WO2016152286A1 - Boîte de vitesses automatique - Google Patents

Boîte de vitesses automatique Download PDF

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Publication number
WO2016152286A1
WO2016152286A1 PCT/JP2016/053730 JP2016053730W WO2016152286A1 WO 2016152286 A1 WO2016152286 A1 WO 2016152286A1 JP 2016053730 W JP2016053730 W JP 2016053730W WO 2016152286 A1 WO2016152286 A1 WO 2016152286A1
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WO
WIPO (PCT)
Prior art keywords
speed
dog
shaft
motor
clutch ring
Prior art date
Application number
PCT/JP2016/053730
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English (en)
Japanese (ja)
Inventor
山本　明弘
Original Assignee
ジヤトコ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ジヤトコ株式会社 filed Critical ジヤトコ株式会社
Priority to JP2017507574A priority Critical patent/JP6262400B2/ja
Publication of WO2016152286A1 publication Critical patent/WO2016152286A1/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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • 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
    • F16D11/00—Clutches in which the members have interengaging parts
    • F16D11/08—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially
    • F16D11/10—Clutches in which the members have interengaging parts actuated by moving a non-rotating part axially with clutching members movable only axially
    • 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
    • F16D41/00—Freewheels or freewheel clutches
    • F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F16H61/684—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings without interruption of drive
    • 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
    • F16H2003/0811—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 using unsynchronised 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
    • 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
    • F16H2003/0818—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 comprising means for power-shifting
    • 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
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds

Definitions

  • the present invention relates to an automatic transmission capable of shifting without interrupting torque transmission.
  • Patent Document 1 in a parallel two-shaft type continuously meshing transmission, in order to smoothly engage the dog clutch, a motor capable of rotating each shaft is provided, and the dog clutch is synchronized by synchronizing the dog clutch by driving the motor.
  • a device that achieves smooth meshing without incurring a bad defect is disclosed.
  • Japanese Patent Application Laid-Open No. 2012-127471 discloses an automatic transmission capable of shifting without interruption of torque transmission (hereinafter referred to as a seamless shift) in a parallel two-shaft type constant mesh transmission.
  • a seamless shift for example, when performing an upshift to the second speed during traveling at the first speed, if a second-speed clutch ring that meshes with the second-speed gear is engaged, a coasting torque acts on the first-speed gear. The coasting torque is used to generate an axial force in the meshing release direction in the first-speed clutch ring to achieve a seamless shift to the second speed.
  • Patent Document 1 By applying the technology shown in Patent Document 1 to an automatic transmission capable of achieving such a seamless shift and synchronizing the dog clutch driven by the motor, a smooth shift can be performed even when the vehicle is stopped. Be expected. However, since the shift time is very short in the running state, the change in the rotation speed of the input shaft of the transmission during the shifting in the running state is large. If a motor or the like is separately provided, the rotation speed of the motor is the same. Therefore, torque due to the inertia of the motor is generated, and this inertia torque is transmitted to the input shaft of the transmission to cause a shock at the time of upshifting.
  • An object of the present invention is to provide an automatic transmission capable of seamless shifting while avoiding a shock caused by an inertia torque of a motor at the time of upshifting.
  • the first low-speed gear and the first high-speed gear fixed to the first shaft on the input side or supported so as to be relatively rotatable, and fixed to the second shaft on the output side.
  • the second low-speed gear supported relative to the first low-speed gear and always engaged with the first low-speed gear and the second high-speed gear always engaged with the first high-speed gear and the first low-speed gear or the second 2 A low-speed clutch ring dog that meshes with a dog of a low-speed relative rotating body that is one of the low-speed gears, and when the torque acts on the low-speed clutch ring dog from the dog of the low-speed relative rotating body, the axial meshing release
  • the first shaft on the input side is rotationally driven by the motor to synchronize the meshing positions of the dogs, enabling shifting, and if necessary, the motor and the first shaft on the input side It becomes possible to cut off the power transmission relationship, and by eliminating the inertia of the motor as appropriate, it is possible to achieve a seamless shift that avoids a shock caused by the inertia of the motor at the time of upshifting.
  • FIG. 1 is a schematic system diagram illustrating an automatic transmission according to a first embodiment.
  • FIG. 2 is a schematic diagram illustrating the operation of the first dog clutch mechanism in the upshift from the first speed to the second speed in the automatic transmission of the first embodiment.
  • 4 is a time chart showing an upshift from the first speed to the second speed in the automatic transmission according to the first embodiment.
  • 3 is a flowchart illustrating motor drive control processing during downshift according to the first embodiment.
  • 4 is a time chart showing a downshift from the fourth speed to the first speed accompanying sudden deceleration in the automatic transmission according to the first embodiment.
  • FIG. 1 is a schematic system diagram showing an automatic transmission according to a first embodiment.
  • An automatic transmission 3 is connected to the engine output shaft 1 a of the engine 1 through a clutch 2.
  • the automatic transmission 3 includes an input-side first shaft 301 connected to the automatic transmission side of the clutch 2, and an output-side second shaft 302 arranged in parallel with the first shaft 301.
  • a first-speed drive gear 311 (corresponding to a first low-speed gear) that rotates integrally with the first shaft 301, a third-speed drive gear 331, and a first shaft 301 can rotate relative to the first shaft 301.
  • a supported second speed drive gear 321 (corresponding to a first high speed gear) and a fourth speed drive gear 341 are provided.
  • the first speed driven gear 312 (corresponding to the second low speed gear) supported so as to be rotatable relative to the second shaft 302, the third speed driven gear 332, and the second shaft 302 rotate integrally.
  • a second-speed driven gear 322 (corresponding to a second high-speed gear) and a fourth-speed driven gear 342 are included. Each driven gear always meshes with each drive gear.
  • the motor 7 is connected to the first shaft 301 via a gear 72 and a gear 331.
  • a one-way clutch 71 is provided between the gear 72 and the motor 7. The one-way clutch 71 is engaged when the first shaft 301 is driven to rotate forward, and transmits torque from the first shaft 301 to the motor 7 side. Further, it is released when the motor 7 is driven to rotate forward, and the torque transmission from the motor 7 to the first shaft 301 side is cut off. In other words, when the motor 7 is driven in reverse rotation, the one-way clutch 71 is engaged and the first shaft 301 is driven in reverse rotation.
  • the transmission controller 3 a determines a desired gear position based on various sensors and shift signals (not shown), and outputs a shift actuator drive signal to the shift actuator 30.
  • the shift actuator 30 is configured to be able to move the first shift fork 31 and the second shift fork 32 in the axial direction.
  • the shift actuator 30 controls the position of a shift drum having a groove engaged with each shift fork on the outer periphery by a motor.
  • the first shift fork 31 and the second shift fork 32 have positioning mechanisms 31b and 32b that can be biased to predetermined positions in the axial direction.
  • the positioning mechanisms 31b and 32b allow a slight movement in the axial direction in accordance with a change in the meshing position of the dog in accordance with the torque acting direction described later after each shift fork is positioned by the shift actuator 30.
  • a holding force at a predetermined axial position is applied to each shift fork at a plurality of positions. Details will be described later.
  • the first speed driven gear 312 and the third speed driven gear 332 are arranged adjacent to each other.
  • the second speed drive gear 321 and the fourth speed drive gear 341 are disposed adjacent to each other.
  • a side surface of the first driven gear 312 facing the third driven gear 332 has a first dog 312 a extending in the axial direction.
  • a third dog 332 a is provided on the side surface of the third driven gear 332 facing the first driven gear 312.
  • a side surface of the second drive gear 321 facing the fourth drive gear 341 has a second dog 321a extending in the axial direction.
  • a fourth dog 341 a is provided on the side surface of the fourth drive gear 341 facing the second drive gear 321.
  • the first and second dog clutch mechanisms DG1 and DG2 are provided between the first speed driven gear 312 and the third speed driven gear 332, and between the second speed drive gear 321 and the fourth speed drive gear 341.
  • the first dog clutch mechanism DG1 is installed on the outer periphery of the first clutch ring cam 400 fixedly installed on the second shaft 302 and meshes with the first shift fork 31 so as to be relatively rotatable.
  • a first clutch ring 33 is provided.
  • On the outer periphery of the first clutch ring cam 400 there is a V-shaped groove 401 formed on the outer peripheral surface.
  • the V-shaped groove 401 includes a first speed side inclined groove 401 a that is inclined toward the positive rotation direction side of the first shaft 301 and a third speed side inclined groove 401 c.
  • the end of the first clutch ring 33 facing the first speed driven gear 312 side has a holding groove 401b connected to the first speed side inclined groove 401a and parallel to the axial direction.
  • an end portion of the first clutch ring 33 facing the third speed driven gear 332 side has a holding groove 401d connected to the third speed side inclined groove 401c and parallel to the axial direction.
  • the second dog clutch mechanism DG2 also includes the second clutch ring 34, the second clutch ring cam 500, the V-shaped groove 501, the second speed side inclined groove 501a, and the fourth speed side inclined groove 501c similar to the first dog clutch mechanism DG1. And holding grooves 501b and 501d. Since the configuration is the same as that of the first dog clutch mechanism DG1, description thereof is omitted.
  • the first clutch ring 33 includes a cylindrical member 33e that can move relative to the outer periphery of the first clutch ring cam 400, and a first sleeve 33a that is expanded in diameter from the axial center to the outer diameter side of the cylindrical member 33e.
  • the first sleeve 33 a is a disk-shaped member that can be applied to the shift fork 31 while being held rotatably relative to the shift fork 31.
  • the first clutch ring 33 includes a first-speed first clutch ring dog 33c extending from the first sleeve 33a in the axial direction of the side facing the first-speed driven gear 312 and an axial direction of the side facing the third-speed driven gear 332
  • the second clutch ring 34 includes a cylindrical member 34e that can move relative to the outer periphery of the second clutch ring cam 500, and a second diameter that is expanded from the axial center to the outer diameter side of the cylindrical member 34e. It has a sleeve 34a.
  • the second sleeve 34 a is a disk-like member that can be applied to the shift fork 32 and an axial force while being held by the shift fork 32 so as to be relatively rotatable.
  • the second clutch ring 34 includes a second-speed second clutch ring dog 34c extending from the second sleeve 34a in the axial direction of the side surface facing the second-speed drive gear 321, and a side shaft facing the fourth-speed gear 341.
  • FIG. 2 is a schematic diagram illustrating the operation of the first dog clutch mechanism in the upshift from the first speed to the second speed in the automatic transmission of the first embodiment.
  • the first shift fork 31 is moved to the left side in FIG.
  • the guide first protrusion 33b is positioned in the holding groove 401b and the coasting torque is applied before the torque is applied to the first speed driven gear 312.
  • it does not move in the axial direction.
  • the tooth surface of the first clutch ring dog 33c for the first speed of the first clutch ring 33 is engaged with the first dog 312a of the first speed driven gear 312 when the driving torque is applied. Is formed with an inclined surface 33c1.
  • the first clutch ring 33 is lifted toward the meshing release side along the inclined surface 33 c 1.
  • the first guide protrusion 33b moves from the holding groove 401b to the position of the first-speed inclined groove 401a.
  • the meshing between the first dog 312a of the first-speed driven gear 312 and the first-speed clutch ring dog 33c is continued, and the torque is transmitted.
  • the positioning mechanism 31b described above operates. That is, the axial position of the first clutch ring 33 after the lift is stably held while allowing the first shift fork 31 to move slightly in the axial direction along with the lift.
  • the second speed drive gear 321 and the second speed second clutch ring dog 34c are engaged, and the first speed driven gear 312 is utilized by utilizing the coasting torque accompanying the interlock state generated by this engagement.
  • the engagement with the first clutch ring 33 is released. Therefore, the torque transmission state can always be maintained during the upshift.
  • Such a shift operation is called seamless shift.
  • the downshift is also performed by the same action, and for details of the shift operation, see, for example, Japanese Patent Application Laid-Open No. 2012-127471.
  • FIG. 3 is a time chart showing an upshift from the first speed to the second speed in the automatic transmission according to the first embodiment.
  • the gear is immediately shifted if the engagement between the drive gear and the clutch ring is established at the post-shift gear stage. Assuming that the first shaft 301 was rotating at, for example, 1000 rpm at the first speed, and assuming that the second dog 321a of the second-speed drive gear 321 is rotating at, for example, 500 rpm from the relationship between the gear ratios of the first and second speeds. To do.
  • the motor 7 is always rotating integrally with the first shaft 301, when the first shaft 301 is decelerated all at once, it is necessary to decelerate the rotation speed of the motor 7 as well. At this time, the influence of the motor inertia is extremely large, and there is a problem that a shock due to the inertia torque of the motor 7 occurs at the time of shift up.
  • the one-way clutch 71 is provided, when the coasting torque is applied to the first shaft 301, the one-way clutch 71 is automatically released, and the inertia of the motor 7 does not affect the shift. .
  • FIG. 4 is a flowchart illustrating motor drive control processing during downshift according to the first embodiment.
  • the automatic transmission according to the first embodiment needs to be synchronized during rotation in order to engage the dog. Therefore, in the first embodiment, when the downshift is performed by the transmission controller 3a, the downshift is performed by reversely rotating the motor 7 after the vehicle is stopped.
  • step S1 it is determined whether or not the downshift is completed.
  • step S4 it is determined whether or not the motor rotational speed is 0, that is, whether or not the motor rotational speed has sufficiently decreased after the vehicle stops. If the motor rotational speed is 0, the process proceeds to step S3. Ends this control flow.
  • step S3 the motor 7 is driven in reverse rotation. Thereby, since the one-way clutch 71 can be fastened and the 1st shaft 301 can be rotated, a downshift can be continued even after a vehicle stops.
  • step S4 it is determined whether or not the motor 7 is being driven in reverse rotation. If the motor 7 is in reverse rotation, the process proceeds to step S5 to stop the motor drive. Otherwise, this control flow is ended.
  • FIG. 5 is a time chart showing a downshift from the fourth speed to the first speed accompanying sudden deceleration in the automatic transmission according to the first embodiment.
  • the coasting torque acts inside the automatic transmission, so that it functions as a generator by the driving torque of the engine 1.
  • the one-way clutch 71 between the motor 7 and the first shaft 301 is in a released state. Therefore, the rotation speed of the motor 7 gradually decreases according to the inertia.
  • the clutch 2 is released. Note that the clutch 2 continues to be released when performing a continuous shift or when the vehicle is decelerated to stop the vehicle.
  • the rotation of the first shaft 301 also stops, so that a downshift using the rotation of the first shaft 301 cannot be performed.
  • the motor 7 has a slight rotational speed due to the influence of inertia.
  • first-speed drive gear 311 first low-speed gear
  • second-speed drive gear 321 first high-speed gear
  • a first-speed driven gear 312 second low-speed gear
  • a first speed first clutch ring dog 33c that meshes with the first dog 312a (the dog of the low-speed relative rotating body that is either the first low-speed gear or the second low-speed gear) by the movement toward the axial meshing side.
  • a V-shaped groove 401 of the first clutch ring cam 400 that moves to the axial engagement release side when torque is applied from the first dog 312a to the first speed first clutch ring dog 33c.
  • a first clutch ring 33 (low speed clutch ring) having a first guide projection 33b (low speed side guide portion);
  • the second clutch ring dog 34c for the second speed that meshes with the second dog 321a (the dog of the high-speed relative rotating body that is either the first high-speed gear or the second high-speed gear) by the movement toward the axial meshing side.
  • a V-shaped groove 501 of the second clutch ring cam 500 that moves to the axial meshing release side when torque is applied from the second dog 321a to the second clutch ring dog 34c for the second speed.
  • a second clutch ring 34 (high speed clutch ring) having a guide second protrusion 34b (high speed side guide portion);
  • a first shift fork 31 capable of moving the first clutch ring 33 and the second clutch ring 34 in the axial meshing direction by movement toward the axial meshing side and allowing movement toward the axial meshing release side;
  • a second shift fork 32 and a shift actuator 30 ;
  • a motor 7 capable of rotationally driving the first shaft 301;
  • a one-way clutch 71 (fastening means) capable of connecting / disconnecting between the first shaft 301 and the motor 7; Equipped with.
  • the one-way clutch 71 is released when the motor 7 rotates forward and is engaged when the motor 7 rotates backward. At the time of seamless shift, it is necessary to decelerate the rotation speed of the motor 7 at a stretch. The influence of the motor inertia is extremely large, and there is a problem that an excessive load is generated inside the transmission. However, since the one-way clutch 71 is provided, when the coasting torque is applied to the first shaft 301, the one-way clutch 71 is automatically released, and the inertia of the motor 7 does not affect the shift. .
  • the transmission controller 3a drives the motor 7 after the rotation of the first shaft 301 is stopped, and shifts while driving the first shaft 301 in the reverse rotation. Therefore, the downshift can be continued even after the vehicle is stopped.
  • the present invention is not limited to the above-described embodiment, and the present invention may be applied to an automatic transmission having another configuration.
  • a driven gear that is a relative rotating body is arranged on the second shaft 302 and a dog clutch mechanism that can selectively fix the driven gear to the second shaft 302 is shown.
  • the first shaft 301 may be provided on both the first shaft 301 and the second shaft 302 in combination with each other.
  • the present invention can be applied not only to the fourth forward speed but also to the second forward speed and further automatic transmissions with multiple stages.
  • the motor 7 and the first shaft 301 are connected via the one-way clutch 71 has been described.
  • not only the one-way clutch 71 but also a two-way clutch capable of switching the locking direction may be employed, or a clutch capable of switching engagement / release may be applied to perform engagement control depending on the situation. Good.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne une boîte de vitesses automatique (3) capable d'obtenir un changement de vitesse continu qui comprend : un moteur (7) capable d'entraîner un premier arbre (301) côté entrée ; et un embrayage unidirectionnel (71) capable de connecter/déconnecter le premier arbre (301) et le moteur (7). Grâce à cette configuration, il est possible d'obtenir un changement de vitesse continu qui permet d'éviter les chocs qui se produisent pendant un passage à la vitesse supérieure et qui sont provoqués par le couple d'inertie du moteur (7), un tel couple étant destiné à la synchronisation d'engagement d'un embrayage à griffes (DG1 ou DC2).
PCT/JP2016/053730 2015-03-20 2016-02-09 Boîte de vitesses automatique WO2016152286A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2017507574A JP6262400B2 (ja) 2015-03-20 2016-02-09 自動変速機

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015-057112 2015-03-20
JP2015057112 2015-03-20

Publications (1)

Publication Number Publication Date
WO2016152286A1 true WO2016152286A1 (fr) 2016-09-29

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PCT/JP2016/053730 WO2016152286A1 (fr) 2015-03-20 2016-02-09 Boîte de vitesses automatique

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JP (1) JP6262400B2 (fr)
WO (1) WO2016152286A1 (fr)

Cited By (11)

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CN106641121A (zh) * 2017-02-15 2017-05-10 苏州萨伯工业设计有限公司 四挡变速传动方法
CN106678340A (zh) * 2017-02-15 2017-05-17 苏州萨伯工业设计有限公司 六挡变速箱
CN106678311A (zh) * 2017-02-15 2017-05-17 苏州萨伯工业设计有限公司 农用机械集成四挡传动方法
CN106763540A (zh) * 2017-02-15 2017-05-31 苏州萨伯工业设计有限公司 四挡变速箱
CN107032062A (zh) * 2017-06-15 2017-08-11 常州百擎智能工程有限公司 变速传动机构及其双螺杆给料机
JP2018071628A (ja) * 2016-10-27 2018-05-10 ジヤトコ株式会社 自動変速機
JP2018076905A (ja) * 2016-11-08 2018-05-17 ジヤトコ株式会社 自動変速機
WO2018173488A1 (fr) * 2017-03-22 2018-09-27 Kabushiki Kaisha Toyota Chuo Kenkyusho Embrayage à griffes et transmission
CN108730510A (zh) * 2017-04-18 2018-11-02 罗朝明 一种无动力中断变速器
CN112224011A (zh) * 2020-10-23 2021-01-15 东风汽车集团有限公司 一种单电机混合动力变速系统
CN112937284A (zh) * 2021-03-24 2021-06-11 何亚芳 混合动力传动装置

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JP2005121219A (ja) * 2003-09-26 2005-05-12 Ntn Corp 車両用変速機
JP2010242834A (ja) * 2009-04-03 2010-10-28 Honda Motor Co Ltd トランスミッション
JP2012127471A (ja) * 2010-12-17 2012-07-05 Ikeya Formula Kk トランスミッション
JP2014168966A (ja) * 2011-05-24 2014-09-18 Jatco Ltd ハイブリッド車両の変速制御装置

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Publication number Priority date Publication date Assignee Title
JP2005121219A (ja) * 2003-09-26 2005-05-12 Ntn Corp 車両用変速機
JP2010242834A (ja) * 2009-04-03 2010-10-28 Honda Motor Co Ltd トランスミッション
JP2012127471A (ja) * 2010-12-17 2012-07-05 Ikeya Formula Kk トランスミッション
JP2014168966A (ja) * 2011-05-24 2014-09-18 Jatco Ltd ハイブリッド車両の変速制御装置

Cited By (12)

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JP2018076905A (ja) * 2016-11-08 2018-05-17 ジヤトコ株式会社 自動変速機
CN106641121A (zh) * 2017-02-15 2017-05-10 苏州萨伯工业设计有限公司 四挡变速传动方法
CN106678340A (zh) * 2017-02-15 2017-05-17 苏州萨伯工业设计有限公司 六挡变速箱
CN106678311A (zh) * 2017-02-15 2017-05-17 苏州萨伯工业设计有限公司 农用机械集成四挡传动方法
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US10883547B2 (en) * 2017-03-22 2021-01-05 Kabushiki Kaisha Toyota Chuo Kenkyusho Dog clutch and transmission
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