WO2013008624A1 - 無段変速機 - Google Patents

無段変速機 Download PDF

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Publication number
WO2013008624A1
WO2013008624A1 PCT/JP2012/066381 JP2012066381W WO2013008624A1 WO 2013008624 A1 WO2013008624 A1 WO 2013008624A1 JP 2012066381 W JP2012066381 W JP 2012066381W WO 2013008624 A1 WO2013008624 A1 WO 2013008624A1
Authority
WO
WIPO (PCT)
Prior art keywords
eccentric
center
input shaft
eccentric disk
disk
Prior art date
Application number
PCT/JP2012/066381
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English (en)
French (fr)
Japanese (ja)
Inventor
優史 西村
和樹 市川
Original Assignee
本田技研工業株式会社
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 本田技研工業株式会社 filed Critical 本田技研工業株式会社
Priority to JP2013523881A priority Critical patent/JP5703379B2/ja
Priority to CN201280031651.6A priority patent/CN103649594B/zh
Publication of WO2013008624A1 publication Critical patent/WO2013008624A1/ja

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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
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts

Definitions

  • the present invention eccentrically rotates one end of the connecting rod by the input shaft, intermittently rotates the output shaft connected to the other end of the connecting rod via the one-way clutch, and changes the eccentric amount of the one end of the connecting rod. It is related with the continuously variable transmission which changes a gear ratio by making it.
  • Such a continuously variable transmission is known from Patent Document 1 below.
  • a disk-shaped eccentric cam is fixed to the input shaft in an eccentric state, and a disk-shaped eccentric disk is supported on the outer periphery of the eccentric cam so as to be relatively rotatable in an eccentric state.
  • the eccentric ratio of the eccentric disk with respect to the axis of the input shaft is changed to change the gear ratio.
  • the present invention has been made in view of the above-described circumstances, and an object of the present invention is to minimize the occurrence of vibration associated with the change in the amount of eccentricity of an eccentric disk of a continuously variable transmission.
  • an eccentric cam fixed in an eccentric state on the outer periphery of an input shaft connected to a drive source, and an eccentric cam that supports relative rotation in an eccentric state are supported.
  • the center of gravity position, a continuously variable transmission according to the first, characterized in that fitted to the eccentric center of rotation relative to the eccentric cam of the eccentric disk is proposed.
  • a continuously variable transmission is proposed in which the transmission shaft is driven by a transmission actuator.
  • the eccentric disk in addition to the first or second feature, is thinned so that the position of the center of gravity of the eccentric disk coincides with the eccentric rotation center of the eccentric disk with respect to the eccentric cam.
  • a continuously variable transmission having a third feature is provided.
  • the eccentric disk is configured so that a center of gravity position of the eccentric disk coincides with an eccentric rotation center of the eccentric disk with respect to the eccentric cam.
  • a continuously variable transmission having a fourth feature of providing a weight on the disk is proposed.
  • the engine E of the embodiment corresponds to the drive source of the present invention
  • the center O1 of the eccentric cam of the embodiment corresponds to the eccentric rotation center of the present invention
  • the lightening recess 19c of the embodiment corresponds to the present invention.
  • the eccentric cam fixed in the eccentric state on the outer periphery of the input shaft rotates eccentrically, and in the eccentric state on the outer periphery of the eccentric cam.
  • the supported eccentric disk rotates eccentrically.
  • the connecting rod connected at one end to the eccentric disk reciprocates, the output shaft rotates intermittently via a one-way clutch connected at the other end of the connecting rod.
  • the eccentric disk is rotated relative to the eccentric cam with the transmission shaft coaxially fitted inside the input shaft, the eccentric amount of the eccentric disk with respect to the input shaft changes, and the reciprocating stroke of the connecting rod changes.
  • the gear ratio is changed by changing the intermittent rotation angle of the shaft.
  • the center of gravity of the eccentric disk is made coincident with the center of eccentric rotation, so that the moment for rotating the eccentric disk relative to the eccentric cam even if an inertial force acts on the eccentric disk. Will not occur. Therefore, the moment is not transmitted back to the transmission actuator from the eccentric disk via the transmission shaft to the transmission actuator that drives the transmission shaft, and the control accuracy of the transmission actuator is improved.
  • the eccentric disk since the eccentric disk is provided with the thinning portion so that the center of gravity of the eccentric disk coincides with the eccentric rotation center of the eccentric disk with respect to the eccentric cam, the eccentric disk has a simple structure. Can be adjusted.
  • the center of gravity of the eccentric disk since the weight of the eccentric disk is provided in order to make the position of the center of gravity of the eccentric disk coincide with the center of eccentric rotation with respect to the eccentric cam of the eccentric disk, the center of gravity of the eccentric disk has a simple structure. The position can be adjusted.
  • FIG. 1 is an overall view of a continuously variable transmission.
  • FIG. 2 is a partially broken perspective view of a main part of the continuously variable transmission.
  • First embodiment 3 is a cross-sectional view taken along line 3-3 of FIG.
  • First embodiment is an enlarged view of part 4 of FIG.
  • First embodiment 5 is a cross-sectional view taken along line 5-5 of FIG.
  • FIG. 6 is a diagram showing the shape of the eccentric disk.
  • FIG. 7 is a diagram showing the relationship between the amount of eccentricity of the eccentric disk and the gear ratio.
  • FIG. 8 is a diagram showing the relationship between the amount of eccentricity of the eccentric disk and the locus of the center of gravity.
  • FIG. 9 corresponds to FIG. (Second Embodiment)
  • a transmission case 11 of a continuously variable transmission T for an automobile includes a frame 51 having a frame main body 51a and a pair of first and second side walls 51b and 51c and an upper surface being opened.
  • the upper cover 52 and the lower cover 53 are divided into two parts covering the periphery of the frame 51.
  • the input shaft 12 and the output shaft 13 are supported in parallel to each other on the first and second side walls 51b and 51c of the transmission case 11, and the rotation of the input shaft 12 connected to the engine E is six transmission units 14 and It is transmitted to the drive wheel via the output shaft 13.
  • a variable speed shaft 15 sharing an axis L with the input shaft 12 is fitted into the hollow formed input shaft 12 via seven needle bearings 16 so as to be relatively rotatable. Since the structure of the six transmission units 14 is substantially the same, the structure will be described below with one transmission unit 14 as a representative.
  • the transmission unit 14 includes a pinion 17 provided on the outer peripheral surface of the transmission shaft 15, and the pinion 17 is exposed from an opening 12 a formed in the input shaft 12.
  • a disc-shaped eccentric cam 18 divided into two in the direction of the axis L is splined to the outer periphery of the input shaft 12 so as to sandwich the pinion 17.
  • the center O1 of the eccentric cam 18 is eccentric with respect to the axis L of the input shaft 12 by a distance d. Further, the six eccentric cams 18 of the six transmission units 14 are offset in phase by 60 ° from each other.
  • a pair of eccentric recesses 19 a and 19 a formed on both end surfaces in the axis L direction of the disc-shaped eccentric disk 19 are rotatably supported via a pair of needle bearings 20 and 20. .
  • the center O1 of the eccentric recesses 19a, 19a (that is, the center O1 of the eccentric cam 18) is shifted from the center O2 of the eccentric disk 19 by a distance d. That is, the distance d between the axis L of the input shaft 12 and the center O1 of the eccentric cam 18 and the distance d between the center O1 of the eccentric cam 18 and the center O2 of the eccentric disk 19 are the same.
  • a pair of crescent-shaped guide portions 18a and 18a are provided on the split surface of the eccentric cam 18 divided into two in the direction of the axis L so as to be coaxial with the center O1 of the eccentric cam 18.
  • the one end side of the input shaft 12 is directly supported by the first side wall 51b of the mission case 11 via the ball bearing 21. Further, a cylindrical portion 18b provided integrally with one eccentric cam 18 positioned on the other end side of the input shaft 12 is supported by the second side wall 51c of the transmission case 11 via the ball bearing 22, and the eccentricity thereof. The other end side of the input shaft 12 splined to the inner periphery of the cam 18 is indirectly supported by the mission case 11.
  • the speed change actuator 23 that changes the speed ratio of the continuously variable transmission T by rotating the speed change shaft 15 relative to the input shaft 12 is a side cover 42 of the transmission case 11 so that the motor shaft 24a is coaxial with the axis L.
  • an planetary gear mechanism 25 connected to the electric motor 24.
  • the planetary gear mechanism 25 includes a carrier 27 that is rotatably supported by an electric motor 24 via a needle bearing 26, a sun gear 28 that is fixed to the motor shaft 24a, and a plurality of two stations that are rotatably supported by the carrier 27.
  • Each double pinion 29 includes a first pinion 29a having a large diameter and a second pinion 29b having a small diameter.
  • the first pinion 29a meshes with the sun gear 28 and the first ring gear 30, and the second pinion 29b has a second ring gear. Mesh with 31.
  • an annular portion 33a on one end side of the connecting rod 33 is supported via a roller bearing 32 so as to be relatively rotatable.
  • the output shaft 13 is supported on the first and second side walls 51b and 51c of the mission case 11 by a pair of ball bearings 34 and 35, and a one-way clutch 36 is provided on the outer periphery thereof.
  • the one-way clutch 36 includes a ring-shaped outer member 38 pivotally supported at the tip of the rod portion 33b of the connecting rod 33 via a pin 37, and an inner member disposed inside the outer member 38 and fixed to the output shaft 13. 39 and a plurality of rollers 41 arranged in a wedge-shaped space formed between the inner circular arc surface of the outer member 38 and the outer peripheral plane of the inner member 39 and biased by a plurality of springs 40. ... And.
  • the center O1 of the eccentric recesses 19a and 19a (that is, the center O1 of the eccentric cam 18) is shifted by a distance d with respect to the center O2 of the eccentric disc 19, the outer periphery of the eccentric disc 19 and the eccentric recess
  • interval with the inner periphery of 19a and 19a is non-uniform
  • the thinning recesses 19c, 19c are formed so as to face each other on both sides of the eccentric disk 19 with the thin bottom wall 19d interposed therebetween.
  • the thinning recess 19c may be formed so as to penetrate the eccentric disk 19 in the thickness direction.
  • the center of gravity G of the eccentric disk 19 exists in the vicinity of the center O2, but the center of gravity of the eccentric disk 19 is formed by forming the hollowing recesses 19c, 19c.
  • the position G moves in a direction away from the thinning recesses 19c and 19c, and in the present embodiment, is aligned with the center O1 of the eccentric recesses 19a and 19a (that is, the center O1 of the eccentric cam 18).
  • the output shaft 13 rotates intermittently when the input shaft 12 rotates continuously. Since the eccentric disks 19 of the six transmission units 14 are out of phase with each other by 60 °, the six transmission units 14 alternately transmit the rotation of the input shaft 12 to the output shaft 13. Thus, the output shaft 13 rotates continuously.
  • the transmission ratio of the continuously variable transmission T is maintained constant.
  • the electric motor 24 may be rotationally driven at the same speed as the input shaft 12.
  • the first ring gear 30 of the planetary gear mechanism 25 is connected to the input shaft 12 and rotates at the same speed as the input shaft 12, but when the electric motor 24 is driven at the same speed, the sun gear 28 and the first ring gear 30. Rotate at the same speed, the planetary gear mechanism 25 is locked and rotates as a whole.
  • the input shaft 12 and the transmission shaft 15 connected to the first ring gear 30 and the second ring gear 31 that rotate integrally are integrated and rotate at the same speed without relative rotation.
  • the first ring gear 30 coupled to the input shaft 12 and the sun gear 28 connected to the electric motor 24 rotate relative to each other.
  • the carrier 27 rotates relative to the first ring gear 30.
  • the gear ratio of the first ring gear 30 and the first pinion 29a meshing with each other is slightly different from the gear ratio of the second ring gear 31 and the second pinion 29b meshing with each other.
  • the transmission shaft 15 connected to the second ring gear 31 rotate relative to each other.
  • FIG. 7A shows a state where the speed ratio is minimum (speed ratio: TD).
  • speed ratio speed ratio: TD
  • the eccentric amount ⁇ of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is the axis L of the input shaft 12.
  • 2d which is the sum of the distance d from the center O1 of the eccentric cam 18 to the center O2 of the eccentric disk 19.
  • the amount of eccentricity ⁇ of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 gradually decreases from the maximum value 2d, and the gear ratio increases.
  • the transmission shaft 15 further rotates relative to the input shaft 12
  • the eccentric disk 19 further rotates relative to the eccentric cam 18 integrated with the input shaft 12, and finally, as shown in FIG.
  • the center O2 of the eccentric disk 19 overlaps the axis L of the input shaft 12, the eccentricity ⁇ becomes zero, the transmission gear ratio is maximized (infinite) (transmission ratio: UD), and power is transmitted to the output shaft 13. Blocked.
  • FIG. 8A shows the state of the minimum speed ratio (speed ratio: TD) in which the amount of eccentricity ⁇ of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 reaches the maximum value 2d.
  • the eccentric direction of the center O1 of the eccentric cam 18 with respect to the axis L (upward in the figure) and the eccentric direction of the center O2 of the eccentric disk 19 with respect to the center O1 of the eccentric cam 18 (upward in the figure) are the same direction.
  • the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 18.
  • FIG. 8B shows the state of the maximum gear ratio (gear ratio: UD) in which the eccentric amount ⁇ of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is the minimum value zero.
  • the eccentric direction of the center O1 of the eccentric cam 18 with respect to the axis L (upward in the figure) is opposite to the eccentric direction of the center O2 of the eccentric disk 19 with respect to the center O1 of the eccentric cam 18 (downward in the figure).
  • the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 18.
  • the eccentric disk 19 since the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 18, the eccentric disk 19 is moved around the center O1 of the eccentric cam 18 with the change of the gear ratio. Even if it rotates eccentrically, the gravity center position G of the eccentric disk 19 always exists on the center O1 of the eccentric cam 18, and the distance between the axis L of the input shaft 12 and the gravity center position G of the eccentric disk 19 changes from a constant value d. None do.
  • the inertia moment of inertia of the eccentric disk 19 around the input shaft 12 increases the distance. Therefore, the rotation load of the input shaft 12 may fluctuate with the change of the gear ratio, and vibration may occur.
  • the inertia moment of the eccentric disk 19 around the input shaft 12 does not change, so that the vibration of the input shaft 12 can be minimized.
  • the eccentric disk 19 Since the eccentric disk 19 is supported by the eccentric cam 18 so as to be relatively rotatable, if the center of gravity G of the eccentric disk 19 does not coincide with the center O1 of the eccentric cam 18, the rotational speed of the input shaft 12 increases. Alternatively, when it decreases, the eccentric disk 19 tends to rotate relative to the eccentric cam 18 with inertial force, and the moment is transmitted from the ring gear 19b of the eccentric disk 19 to the electric motor 24 of the transmission actuator 23 via the pinion 17. Unnecessary torque may act on the electric motor 24 to reduce the accuracy of the shift control.
  • the eccentric disk 19 since the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 18, even if the rotational speed of the input shaft 12 increases or decreases, the eccentric disk 19 is inertial. No moment is generated to rotate relative to the eccentric cam 18 by force, thereby preventing unnecessary torque from acting on the electric motor 24 and ensuring the accuracy of the shift control.
  • the center of gravity position G of the eccentric disc 19 is made to coincide with the center O1 of the eccentric recesses 19a, 19a by forming the hollow recesses 19c, 19c in the eccentric disc 19.
  • a pair of weights 19e, 19e are further provided on the side of the eccentric disc 19 opposite to the thinned recesses 19c, 19c so that the center of gravity G of the eccentric disc 19 is located at the center O1 of the eccentric recess 19a, 19a. Match. The reason why the weights 19e and 19e are divided into two is to avoid the interference with the roller bearing 32 and the connecting rod 33.
  • the center of gravity position G of the eccentric disk 19 is further increased by the weights 19e and 19e. It can be moved to coincide with the center O1 of the eccentric recesses 19a, 19a.
  • the center of gravity G of the eccentric disk 19 can be adjusted with a simple structure.
  • the drive source of the present invention is not limited to the engine E of the embodiment, and may be another drive source such as an electric motor.
  • the lightening part of the present invention is not limited to the lightening recessed part 19c of the embodiment, and may be a lightening hole penetrating the eccentric disk 19.
  • the weight 19e of the present invention is not necessarily formed integrally with the eccentric disk 19, and may be configured by a separate member and fixed to the eccentric disk 19.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
PCT/JP2012/066381 2011-07-13 2012-06-27 無段変速機 WO2013008624A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2013523881A JP5703379B2 (ja) 2011-07-13 2012-06-27 無段変速機
CN201280031651.6A CN103649594B (zh) 2011-07-13 2012-06-27 无级变速器

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JP2011-154521 2011-07-13
JP2011154521 2011-07-13

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CN (1) CN103649594B (zh)
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CN103968026A (zh) * 2013-02-05 2014-08-06 本田技研工业株式会社 车辆用动力传递装置
JP2014145390A (ja) * 2013-01-28 2014-08-14 Honda Motor Co Ltd 無段変速機
JP2014152806A (ja) * 2013-02-05 2014-08-25 Honda Motor Co Ltd 車両用動力伝達装置
JP2014206268A (ja) * 2013-03-21 2014-10-30 本田技研工業株式会社 一方向回転阻止機構
DE102013010753A1 (de) * 2013-06-27 2014-12-31 Audi Ag Exzenteranordnung sowie Brennkraftmaschine
JP2015038371A (ja) * 2013-08-19 2015-02-26 本田技研工業株式会社 無段変速機
CN104553741A (zh) * 2013-10-09 2015-04-29 本田技研工业株式会社 车辆用动力传递装置
JP2015098923A (ja) * 2013-11-20 2015-05-28 本田技研工業株式会社 車両用動力伝達装置
JP2015132322A (ja) * 2014-01-14 2015-07-23 本田技研工業株式会社 無段変速機
CN104832639A (zh) * 2014-02-07 2015-08-12 本田技研工业株式会社 车辆用动力传递装置
CN105317959A (zh) * 2014-08-01 2016-02-10 本田技研工业株式会社 无级变速机构
WO2017012903A1 (de) 2015-07-21 2017-01-26 Martin Weilenmann Getriebe mit einem schwungrad und verfahren zum betreiben eines getriebes
CN106555867A (zh) * 2017-01-20 2017-04-05 蔡明� 一种变速箱
US10605321B2 (en) 2015-07-21 2020-03-31 Martin Weilenmann Transmission with a torsion spring and method for operating a transmission

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CN104583647B (zh) * 2012-09-13 2017-05-24 本田技研工业株式会社 车辆用动力传递装置
JP6163124B2 (ja) * 2014-03-20 2017-07-12 本田技研工業株式会社 無段変速機
JP6180993B2 (ja) * 2014-05-07 2017-08-16 本田技研工業株式会社 無段変速機
JP2016035287A (ja) * 2014-08-01 2016-03-17 本田技研工業株式会社 無段変速機構
JP2016138599A (ja) * 2015-01-28 2016-08-04 本田技研工業株式会社 車両用動力伝達装置
JP6407119B2 (ja) * 2015-09-10 2018-10-17 本田技研工業株式会社 動力伝達装置
KR101889307B1 (ko) * 2016-11-23 2018-09-28 이스트바이크 주식회사 무단변속기
CN109236975A (zh) * 2018-10-31 2019-01-18 江苏牛牌纺织机械有限公司 一种偏心轮及连杆结合件
JP6760674B1 (ja) * 2019-09-05 2020-09-23 昌幸 池田 歯車変速装置

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JPH04501452A (ja) * 1988-11-08 1992-03-12 イーガン、マイケル・ジョセフ 可変速駆動動力伝動装置
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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014145390A (ja) * 2013-01-28 2014-08-14 Honda Motor Co Ltd 無段変速機
CN103968026A (zh) * 2013-02-05 2014-08-06 本田技研工业株式会社 车辆用动力传递装置
JP2014152806A (ja) * 2013-02-05 2014-08-25 Honda Motor Co Ltd 車両用動力伝達装置
JP2014206268A (ja) * 2013-03-21 2014-10-30 本田技研工業株式会社 一方向回転阻止機構
DE102013010753A1 (de) * 2013-06-27 2014-12-31 Audi Ag Exzenteranordnung sowie Brennkraftmaschine
DE102013010753B4 (de) * 2013-06-27 2015-02-12 Audi Ag Exzenteranordnung sowie Brennkraftmaschine
JP2015038371A (ja) * 2013-08-19 2015-02-26 本田技研工業株式会社 無段変速機
CN104553741A (zh) * 2013-10-09 2015-04-29 本田技研工业株式会社 车辆用动力传递装置
JP2015098923A (ja) * 2013-11-20 2015-05-28 本田技研工業株式会社 車両用動力伝達装置
JP2015132322A (ja) * 2014-01-14 2015-07-23 本田技研工業株式会社 無段変速機
CN104832639A (zh) * 2014-02-07 2015-08-12 本田技研工业株式会社 车辆用动力传递装置
CN104832639B (zh) * 2014-02-07 2017-04-19 本田技研工业株式会社 车辆用动力传递装置
CN105317959A (zh) * 2014-08-01 2016-02-10 本田技研工业株式会社 无级变速机构
WO2017012903A1 (de) 2015-07-21 2017-01-26 Martin Weilenmann Getriebe mit einem schwungrad und verfahren zum betreiben eines getriebes
US10605321B2 (en) 2015-07-21 2020-03-31 Martin Weilenmann Transmission with a torsion spring and method for operating a transmission
CN106555867A (zh) * 2017-01-20 2017-04-05 蔡明� 一种变速箱

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JPWO2013008624A1 (ja) 2015-02-23
CN103649594A (zh) 2014-03-19
CN103649594B (zh) 2016-03-09
JP5703379B2 (ja) 2015-04-15

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