WO2009096385A1 - Groupe moteur - Google Patents

Groupe moteur Download PDF

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Publication number
WO2009096385A1
WO2009096385A1 PCT/JP2009/051260 JP2009051260W WO2009096385A1 WO 2009096385 A1 WO2009096385 A1 WO 2009096385A1 JP 2009051260 W JP2009051260 W JP 2009051260W WO 2009096385 A1 WO2009096385 A1 WO 2009096385A1
Authority
WO
WIPO (PCT)
Prior art keywords
movable
pulley
driven
driven shaft
pulley half
Prior art date
Application number
PCT/JP2009/051260
Other languages
English (en)
Japanese (ja)
Inventor
Kaoru Hanawa
Yutaka Imoto
Original Assignee
Honda Motor Co., Ltd.
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 Honda Motor Co., Ltd. filed Critical Honda Motor Co., Ltd.
Publication of WO2009096385A1 publication Critical patent/WO2009096385A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • 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
    • 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
    • F16H63/067—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 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/52—Pulleys or friction discs of adjustable construction
    • F16H55/56—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable
    • F16H55/563—Pulleys or friction discs of adjustable construction of which the bearing parts are relatively axially adjustable actuated by centrifugal masses
    • 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
    • F16H61/66—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 continuously variable gearings
    • F16H61/662—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 continuously variable gearings with endless flexible members
    • F16H61/66254—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 continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling
    • F16H61/66268—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 continuously variable gearings with endless flexible members controlling of shifting being influenced by a signal derived from the engine and the main coupling using purely mechanical sensing or control 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
    • 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
    • F16H61/66—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 continuously variable gearings
    • F16H61/662—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 continuously variable gearings with endless flexible members
    • F16H61/66272—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 continuously variable gearings with endless flexible members characterised by means for controlling the torque transmitting capability of the gearing

Definitions

  • the present invention relates to a power unit including a belt type continuously variable transmission.
  • a belt-type continuously variable transmission provided in a path for transmitting the rotational force of a crankshaft to drive wheels is known as disclosed in Patent Document 1.
  • This belt-type continuously variable transmission is composed of a belt wound between a drive pulley unit and a driven pulley unit, and performs a speed change action by changing a winding diameter of the belt.
  • the belt-type continuously variable transmission disclosed in Patent Document 1 includes an input shaft side transmission pulley, an output shaft side transmission pulley, and a belt wound around these pulleys.
  • the output shaft side transmission pulley includes an output side fixed pulley and an output side movable pulley.
  • the movable pulley piece on the output side moves away from the fixed pulley piece on the output side so that the belt winding diameter decreases.
  • the coil spring is compressed following the movement of the output side pulley piece, and the reaction force of the coil spring increases in proportion to the amount of compression.
  • the reaction force by the coil spring increases, the side pressure acting on the side edge of the belt increases. At this time, the transmission efficiency of the transmission may be reduced.
  • a centrifugal force imparting material is provided on the output side shifting pulley side. That is, the centrifugal force increases at a high speed, and the centrifugal force imparting material moves outward in the radial direction.
  • the extension part of the output side movable pulley piece moves away from the output side fixed pulley piece.
  • a force in a direction away from the output side fixed pulley piece is applied to the output side movable pulley piece.
  • the force applied to the output side movable pulley piece plays a role of relaxing the pressing force to the belt by the coil spring. As a result, a reduction in transmission efficiency of the transmission can be suppressed.
  • the said coil spring is arrange
  • An object of the present invention is to provide a power unit including a belt-type continuously variable transmission that does not protrude greatly to only one side of the vehicle width.
  • a power unit that performs belt-type continuously variable transmission, a driving pulley that transmits a rotational force from a crankshaft, and a driven shaft that transmits a rotational driving force from the crankshaft to driving wheels.
  • the driven pulley is provided with a fixed pulley half body in which movement of the driven shaft in the axial direction is restricted, and movement of the driven shaft in the axial direction is possible.
  • a centrifugal mechanism that applies a thrust force against the biasing force of the biasing means to the movable pulley half corresponding to the rotational speed of the biasing means, the biasing means and the centrifugal mechanism in the axial direction of the driven shaft
  • the driven pulley Power unit that is arranged to be distributed as a quasi on both sides of the driven pulley is provided.
  • the centrifugal mechanism and the urging means are distributed and arranged on both sides of the driven pulley, so that only one side of the driven pulley unit is enlarged, that is, it is prevented from projecting to only one side of the vehicle width. be able to.
  • the movable pulley half includes a movable umbrella portion that contacts one side surface of the belt, and a movable cylinder portion that extends from the movable umbrella portion in the direction of the urging means along the driven shaft.
  • a thrust force against the urging force of the urging means is applied to the movable pulley half.
  • the centrifuge mechanism since the centrifuge mechanism is connected to the movable side cylinder, the outer diameter of the centrifuge mechanism can be reduced, and the centrifuge mechanism can be easily made compact.
  • the fixed pulley half is fixed to the other side surface of the belt, a fixed umbrella portion extending from the fixed umbrella portion in the direction of the urging means along the driven shaft, and inside the movable cylinder portion.
  • a fixed-side cylinder portion having a long-hole-like cam groove, and at least one pin protrudes from the movable-side cylinder portion toward the outer peripheral surface of the driven shaft and passes through the cam groove.
  • FIG. 1 is a schematic diagram of a power unit according to a first embodiment of the present invention
  • FIG. 2 is an enlarged sectional view taken along line 2-2 in FIG.
  • FIG. 2 is a cross-sectional view taken along line 3-3 in FIG.
  • FIG. 3 is an exploded perspective view of the driven pulley shown in FIG. Sectional drawing which showed the action
  • the power unit 10 of the first embodiment shown in FIG. 1 is provided in a power transmission path for transmitting the rotational force of the crankshaft 12 driven by the piston 11 to the drive wheels W, and includes a drive pulley 13 and a driven pulley 15.
  • the basic elements are the driven pulley unit 14 provided and the belt 16 wound between the driving pulley 13 and the driven pulley 15.
  • a final reduction mechanism 17 including a driving pulley 13, a driven pulley 15, a belt 16 and a plurality of gears is collectively stored in a power unit case 18, and an engine 19 is mounted on the front end of the power unit case 18. .
  • the driven pulley unit 14 includes a driven pulley 15, a centrifugal mechanism 20 provided on the driven shaft 21, and a centrifugal clutch mechanism 50.
  • the driven pulley 15 includes a fixed pulley half 30 that does not move in the longitudinal direction of the driven shaft 21, and a movable pulley that is movable relative to the longitudinal direction of the driven shaft 21 so as to move away from or approach the fixed pulley half 30. It consists of half body 40.
  • the centrifugal mechanism 20 includes a fixed inclined plate 22 fixed to the driven shaft 21, and is disposed to face the fixed inclined plate 22 via steel balls 23, 23 and moves along the driven shaft 21.
  • a movable tilting plate 24 that can be arranged, an inner cylinder 25 extending from the movable tilting plate 24 along the driven shaft 21, and the inner cylinder 25 supported on the driven shaft 21 so as to be rotatable and axially movable. It consists of a needle bearing 26.
  • the needle bearing 26 is provided on the inner cylinder 25 so as to be slidable with respect to the driven shaft 21, or is provided on the driven shaft 21 slidable with respect to the inner cylinder 25.
  • the fixed pulley half 30 extends from the fixed umbrella 31 so as to cover the inner cylinder 25 and contacts the belt 16, and the tip is rotatable to the driven shaft 21 via the radial bearing 32. And a fixed-side cylinder portion 33 that is supported so as not to move in the longitudinal direction of the driven shaft 21.
  • Reference numeral 34 is an oil seal interposed between the base portion of the fixed-side tube portion 33 and the inner tube 25.
  • the movable pulley half 40 extends so as to cover the movable side umbrella portion 41 that contacts the belt 16 and the fixed side cylindrical portion 33 from the movable side umbrella portion 41, is rotatable about the driven shaft 21, and is the longitudinal length of the driven shaft 21.
  • the movable side cylinder part 42 supported by the fixed side cylinder part 33 so as to be movable in the direction, and the compression spring (biasing means) 43 that urges the movable side umbrella part 41 to the fixed side umbrella part 31.
  • the biasing means may be a torsion spring in addition to the compression spring 43. 44 and 45 are oil seals.
  • projecting portions 46 and 46 are formed to project radially inward, and these projecting portions 46 and 46 are in sliding contact with the outer peripheral surface of the fixed side cylindrical portion 33.
  • the centrifugal clutch mechanism 50 is provided at the distal end portion of the fixed side cylindrical portion 33 which is a position opposite to the position where the centrifugal mechanism 20 is provided with respect to the position of the belt 16.
  • the centrifugal clutch mechanism 50 includes a cup member 51 provided on the driven shaft 21, arm members 52, 52 extending from the fixed-side cylinder portion 33 toward the outer periphery of the cup member 51, and these arm members 52. , 52 is provided at weights 53 and 53 which are swingably provided at the front end portion, and which swing when the applied centrifugal force increases and contact the cup member 51 to transmit power.
  • the cylinder 54 to which the compression spring 43 is attached is fitted on the outer periphery of the movable side cylinder portion 42.
  • the cylindrical body 54 has a spring receiving portion 55 at one end near the movable side umbrella portion 41.
  • the spring receiving portion 55 protrudes in a bowl shape toward the outside of the diameter of the cylindrical body 54.
  • the compression spring 43 is attached to the outer periphery of the cylindrical body 54 along the longitudinal direction of the driven shaft 21.
  • the compression spring 43 is mounted on the outer periphery of the cylindrical body 54 so as to be interposed between the arm members 52, 52 of the centrifugal clutch mechanism 50 and the spring receiving portion 55, and the movable pulley half 40 is fixed to the fixed pulley half. Always energized to move in 30 directions. Thus, since the other end of the compression spring 43 is received by the arm members 52, 52, a spring receiving portion for receiving the other end or a dedicated member is not required.
  • the movable side cylinder part 42 Since the movable side cylinder part 42 has projecting parts 46 and 46 projecting inward in the diameter on the inner peripheral surface thereof, as shown in FIG. 3, it has a sufficient gap.
  • the fixed side cylinder portion 33 is fitted.
  • the fixed-side cylinder portion 33 is fitted into the inner cylinder 25 of the centrifugal mechanism 20.
  • the fixed side cylinder portion 33 has a cam groove 58.
  • the movable side cylinder part 42 has a pin 56 protruding from the movable side cylinder part 42 toward the driven shaft 21.
  • the tip portion 57 of the pin 56 passes through the cam groove 58 and is connected to the inner cylinder 25. Therefore, the movable side cylinder portion 42 is mechanically connected to the inner cylinder 25 via the pin 56.
  • the cylindrical body 54 receives the compression spring 43 and prevents the pin 56 from coming out radially outward by centrifugal force.
  • the cam groove 58 is provided obliquely so as to draw a spiral in the fixed-side cylinder portion 33.
  • Such a mechanism is called a torque cam mechanism because it uses the cam groove skillfully. That is, the torque cam mechanism includes a cam groove 58 formed in the fixed-side cylinder portion 33 and a pin 56 extending from the movable-side cylinder portion 42.
  • the present invention is characterized in that the inner cylinder 25 is mechanically connected to the tip portion 57 of the pin 56 constituting the torque cam mechanism.
  • the tip portion 57 of the pin 56 and the inner cylinder 25 may be in contact with each other.
  • the compression spring 43 is disposed so as to be at a position opposite to the position of the centrifugal mechanism 20 provided near the drive wheel W with respect to the belt 16.
  • the amount of protrusion from the driven pulley unit 14 can be reduced. That is, an increase in the size of only one side of the driven pulley unit 14 can be suppressed.
  • the movable tilting plate 24 of the centrifugal mechanism 20 is connected to the movable side cylinder portion 42 via the inner cylinder 25 and the pin 56. Since the inner cylinder 25 has a small diameter, both the inner diameter and the outer diameter of the movable tilting plate 24 can be reduced. That is, if the centrifuge mechanism 20 is connected to the movable cylinder portion 42 via the pin 56, the inner diameter D1 of the centrifuge mechanism 20 can be reduced. If the inner diameter D1 is reduced, the outer diameter D2 of the centrifugal mechanism 20 can be reduced, and the centrifugal mechanism 20 can be easily made compact.
  • the centrifugal mechanism 20 is connected to the tip of the pin (tip portion 57) via the pin 56 and the cam groove 58.
  • the existing torque cam mechanism can be used as it is for the pin 56 and the cam groove 58. As a result, the number of parts for connecting the centrifugal mechanism 20 to the movable cylinder portion 42 can be reduced.
  • the power unit 10 shown in FIG. 1 is suitable for a scooter type vehicle in which the power unit 10 swings up and down together with the drive wheels 13.
  • the present invention can also be applied to a non-oscillating power unit.
  • Such an example will be described as a second embodiment with reference to FIG.
  • the same members as those in the first embodiment shown in FIG. 1 are denoted by the same reference numerals, and the description thereof is omitted.
  • FIG. 6 shows a non-oscillating power unit 10B.
  • a drive sprocket 62 is attached to the output shaft 61 of the final reduction mechanism 17
  • a driven sprocket 64 is attached to the axle 63 of the drive wheel W
  • the drive chain 65 is wound between the two sprockets 62, 64 as shown in FIG. This is different from the first embodiment.
  • the drive chain 65, the driven sprocket 64, the axle 63, and the driving wheel W are swung in the front and back direction of the drawing.
  • the power unit 10B can be fixedly attached to the vehicle body frame.
  • the non-oscillating power unit 10B can be disposed in front of the drive wheel W.
  • the compression spring 43 and the centrifugal clutch mechanism 50 are arranged on the right side of the belt 16 in the drawing, and the centrifugal mechanism 20 and the final reduction mechanism 17 are arranged on the left side of the belt 16 in the drawing.
  • the right overhang L1 and the left overhang L2 can be approximated with respect to the center axis 66 in the vehicle width direction passing through the center of the drive wheel W.
  • first and second embodiments are applied to a two-wheeled vehicle
  • the first and second embodiments can be applied to a three-wheeled vehicle and a four-wheeled vehicle, and can be applied to a general vehicle.
  • the power unit of the present invention is suitable for a motorcycle.

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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 groupe moteur pourvu d'une transmission à variation continue à courroie. Le groupe moteur comporte un ressort de compression (43) pour pousser une moitié de poulie mobile (40) d'une poulie entraînée (14) vers une moitié de poulie stationnaire (30), et possède également un mécanisme centrifuge (20) pour appliquer une force de poussée, qui agit contre la force de poussée du ressort de compression, sur la moitié de poulie mobile. Le ressort de compression (43) et le mécanisme centrifuge (20) sont agencés sur des côtés opposés de la poulie entraînée pour minimiser la largeur du groupe moteur mesurée dans le sens de la largeur du véhicule.
PCT/JP2009/051260 2008-01-31 2009-01-27 Groupe moteur WO2009096385A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008022032A JP2009180356A (ja) 2008-01-31 2008-01-31 パワーユニット
JP2008-022032 2008-01-31

Publications (1)

Publication Number Publication Date
WO2009096385A1 true WO2009096385A1 (fr) 2009-08-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2009/051260 WO2009096385A1 (fr) 2008-01-31 2009-01-27 Groupe moteur

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JP (1) JP2009180356A (fr)
TW (1) TW200949105A (fr)
WO (1) WO2009096385A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2491440A1 (es) * 2014-05-09 2014-09-05 Xavier PALLARÈS MATEOS Sistema axial de transmisión
ITUB20156910A1 (it) * 2015-12-10 2017-06-10 Piaggio & C Spa Dispositivo di trasmissione a variazione continua con dispositivo di variazione della curva di cambiata
WO2017186222A1 (fr) * 2016-04-27 2017-11-02 Schaeffler Technologies AG & Co. KG Transmission à variation continue
WO2019111131A1 (fr) * 2017-12-05 2019-06-13 Piaggio & C. S.P.A. Dispositif de transmission à variation continue avec dispositif de réglage
US20230030435A1 (en) * 2021-07-30 2023-02-02 Textron Inc. Continuously variable transmission having tunable acceleration and deceleration

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6501224B2 (ja) * 2015-05-22 2019-04-17 株式会社エクセディ プーリ装置
JP2019002518A (ja) * 2017-06-16 2019-01-10 ジヤトコ株式会社 トルクカム装置及びベルト式無段変速機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5236257A (en) * 1975-09-16 1977-03-19 Toyota Motor Corp Belt type automatic transmission
JPH0552245A (ja) * 1991-08-22 1993-03-02 Mitsuboshi Belting Ltd ベルト式無段変速装置及び変速プーリ
JPH08178004A (ja) * 1994-12-27 1996-07-12 Suzuki Motor Corp Ｖベルト式自動変速装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5236257A (en) * 1975-09-16 1977-03-19 Toyota Motor Corp Belt type automatic transmission
JPH0552245A (ja) * 1991-08-22 1993-03-02 Mitsuboshi Belting Ltd ベルト式無段変速装置及び変速プーリ
JPH08178004A (ja) * 1994-12-27 1996-07-12 Suzuki Motor Corp Ｖベルト式自動変速装置

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2491440A1 (es) * 2014-05-09 2014-09-05 Xavier PALLARÈS MATEOS Sistema axial de transmisión
WO2015169991A1 (fr) * 2014-05-09 2015-11-12 Automatic Transmission & Innovation, S.A. Système axial de transmission
ITUB20156910A1 (it) * 2015-12-10 2017-06-10 Piaggio & C Spa Dispositivo di trasmissione a variazione continua con dispositivo di variazione della curva di cambiata
WO2017098379A1 (fr) * 2015-12-10 2017-06-15 Piaggio & C. S.P.A. Dispositif de transmission à variation continue comprenant un dispositif de variation de la courbe du passage de vitesse
TWI721059B (zh) * 2015-12-10 2021-03-11 義大利商比雅久股份有限公司 具有變動曲線的裝置之無段傳動裝置
US11359711B2 (en) 2015-12-10 2022-06-14 Piaggio & C. S.P.A. Continuously variable transmission device with a device for varying the gear shift curve
WO2017186222A1 (fr) * 2016-04-27 2017-11-02 Schaeffler Technologies AG & Co. KG Transmission à variation continue
WO2019111131A1 (fr) * 2017-12-05 2019-06-13 Piaggio & C. S.P.A. Dispositif de transmission à variation continue avec dispositif de réglage
US20230030435A1 (en) * 2021-07-30 2023-02-02 Textron Inc. Continuously variable transmission having tunable acceleration and deceleration
US11732786B2 (en) * 2021-07-30 2023-08-22 Textron Innovations Inc. Continuously variable transmission having tunable acceleration and deceleration

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Publication number Publication date
TW200949105A (en) 2009-12-01
JP2009180356A (ja) 2009-08-13

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