shaft 23 and the reverse driven gear 69 on the output shaft 31, a reverse state is set.
  • a select / shift mechanism 74 is provided that causes the torque of the motor 34 that outputs the above-described operation force for shifting to act on the hub sleeve 66 and the reverse idle gear 72 as an operation force for moving them in the axial direction.
  • the select / shift mechanism 74 is configured to select an operation for setting the forward movement state and an operation for setting the reverse movement state, and to execute the selected operations.
  • the operation for setting the forward state and the operation for setting the reverse state are performed by the feed shaft 75 moving back and forth and rotating in accordance with the back and forth movement.
  • FIGS A specific example is shown in FIGS.
  • the feed shaft 75 has a circular cross section at the middle and a non-circular cross section at both ends, and is arranged in parallel with the output shaft 31 and the reverse idle shaft 73 described above. Further, the feed shaft 75 linearly moves back and forth between the neutral position and the forward and backward positions on both sides of the neutral position, and rotates by a predetermined angle around the central axis along with the forward and back
  • the output gear 48 attached to the tip of the motor shaft 37 is a bevel gear in the example shown in the figure, and the output gear 48
  • a bevel gear 76 on the driven side meshing with 48 is arranged with its center axis oriented in a direction perpendicular to the motor shaft 37.
  • a cylindrical or columnar gear 77 integrated with the bevel gear 76 is provided so as to rotate along the central axis of the bevel gear 76.
  • a fan-shaped gear (hereinafter referred to as a fan-shaped gear) 78 is engaged with the gear 77.
  • An arm portion 79 extends diametrically opposite the gear portion of the sector gear 78.
  • a pin 80 is attached to the distal end portion of the arm portion 79 in a direction parallel to the rotation center axis of the arm portion 79.
  • a sleeve 81 is fitted in an intermediate portion of the feed shaft 75 so as to be rotatable relative to the feed shaft 75 and relatively movable in the axial direction.
  • the pin 80 is inserted into a groove 82 formed in the outer peripheral portion of the sleeve 81.
  • the pin 80 and the groove 82 are a coupling mechanism that converts the rotational motion of the sector gear 78 or the arm portion 79 into the linear motion of the sleeve 81. Therefore, a groove is formed in the arm portion 79, and the groove is formed in the groove.
  • An engaging pin may be provided on the sleeve 81.
  • the sector gear 78 may be a circular gear and a rack that meshes with the sector gear 78 may be provided on the sleeve 81.
  • a cam portion that converts the relative movement of both in the axial direction into a rotational operation.
  • a cam portion is constituted by a spiral groove or a spiral through hole (hereinafter referred to as a spiral groove) 83 and a cam follower 84 such as a pin fitted to the spiral groove or spiral through hole (hereinafter referred to as a spiral groove). That is, the sleeve 81 is formed with a spiral groove 83 having a length corresponding to an angle at which the feed shaft 75 should be rotated about its central axis, and a pin 84 moving along the spiral groove 83 is fed.
  • the shaft 75 is provided in a state of protruding outward in the radial direction.
  • engaging portions 85F and 85R having non-circular cross sections are provided at both ends of the feed shaft 75.
  • the engaging portions 85F and 85R are two-surface width portions obtained by cutting the end portion of the feed shaft 75 into two surfaces parallel to each other along the central axis. This is for stopping the rotation of the feed shaft 75. Therefore, the shape may be a non-circular cross section, and is not limited to the two-plane width.
  • Holder portions 86 ⁇ / b> F and 86 ⁇ / b> R with which end portions of the feed shaft 75 are fitted are provided on the predetermined fixing portion 17.
  • These holder portions 86F and 86R have cylindrical shapes with closed ends, and the rear end portions thereof are fitting portions 87F that are hollow portions having a non-circular cross section corresponding to the cross sectional shape of the engagement portions 85F and 85R. , 87R.
  • the relative phases of the engaging portions 85F and 85R and the fitting portions 87F and 87R are set as follows.
  • the feed shaft 75 has the length of the spiral groove 83 and the stroke of the sleeve 81 by the action of the cam portion formed of the spiral groove 83 and the pin 84.
  • the angle is rotated according to the amount.
  • the phase of the engaging portion 85R on the moving direction side of the sleeve 81 coincides with one fitting portion 87R corresponding thereto.
  • the position where the feed shaft 75 has moved to the left end in FIG. 6 is the reverse (reverse) position.
  • the feed shaft 75 is moved by the action of the cam portion composed of the spiral groove 83 and the pin 84 described above.
  • the angle rotates according to the length of the spiral groove 83 and the stroke amount of the sleeve 81.
  • the phase of the engaging portion 85F on the moving direction side of the sleeve 81 coincides with the other fitting portion 87F corresponding thereto.
  • the position where the feed shaft 75 has moved to the right end in FIG. 7 is the forward (forward) position.
  • the feed shaft 75 is further provided with a protruding portion 88 that functions as an operation portion.
  • the projecting portion 88 is a plate-like arm portion projecting outward in the radial direction from the feed shaft 75, rotates integrally with the feed shaft 75, and linearly moves back and forth in the axial direction. That is, the protrusion 88 rotates a predetermined angle left and right around the position where the feed shaft 75 is in the neutral position.
  • FIG. 8 shows the rotation position of the protrusion 88 at the neutral position, the rotation position at the forward movement position, and the rotation position at the reverse movement position.
  • FIG. 8 also shows the relative positions of the driven shaft 8 and the cam shaft 23, the output shaft 31, the reverse idle shaft 73, and the feed shaft 75 described above by the positions of the respective central axes.
  • the reverse idle shaft 73 is arranged out of a plane passing (including) the center axis of the driven shaft 8 and the cam shaft 23. Therefore, the reverse idle gear 72 fitted to the reverse idle shaft 73 is moved in the axial direction, so that the reverse drive gear 62 on the cam shaft 23 and the reverse driven gear 69 integrated with the hub sleeve 66 in the synchronizer 64 are integrated. It comes to mesh.
  • a reverse fork 89 for moving the reverse idle gear 72 in the axial direction is provided.
  • the reverse fork 89 is a member similar to a shift fork provided in a conventional vehicle transmission, and is disposed near the reverse idle shaft 73 so as to be parallel to the reverse idle shaft 73 and movable in the axial direction.
  • the support shaft 90 is attached.
  • reference numeral 90 ⁇ / b> A is a sensor that detects the position of the support shaft 90.
  • One end of the reverse fork 89 is engaged with a groove formed in the boss portion of the reverse idle gear 72, and the other end of the reverse fork 89 is the rotational position of the projecting portion 88 that performs the select operation.
  • the feed shaft 75 extends to a position that coincides with the rotational position when the feed shaft 75 is moved to the reverse position. That is, when the feed shaft 75 moves to the reverse position, the projecting portion 88 engages with the reverse fork 89 and moves integrally in the axial direction. That is, the reverse fork 89 and the reverse idle gear 72 with which the reverse fork 89 is engaged correspond to a reverse torque transmission member and linearly move back and forth between the neutral position and the reverse position.
  • a forward fork 91 for moving the hub sleeve 66 in the synchronizer 64 in the axial direction is provided.
  • the forward fork 91 is a member similar to a shift fork provided in a conventional vehicle transmission, and is disposed in a position close to the output shaft 31 so as to be parallel to the output shaft 31 and movable in the axial direction. Attached to the shaft 92. One end portion of the forward fork 91 is engaged with a groove formed in the boss portion of the hub sleeve 66. Further, between the support shaft 92 and the feed shaft 75, there is provided a rotating arm 93 corresponding to the connection reversal member in the present invention.
  • the rotary arm 93 is disposed between the feed shaft 75 and the support shaft 92 and is provided so as to rotate about a mounting shaft 94 that is oriented perpendicularly to the central axis of the shafts 75 and 92. ing.
  • One end of the rotating arm 93 is engaged with the protrusion 88 of the feed shaft 75 described above, and the other end is engaged with the support shaft 92 so as to push the support shaft 92 in the axial direction. That is, the moving direction of the support shaft is opposite to the moving direction of the feed shaft 75.
  • Forward fork 91 linearly moves in the direction opposite to the feed shaft 75.
  • the forward fork 91 and the hub sleeve 66 with which the forward fork 91 is engaged correspond to a forward torque transmitting member, and linearly move back and forth between the neutral position and the forward position.
  • the starting clutch 26 is controlled to a release state in which torque is cut off. This is performed by operating the clutch actuator 29. In this state, torque does not act on the forward / reverse switching mechanism 30, so forward / reverse or neutral switching is performed.
  • the shift control device described here is configured to perform forward / reverse switching and shifting by the motor 34 that is a single actuator, and in order to switch the forward / reverse switching mechanism 30 for that purpose,
  • the two-way clutch 36 is operated to transmit torque to the second drive plate 44.
  • the electromagnetic coil 49 is energized to move the armatures 39 and 40 to the second drive plate 44 side.
  • the first armature 39 is separated from the drive gear 46 for speed change, the second armature 40 is in frictional contact with the second drive plate 44 which is a flange portion integrated with the output gear 48, and the second drive plate 44 side is subjected to torque.
  • the engaged state can be transmitted.
  • the sector gear 78 is rotated by the torque of the motor 34 through the bevel gear 76 and the gear 77 integral therewith.
  • the sector gear via the pin 80 is rotated.
  • the sleeve 81 connected to 78 moves in the axial direction. Since the sleeve 81 and the feed shaft 75 are connected by the cam portion composed of the spiral groove 83 and the pin 84 described above, the feed shaft 75 is engaged with the engaging portions 85F and 85R at the end thereof and the fitting portion into which the sleeve 81 and the feed shaft 75 are fitted.
  • the feed shaft 75 moves in the axial direction together with the sleeve 81.
  • the projecting portion 88 is engaged with any of the forks 89 and 91
  • the support shafts 90 and 92 are moved together with the forks 89 and 91, and the positions thereof are provided corresponding to the sensors. Detected by 90A.
  • the motor 34 stops at the target shift position.
  • the feed shaft 75 When the neutral position is selected as the shift position, the feed shaft 75 has been moved to the neutral position. In this state, the engaging portions 85F and 85R formed at both ends of the feed shaft 75 have come out of the corresponding fitting portions 87E and 87R, and the feed shaft 75 is in a rotatable state. Further, the protrusion 88 is not engaged with either the reverse fork 89 or the forward fork 91. Accordingly, the forks 89 and 91 and the support shafts 90 and 92 are returned to the neutral position, and the reverse idle gear 72 is disengaged from the reverse drive gear 62 and the reverse driven gear 69. The synchronizer 64 is in a released state, and torque transmission between the forward driven gear 63 and the output shaft 31 is interrupted. That is, the entire forward / reverse switching mechanism 30 is in a neutral state where torque is not transmitted.
  • the two-way clutch 36 constituting the power transmission switching mechanism 35 is energized and the two-way clutch 36 is engaged with the second drive plate 44 side.
  • the motor 34 rotates and the bevel gear 76 engaged with the output gear 70 rotates in the clockwise direction in FIG. 7, and the sector gear 78 engaged therewith rotates in the counterclockwise direction in FIG.
  • the sleeve 81 fitted to the feed shaft 75 is pushed from the neutral position toward the forward position (right direction in FIG. 7).
  • the feed shaft 75 since the feed shaft 75 is in a state where it can rotate without being moved in the axial direction, the feed shaft 75 is rotated by the action of a cam portion provided between the sleeve 81 and the feed shaft 75. As a result, the protrusion 88 rotates counterclockwise in FIG. 8 and engages with one end of the rotary arm 93 described above. At the same time, the phase of one of the engaging portions 85F formed at the end of the feed shaft 75 coincides with the phase of the fitting portion 87F formed corresponding thereto, so that the feed shaft 75 has its axis line. It will be ready to move in the direction.
  • the engagement portion 85F having a non-circular cross section is fitted to the fitting portion 87F to prevent the rotation of the feed shaft 75, and the feed shaft 75 and the protrusion 88 integrated therewith are axially moved together with the sleeve 81. Move to.
  • the rotary arm 93 is supported so as to rotate about the intermediate portion thereof. Therefore, when the end portion on the feed shaft 75 side moves in the right direction in FIG. 7, the other end portion is in FIG. Moving leftward, the support shaft 92 and the forward fork 91 attached thereto are moved leftward in FIG. As a result, the hub sleeve 66 in the synchronizer 64 moves to the forward driven gear 63 side, and the synchronizer 64 is engaged. That is, the forward driven gear 63 is connected to the output shaft 31.
  • the feed shaft 75 Since it comes out of the portion 87F, the feed shaft 75 becomes rotatable. In order to further move the sleeve 81, the feed shaft 75 is rotated by the action of a cam portion provided between the sleeve 81 and the feed shaft 75, and the projecting portion 88 projecting to the outer peripheral side of the feed shaft 75 Leave the end and return to the neutral position.
  • the two-way clutch 36 constituting the power transmission switching mechanism 35 is energized and the two-way clutch 36 is moved to the second drive plate 44 side, as in the case of setting the forward state.
  • Engage In this state, the bevel gear 76 that rotates in the opposite direction to the case where the motor 34 sets the forward movement state and meshes with the output gear 70 rotates counterclockwise in FIG.
  • the gear 78 rotates clockwise in FIG.
  • the sleeve 81 fitted to the feed shaft 75 is pushed from the neutral position toward the reverse position (left direction in FIG. 6).
  • the feed shaft 75 since the feed shaft 75 is in a state where it can rotate without being moved in the axial direction, the feed shaft 75 is rotated by the action of a cam portion provided between the sleeve 81 and the feed shaft 75. As a result, the protrusion 88 rotates clockwise in FIG. 8 and engages with one end of the reverse fork 89 described above. At the same time, the phase of the other engaging portion 85R formed at the end portion of the feed shaft 75 coincides with the phase of the fitting portion 87R formed corresponding thereto, and the feed shaft 75 has its axis line. It will be ready to move in the direction.
  • the engaging portion 85R having a non-circular cross section is fitted into the fitting portion 87R to prevent the rotation of the feed shaft 75, and the feed shaft 75 and the protruding portion 88 integrated with the feed shaft 75 are axially moved together with the sleeve 81. Move to.
  • the reverse fork 89 is attached to the support shaft 90 as described above and is configured to move in the axial direction together with the support shaft 90, the reverse fork 89 is pushed by the protruding portion 88 to the left in FIG.
  • the reverse idle gear 72 is moved between the reverse drive gear 62 and the reverse driven gear 69 formed on the hub sleeve 66 and meshes with these gears 62 and 69.
  • these gears 62 and 69 are connected via the reverse idle gear 72, the output shaft 31 is rotated in the direction opposite to the above-described forward state, and the reverse state is set.
  • the motor 34 rotates in the opposite direction to the case where the reverse state is set. Therefore, the sleeve 81 is moved to the right in FIG. 6 opposite to the case described above. In that case, initially, since the engaging portion 85R formed on the feed shaft 75 is fitted to the corresponding fitting portion 87R and the rotation of the feed shaft 75 is stopped, the feed shaft 75 and this The projecting portion 88 integral with the sleeve 81 recedes linearly in the axial direction together with the sleeve 81.
  • the forks 89 and 91 are linearly moved by the torque output from the motor 34, thereby allowing the neutral state, the forward state, and the reverse state.
  • the state can be set. Since the direction of the shift operation of the forward fork 91 from the neutral position to the forward position and the direction of the shift operation of the reverse fork 89 from the neutral position to the reverse position are the same, it is ensured for those shift operations.
  • the required axial space can be reduced. Therefore, according to this invention, the axial length of the continuously variable transmission as a whole can be shortened.
  • the forward / reverse switching mechanism 30 can set a neutral state in which torque transmission is interrupted and is connected to the output side of the driven pulley 3, the forward / reverse switching mechanism 30 is in a state where the vehicle is stopped. Is set to the neutral state, the transmission 1 can be rotated. Therefore, according to the above-described continuously variable transmission or the transmission control device thereof, when the vehicle is traveling in a state where the transmission ratio set in the transmission unit 1 is relatively small, the speed is reduced rapidly so that the transmission ratio is sufficient. Even if the vehicle stops before it increases, the forward / reverse switching mechanism 30 is set to the neutral state and the transmission unit 1 is rotated to change the gear ratio to a large gear ratio in preparation for re-start.
  • the torque of the motor 34 is transmitted to the drive gear 46 for speed change via the two-way clutch 36, and from here to the speed change gear 19 via the reduction gear mechanism 51 described above. Since the transmission gear 19 is integrated with one screw member (first screw member 14) constituting the thrust generating mechanism 20, the first screw member 14 rotates together with the transmission gear 19 to cause the thrust generating mechanism.
  • the thrust in the axial direction is generated by 20, and the movable sheave 7 moves in the axial direction by the thrust. That is, as the width of the belt winding groove 11 in the drive pulley 2 changes, the winding radius of the belt 4, that is, the gear ratio changes.
  • the motor 34 is a drive source that generates an operating force between the forward / reverse switching mechanism 30 and the transmission unit 1.
  • the number of operation target units is two, and the number of driving sources is one. Therefore, in the present invention, the number of required parts can be reduced and the overall configuration can be downsized.
  • the gear ratio can be increased to a gear ratio in preparation for restart when the vehicle is stopped.
  • This control is a control that can be called “belt return” in the belt type continuously variable transmission, and an example of the control will be described below.
  • the control can be performed by an electronic control unit (ECU) 95, and more specifically, calculation is performed by the ECU 95 based on the rotational speed and vehicle speed of each pulley 2 and 3, the detection signal of the sensor 90A, and the like. The calculation result is output to the two-way clutch 36, the motor 34, etc. as a control command signal.
  • FIG. 9 is a flowchart for explaining an example of the control, and the routine shown here is performed every predetermined short time by the ECU 95 when the vehicle is stopped or when the vehicle speed becomes a predetermined vehicle speed or less. It is executed repeatedly.
  • step S1 it is determined whether there is a belt return failure (step S1).
  • This determination is, in essence, determining whether or not the gear ratio is a gear ratio suitable for restarting. Therefore, the rotational speed of the drive pulley 2 and the rotational speed of the driven pulley 3 immediately before the vehicle stops.
  • the gear ratio can be calculated from the above and the gear ratio can be determined by determining whether or not the gear ratio is equal to or greater than a predetermined gear ratio for starting. If the belt return is good because the gear ratio is equal to or greater than the starting gear ratio, a negative determination is made in step S1. In this case, the routine of FIG. 9 is temporarily terminated without performing any particular control.
  • step S1 control for increasing the gear ratio, that is, belt return, is performed in preparation for re-start of the vehicle. Since this control is a control for rotating the transmission unit 1 even when the vehicle is stopped, the belt return is notified in advance so that the transmission unit 1 does not feel uncomfortable (step S2). ).
  • This notification may be any visual notification or auditory notification that can be felt by the passenger. For example, characters are displayed on the instrument panel, or a predetermined LED is turned on, and sound or vibration is generated. It may be an announcement.
  • step S3 the forward / reverse switching mechanism 30 is switched from the forward state (D) to the neutral state (N) (step S3).
  • step S4 the starting clutch 26 is switched from the released state to the engaged state (step S4).
  • the transmission unit 1 is not connected to the drive wheels 5 because the forward / reverse switching mechanism 30 is in the neutral state, and is thus rotated by the torque of the drive force source 27 when the start clutch 26 is engaged.
  • the wrapping radius of the belt 4 can be changed by the rotation of the pulleys 2 and 3. Therefore, in this state, the gear ratio is increased to a predetermined target gear ratio in preparation for restart (step S5).
  • the increase in the gear ratio up to the target gear ratio can be detected on the basis of the ratio of the rotational speeds of the pulleys 2 and 3, and after the determination that the actual gear ratio has reached the target gear ratio is established, the vehicle starts.
  • the clutch 26 is switched from the engaged state to the released state (step S6), and then the forward / reverse switching mechanism 30 is switched from the neutral state (N) to the forward state (D) (step S7).
  • This is a control for setting the operation state of the forward / reverse switching mechanism 30 to an operation state suitable for the shift position selected by the driver when the vehicle stops. Therefore, when the neutral position is selected when the vehicle is stopped, the forward / reverse switching mechanism 30 is maintained in the neutral state in step S7.
  • step S8 the notification executed in step S2 is canceled.
  • This control for notification need not be performed when the belt return control is not particularly uncomfortable.
  • the switching control and shift control of the forward / reverse switching mechanism 30 in the routine shown in FIG. 9 will be described more specifically.
  • the belt return is notified in the above step S2, and at the same time or before and after the above,
  • the two-way clutch 36 thus engaged is engaged with the forward / reverse switching side (second drive plate 44 side).
  • the motor 34 is connected to the forward / reverse switching mechanism 30, so that the motor 34 is driven to switch the forward / reverse switching mechanism 30 from the forward state (D) to the neutral state (N).
  • the specific operation in that case is as described above.
  • step S4 the two-way clutch 36 is engaged with the speed change side (first drive plate 43 side).
  • this can be performed by stopping energization of the electromagnetic coil 49 and turning it off.
  • the motor 34 since the motor 34 is connected to the transmission unit 1, the movable sheave 7 in the drive pulley 2 is separated from the fixed sheave 6 by the motor 34 while rotating the transmission unit 1 with the torque of the driving force source 27. , Increase the gear ratio.
  • step S6 after the start clutch 26 is released as the gear ratio increases to the target gear ratio, the two-way clutch 36 is engaged with the forward / reverse switching side (second drive plate 44 side). As a result, the motor 34 is connected to the forward / reverse switching mechanism 30, so that the motor 34 is driven to switch the forward / reverse switching mechanism 30 from the neutral state (N) to the forward state (D).
  • the specific operation in that case is as described above.
  • Two-way clutch (two-way-clutch), 37 ...
  • Motor shaft 46 drive gear for shifting, 48: output gear, 60: drive gear, 35A, 35B: electromagnetic clutch, 61: forward drive gear, 62 ... Reverse drive gear, 63 ... Forward driven gear, 64 ... Synchronizer, 65 ... Hub, 66 ... Hub sleeve, 67 ... Spline part, 68 ... Synchronizer ring, 69 ... Reverse driven gear, 70 ... Output gear, 71 ... Ring gear, 72 ... Reverse idle gear, 73 ... Reverse idle shaft, 74 ... Select shift mechanism, 75 ... Feed shaft, 76 ... Bevel gear, 77 ... Gear, 78 ... Fan gear, 79 ...
  • ECU Electronice control unit

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

La présente invention concerne un dispositif de commande de transmission pour une transmission à variation continue, doté d'une unité de transmission (1) permettant de faire varier en continu un rapport de transmission en faisant varier les largeurs de gorges d'enroulement de courroie (11, 12) dans des poulies (2, 3) sur lesquelles une courroie (4) est enroulée, ainsi qu'une unité de basculement vers l'avant/l'arrière (30) permettant de changer la direction de rotation d'un arbre de sortie (31) pour sortir un couple sur des roues d'entraînement (33) dans une direction avant et une direction arrière, le dispositif de commande de transmission étant également doté d'un actionneur (34) permettant de produire une force de fonctionnement pour faire varier le rapport de transmission et une force de fonctionnement pour basculer l'unité de basculement vers l'avant/l'arrière (30), ainsi qu'un mécanisme de basculement de transfert d'énergie motrice (35) permettant de lier sélectivement l'actionneur (34) à l'unité de transmission (1) et l'unité de basculement vers l'avant/l'arrière (30).
PCT/JP2014/077667 2013-10-24 2014-10-17 Dispositif de commande de transmission pour transmission à variation continue WO2015060209A1 (fr)

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JP2013221330 2013-10-24
JP2013-221330 2013-10-24

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02292570A (ja) * 1989-05-01 1990-12-04 Aisin Aw Co Ltd 変速操作装置
JPH10148256A (ja) * 1996-11-19 1998-06-02 Aichi Mach Ind Co Ltd 歯車式変速機の自動変速装置
JP2000035127A (ja) * 1998-07-17 2000-02-02 Aisin Seiki Co Ltd 同期かみあい式歯車変速機における電動式セレクト・シフト装置
JP2000240791A (ja) * 1999-02-22 2000-09-05 Honda Motor Co Ltd 変速機のギヤシフト機構
JP2004156658A (ja) * 2002-11-05 2004-06-03 Yamaha Motor Co Ltd エンジン
JP2011075097A (ja) * 2009-09-01 2011-04-14 Jtekt Corp 変速装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02292570A (ja) * 1989-05-01 1990-12-04 Aisin Aw Co Ltd 変速操作装置
JPH10148256A (ja) * 1996-11-19 1998-06-02 Aichi Mach Ind Co Ltd 歯車式変速機の自動変速装置
JP2000035127A (ja) * 1998-07-17 2000-02-02 Aisin Seiki Co Ltd 同期かみあい式歯車変速機における電動式セレクト・シフト装置
JP2000240791A (ja) * 1999-02-22 2000-09-05 Honda Motor Co Ltd 変速機のギヤシフト機構
JP2004156658A (ja) * 2002-11-05 2004-06-03 Yamaha Motor Co Ltd エンジン
JP2011075097A (ja) * 2009-09-01 2011-04-14 Jtekt Corp 変速装置

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