WO2015076333A1 - Ｖベルト式無段変速機 - Google Patents

Ｖベルト式無段変速機 Download PDF

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Publication number
WO2015076333A1
WO2015076333A1 PCT/JP2014/080766 JP2014080766W WO2015076333A1 WO 2015076333 A1 WO2015076333 A1 WO 2015076333A1 JP 2014080766 W JP2014080766 W JP 2014080766W WO 2015076333 A1 WO2015076333 A1 WO 2015076333A1
Authority
WO
WIPO (PCT)
Prior art keywords
pulley
shaft
movable pulley
axial direction
arm member
Prior art date
Legal status (The legal status 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 status listed.)
Ceased
Application number
PCT/JP2014/080766
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
卓 板垣
嘉昭 漁野
和也 赤石
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing 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 NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Priority to US15/038,305 priority Critical patent/US20160290450A1/en
Priority to EP14864005.5A priority patent/EP3073150A4/en
Priority to CN201480056973.5A priority patent/CN105683623A/zh
Publication of WO2015076333A1 publication Critical patent/WO2015076333A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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

Definitions

  • the present invention relates to a V-belt type continuously variable transmission that rotates a driven pulley by changing the winding diameter of a V-belt due to a change in groove width of a driving pulley and a driven pulley.
  • V-belt type continuously variable transmissions employed in vehicles such as motorcycles those described in Patent Documents 1 and 2 below have been conventionally known.
  • a V-belt is stretched between a drive pulley supported by a drive shaft and a driven pulley supported by a driven shaft, and the actuator can be moved by the actuator. Slide the pulley in the axial direction to change the groove width of the drive pulley, and change the groove width of the driven pulley by the fluctuation of the tension of the V-belt due to the change in winding diameter so that the driven pulley is rotated at an increased or decreased speed.
  • the actuator includes an electric motor and a ball screw that operates using the electric motor as a drive source.
  • the screw shaft that rotates the nut of the ball screw by the electric motor and engages the nut with the screw via the ball.
  • the fork member By moving in the axial direction, the fork member is swung to move the movable pulley in the axial direction.
  • an arm member is connected to a movable pulley of a driving pulley supported by a driving shaft so as to be relatively rotatable and non-movable in an axial direction.
  • the arm member is moved in the axial direction of the drive shaft by an actuator unit as an arm drive device, and the movable pulley is moved in the axial direction of the drive shaft together with the arm member to adjust the groove width.
  • the actuator unit has an electric motor and a gear reduction mechanism that reduces the rotation of the electric motor, and a screw shaft is coupled to the output gear of the gear reduction mechanism, and the shaft end of the output shaft is connected to the screw shaft.
  • the internal thread of the cylindrical part provided in the part is threadedly engaged, the output shaft is moved in the axial direction by rotation of the screw shaft, and the arm member is moved in the axial direction by the movement of the output shaft.
  • the arm member is moved by moving the output shaft of the actuator unit in the axial direction, and the movable pulley is moved in the axial direction of the drive shaft. Since it has a configuration, the number of parts is small, and the configuration is simplified so that downsizing can be achieved.
  • the hooks provided at the end of the output shaft are engaged with the pins provided on the arm member and connected to each other, the V-belt continuously variable transmission can be assembled or disassembled by replacing parts. There is a problem that the work of unhooking the hook is necessary and the workability is poor.
  • An object of the present invention is to provide a V-belt type continuously variable transmission that is easy to assemble and disassemble with a small number of parts.
  • a driving pulley supported by a driving shaft a driven pulley supported by a driven shaft, a V belt stretched between the driving pulley and the driven pulley
  • a slide guide mechanism that supports the movable pulley in one of the driving pulley and the driven pulley so as to be slidably supported with respect to an axis that supports the movable pulley, and is coupled to the movable pulley so as to be relatively rotatable.
  • an arm member that changes the groove width of the pulley by moving the movable pulley integrally by moving the movable pulley in the axial direction, and an arm drive device that moves the arm member in the axial direction.
  • the arm driving device includes an eccentric cam that moves the arm member in the axial direction by contact rotation with the arm member. Its is an eccentric cam than to adopt a structure consisting of a rotary drive device for rotating.
  • the contact between the eccentric cam and the arm member becomes a rolling contact, so that the rotational resistance of the eccentric cam is small, and the eccentric cam is It is possible to reduce the load on the rotating drive device to be rotated.
  • an annular slide guide member having a plurality of guide pins is fitted and fixed to the shaft that supports the movable pulley, and the slide
  • Each of the plurality of guide pins in the guide member is slidably inserted into the same number of axial guide recesses as the guide pins formed on the bosses of the movable pulley, and the movable pulley is slidably supported, so that the spline is fitted.
  • the sliding resistance of the movable pulley can be greatly reduced. For this reason, it is possible to reduce the load on the rotation drive device, and to adopt a small electric motor with a small capacity as the electric motor forming the rotation drive device.
  • the arm member connected to the movable pulley so as to be relatively rotatable is moved in the axial direction of the drive shaft by the rotation of the eccentric cam to adjust the groove width of the pulley. Therefore, it is not necessary to connect the arm member and the arm drive device, and the workability of assembly and disassembly can be improved.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of a V-belt type continuously variable transmission according to the present invention.
  • Sectional drawing which expands and shows the driven pulley part of FIG. 2A is a cross-sectional view taken along line IV-IV in FIG. 2
  • FIG. 2B is a cross-sectional view showing an adjustment state in which the groove width of the drive pulley is narrowed.
  • the V-belt type continuously variable transmission according to the present invention has a transmission case 10.
  • the transmission case 10 includes a case body 11 and a cover 12 screwed to the case body 11.
  • the case main body 11 also serves as an engine cover, and shaft insertion holes 13 and 14 are provided at one end and the other end of the case main body 11, respectively.
  • the crankshaft 16 provided in the crank disk 15 of the engine is inserted into the shaft insertion hole 13 provided in one end of the case body 11.
  • the crankshaft 16 is a primary shaft as a drive shaft, and the primary shaft 16 is rotatably supported by a bearing 17 incorporated in the shaft insertion hole 13.
  • a secondary shaft 18 as a driven shaft is inserted into the shaft insertion hole 14 provided at the other end of the case body 11 and faces the transmission case 10.
  • the secondary shaft 18 is rotatably supported by a bearing 19 incorporated in the shaft insertion hole 14.
  • each of the shaft insertion holes 13 and 14 is sealed by incorporating a seal member 20.
  • V-belt type continuously variable transmission mechanism A is accommodated in the transmission case 10.
  • the V-belt type continuously variable transmission mechanism A includes a drive pulley 30 supported by a primary shaft 16, a driven pulley 40 supported by a secondary shaft 18, and a V belt 50 spanned between these pulleys 30 and 40. Have.
  • V-belt type continuously variable transmission mechanism A has an arm member 60 that adjusts the groove width of the drive pulley 30 and an arm drive device 70 that operates the arm member 60.
  • the drive pulley 30 includes a dish-shaped fixed pulley 31 and a dish-shaped movable pulley 32.
  • the fixed pulley 31 is spline-fitted to a small-diameter shaft portion 16a provided on the primary shaft 16 and rotates integrally with the primary shaft 16, and the sleeve 33 fitted to the small-diameter shaft portion 16a and the end portion of the small-diameter shaft portion 16a.
  • the nut 34 is screwed to the outer peripheral male screw 16b and is clamped from the axial direction so as to be non-movable in the axial direction.
  • the movable pulley 32 is fitted to a sleeve 33, and a sliding bearing 39 is incorporated between the fitting portions. Further, the movable pulley 32 is prevented from rotating around the primary shaft 16 by a slide guide mechanism 35 provided between the movable pulley 32 and the primary shaft 16 and is slidable in the axial direction.
  • the slide guide mechanism 35 is fixed in such a manner that an annular slide guide member 36 is fitted to the base of the small-diameter shaft portion 16a, and the step portion 16c provided at the base of the small-diameter shaft portion 16a and the sleeve 33 are sandwiched from the axial direction.
  • Each of the plurality of guide pins 37 implanted on one side of the slide guide member 36 is inserted into the same number of guide recesses 38 in the axial direction as the guide pins 37 formed on the boss portion 32a of the movable pulley 32.
  • the guide pin 37 supports the rotation of the primary shaft 16 to transmit the torque to the movable pulley 32.
  • the plurality of guide pins 37 are arranged at a predetermined interval on one circle centered on the axis of the slide guide member 36.
  • an axial groove having a groove width substantially the same as the pin diameter of the guide pin 37 is shown here. It may consist of pin holes of the same diameter.
  • the driven pulley 40 includes a dish-shaped fixed pulley 41 and a dish-shaped movable pulley 42, as with the drive pulley 30 described above.
  • the fixed pulley 41 has a boss portion 41a fitted to the secondary shaft 18, and is rotatably supported by a pair of bearings 43 and 44 incorporated in the boss portion 41a.
  • the bearing 44 positioned on the shaft end side of the secondary shaft 18 is non-movable in the axial direction, and a step 41 b formed on the inner periphery of the boss 41 a is provided on the bearing 44.
  • the fixed pulley 41 is engaged so as to be non-movable in the axial direction.
  • the movable pulley 42 has a cylindrical portion 42 a fitted to the boss portion 41 a of the fixed pulley 41, and a slit 42 b extending in the axial direction is formed in the cylindrical portion 42 a and is attached to the boss portion 41 a of the fixed pulley 41.
  • the key member 45 is inserted into the slit 42b so that the movable pulley 42 is slidable in the axial direction and is urged toward the fixed pulley 41 by an elastic member 46 made of a coil spring.
  • the movable pulley 42 is prevented from rotating around the boss portion 41a by the engagement of the slit 42b and the key member 45, and rotates integrally with the boss portion 41a.
  • a centrifugal clutch 47 is incorporated between the boss 41 a of the fixed pulley 41 and the secondary shaft 18.
  • the centrifugal clutch 47 is fitted and fixed to the boss 41a so that the weight arm 47a rotates together with the boss 41a, and the weight 47b is attached to the weight arm 47a so as to be swingable around an axis parallel to the secondary shaft 18,
  • a hook-shaped outer clutch 47c surrounding the outside of the weight 47b is fitted and fixed so as to rotate together with the secondary shaft 18.
  • the centrifugal clutch 47 when the rotational speed of the driven pulley 40 rotated by the movement of the V-belt 50 increases and reaches a set speed, the weight 47b swings radially outward due to the centrifugal force and the outer clutch. The inner surface of 47c is brought into press contact with each other so as to be engaged, and the rotation of the driven pulley 40 is transmitted to the secondary shaft 18.
  • the arm member 60 is configured such that a forked piece 62 is provided on the outer periphery of the ring portion 61, and the ring portion 61 is fitted to the boss portion 32 a of the movable pulley 32. It is supported so as to be relatively rotatable via a release bearing 63 and is non-movable in the axial direction so as to move integrally with the movable pulley 32.
  • the arm member 60 moves the movable pulley 42 in the axial direction of the primary shaft 16 by the axial pressing force applied to the bifurcated piece 62, and the ring portion 61 receives the pressing force applied to the bifurcated piece 62.
  • a moment load that causes an inclination is applied.
  • a double row angular ball bearing is used here as the release bearing 63, but a deep groove ball bearing may be adopted. There may be one deep groove ball bearing, but it is preferable to use two or more.
  • the bifurcated piece 62 has an L-shaped planar shape and is opposed to the upper and lower sides, and both end portions of the roller shaft 64 are supported by the front end portion facing the inside of the V belt 50, and the roller 65 is rotatably supported by the roller shaft 64.
  • a rolling bearing is employed as the roller 65.
  • the arm driving device 70 includes an eccentric cam 84 that rotates in contact with a rotatable roller 65 incorporated between the forked pieces 62 of the arm member 60, and a rotation that rotationally drives the eccentric cam 84.
  • a drive device 71 is included.
  • the arm driving device 70 has a unit case 90 that houses the rotation driving device 71, and the unit case 90 is fitted in a fitting recess 91 provided in the cover 12 of the transmission case 10.
  • the rotation drive device 71 has an electric motor 72 and a speed reduction mechanism 80 that decelerates and outputs the rotation of the rotor shaft 72a of the electric motor 72.
  • the speed reduction mechanism 80 is composed of a spur gear type reduction gear using a plurality of spur gears.
  • the output shaft 81 provided on the output gear 80a at the final stage of the spur gear type speed reducer 80 is arranged parallel to the primary shaft 16, and the transmission case is formed from a bearing fitting hole 92 formed at the end of the unit case 90. 10 which covers the cover 12 and is rotatably supported by a bearing 93 incorporated in the bearing fitting hole 92.
  • the rotation of the output shaft 81 is transmitted to the cam shaft 83 through a pair of bevel gears 82 that mesh with each other as shown in FIG.
  • the cam shaft 83 extends in the vertical direction and is orthogonal to the output shaft 81.
  • the upper end of the cam shaft 83 faces the roller 65 that can rotate between the forked pieces 62 of the arm member 60 in the front-rear direction, and an eccentric cam 84 is provided at the upper end. It has been.
  • a spur gear type reduction gear composed of a plurality of spur gears is adopted as the reduction mechanism 80, but a planetary gear type reduction gear or a gear reduction gear consisting of a worm and a worm wheel may be adopted.
  • the gear type speed reducer composed of a worm and a worm wheel
  • the worm wheel is fixed to the lower end portion of the cam shaft 83 shown in FIG. Therefore, the bevel gear 82 shown in the figure can be omitted, and the configuration can be simplified.
  • the V-belt type continuously variable transmission shown in the embodiment has the above structure, and the electric motor 72 in the arm driving device 70 is controlled by a control unit (not shown). Now, when the primary shaft 16 rotates and the driving pulley 30 rotates together with the primary shaft 16, the rotation is transmitted to the driven pulley 40 via the V belt 50, and the driven pulley 40 rotates in the same direction as the driving pulley 30. Then, the centrifugal clutch 47 is engaged and the rotation of the driven pulley 40 is transmitted to the secondary shaft 18.
  • FIG. 2 and FIG. 4A show a state where the outer periphery with the smallest eccentric amount of the eccentric cam 84 is in contact with the roller 65, and when the eccentric cam 84 rotates from that state, the eccentric cam 84 causes the eccentric cam 84 to rotate.
  • the roller 65 is pressed, and the arm member 60 moves in the axial direction of the primary shaft 16 by the pressing.
  • the movable pulley 32 of the drive pulley 30 is connected to the arm member 60, the movable pulley 32 moves toward the fixed pulley 31, and the movement reduces the groove width of the drive pulley 30, and the V belt.
  • the winding diameter of 50 increases.
  • the tension of the V-belt 50 increases as the winding diameter of the driving pulley 30 increases, the movable pulley 42 in the driven pulley 40 slides away from the fixed pulley 41, and the groove width of the driven pulley 40 increases. The winding diameter of the V belt 50 is reduced.
  • FIGS. 4B and 6 show a state in which the eccentric cam 84 rotates 180 ° and the portion having the largest eccentric amount is in contact with the roller 65, and the winding diameter of the V belt 50 on which the drive pulley 30 is applied is the maximum. The diameter.
  • the movable pulley 42 in the driven pulley 40 is loaded with the pressing force of the elastic member 46, so that the movable pulley 42 moves toward the fixed pulley 41 to move the driven pulley 40.
  • the groove width is narrowed and the winding diameter of the V-belt 50 is increased.
  • the tension of the V belt 50 increases due to the increase in the winding diameter of the driven pulley 40, the movable pulley 32 in the drive pulley 30 slides away from the fixed pulley 31, and the groove width of the drive pulley 30 increases. The winding diameter of the V belt 50 is reduced.
  • the movable pulley 32 is slidably supported by the plurality of guide pins 37 of the slide guide member 36, the movable pulley 32 is slidably supported by the spline fitting. Compared to the case, the slide resistance of the movable pulley 32 can be greatly reduced, and a small-sized electric motor 72 having a small capacity can be employed.
  • the arm member 60 connected to the movable pulley 32 of the drive pulley 30 by a release bearing 63 is provided with a bifurcated piece 62 and is rotatably supported by the bifurcated piece 62.
  • the eccentric cam 84 By rotating the eccentric cam 84 in contact with the roller 65 and moving the movable pulley 32 in the axial direction of the primary shaft 16 together with the arm member 60 to adjust the groove width of the drive pulley 30, the arm drive device 70. It is not necessary to connect the arm member 60 and the arm member 60, and the workability of assembly and disassembly can be improved.
  • the movable pulley 32 of the driving pulley 30 is slid with respect to the fixed pulley 31 by the arm driving device 70 to change the gear ratio, but the movable pulley 42 of the driven pulley 40 is moved with respect to the fixed pulley 41.
  • the gear ratio may be changed by sliding the slider.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmissions By Endless Flexible Members (AREA)
PCT/JP2014/080766 2013-11-22 2014-11-20 Ｖベルト式無段変速機 Ceased WO2015076333A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US15/038,305 US20160290450A1 (en) 2013-11-22 2014-11-20 V-belt type infinitely variable transmission
EP14864005.5A EP3073150A4 (en) 2013-11-22 2014-11-20 V-belt continuously variable transmission
CN201480056973.5A CN105683623A (zh) 2013-11-22 2014-11-20 V带式无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013-241682 2013-11-22
JP2013241682A JP6461468B2 (ja) 2013-11-22 2013-11-22 Ｖベルト式無段変速機

Publications (1)

Publication Number Publication Date
WO2015076333A1 true WO2015076333A1 (ja) 2015-05-28

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ID=53179593

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2014/080766 Ceased WO2015076333A1 (ja) 2013-11-22 2014-11-20 Ｖベルト式無段変速機

Country Status (5)

Country Link
US (1) US20160290450A1 (enExample)
EP (1) EP3073150A4 (enExample)
JP (1) JP6461468B2 (enExample)
CN (1) CN105683623A (enExample)
WO (1) WO2015076333A1 (enExample)

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EP3597964A4 (en) * 2017-03-16 2020-03-04 Honda Motor Co., Ltd. Belt-type continuously variable transmission

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EP3073150A1 (en) 2016-09-28
JP6461468B2 (ja) 2019-01-30
JP2015102119A (ja) 2015-06-04
CN105683623A (zh) 2016-06-15
EP3073150A4 (en) 2017-03-29
US20160290450A1 (en) 2016-10-06

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