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WO2014038296A1 - Transmission à variation continue - Google Patents

Transmission à variation continue Download PDF

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Publication number
WO2014038296A1
WO2014038296A1 PCT/JP2013/069544 JP2013069544W WO2014038296A1 WO 2014038296 A1 WO2014038296 A1 WO 2014038296A1 JP 2013069544 W JP2013069544 W JP 2013069544W WO 2014038296 A1 WO2014038296 A1 WO 2014038296A1
Authority
WO
WIPO (PCT)
Prior art keywords
wall portion
continuously variable
variable transmission
output shaft
input shaft
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/JP2013/069544
Other languages
English (en)
Japanese (ja)
Inventor
將司 ▲高▼杉
文康 菅
和樹 市川
優史 西村
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.)
Honda Motor Co Ltd
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
Priority to JP2014534234A priority Critical patent/JP5882478B2/ja
Priority to CN201380031110.8A priority patent/CN104364557B/zh
Publication of WO2014038296A1 publication Critical patent/WO2014038296A1/fr
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
    • 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
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/028—Gearboxes; Mounting gearing therein characterised by means for reducing vibration or noise
    • 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
    • F16D41/064—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls
    • F16D41/066—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical
    • F16D2041/0665—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by rolling and having a circular cross-section, e.g. balls all members having the same size and only one of the two surfaces being cylindrical characterised by there being no cage other than the inner and outer race for distributing the intermediate 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02021—Gearboxes; Mounting gearing therein with means for adjusting alignment

Definitions

  • the present invention relates to a continuously variable transmission of a four-bar linkage mechanism type that is variable by adjusting the radius of rotational motion on the input shaft side with a rotation radius adjusting mechanism provided on the input shaft.
  • a plurality of swing links pivotally supported on the output shaft, an input-side annular portion that is rotatably fitted to the rotation radius adjusting mechanism at one end, and the other end is
  • a four-bar link mechanism type continuously variable transmission is known that includes a connecting rod connected to a swing end of a swing link (see, for example, Japanese Patent Publication No. 2005-502543).
  • each turning radius adjustment mechanism includes a cam disk provided eccentrically on the input shaft, a rotating disk provided eccentrically on the cam disk, and a pinion shaft.
  • a one-way clutch is provided between the swing link and the output shaft. The one-way clutch fixes the swing link to the output shaft when the swing link is about to rotate relative to the output shaft, and To idle the swing link.
  • Each cam disk includes a through hole penetrating in the axial direction of the input shaft and a notch hole provided at a position facing the eccentric direction with respect to the input shaft and communicating the outer peripheral surface of the cam disk with the through hole.
  • the notch hole is provided from one end surface in the axial direction of the cam disk to the other end surface. Adjacent cam disks are fixed with bolts, thereby forming a cam disk coupling body. One end in the axial direction of the cam disk coupling body is coupled to the input shaft, and the cam disk coupling body and the input shaft constitute a cam shaft.
  • the cam disk coupling body is hollow by connecting through holes of each cam disk, and a pinion shaft is inserted into the inside.
  • the inserted pinion shaft is exposed from the notch hole of each cam disk.
  • the rotating disk is provided with a receiving hole for receiving the camshaft. Internal teeth are formed on the inner peripheral surface of the rotating disk that forms the receiving hole.
  • the inner teeth mesh with the pinion shaft exposed from the notch hole in the camshaft.
  • the radius of rotational motion on the input shaft side of the rotational radius adjusting mechanism is maintained.
  • the rotational speeds of the input shaft and the pinion shaft are made different, the radius of the rotational motion on the input shaft side of the rotational radius adjusting mechanism is changed, and the gear ratio is changed.
  • a lever crank mechanism is configured by the turning radius adjusting mechanism, the connecting rod, and the swing link. Since the swing link is provided on the output shaft via the one-way clutch, the rotational drive force (torque) is transmitted to the output shaft only when rotating to one side.
  • the eccentric direction of the cam disk of each turning radius adjusting mechanism is set so as to make a round around the input shaft with different phases. Therefore, the connecting rod that is externally fitted to each turning radius adjusting mechanism causes the swing link to transmit torque to the output shaft in order, so that the output shaft can be smoothly rotated.
  • the load applied to the bearings that support the input shaft and the output shaft changes with the change in the radius of rotational motion by the turning radius adjustment mechanism. Further, the timing at which each lever crank mechanism transmits power is different. For this reason, in the continuously variable transmission, the input shaft and the output shaft are more easily bent and the angle between the inner ring and the outer ring of the bearing supporting these shafts is deviated as compared with a parallel shaft type or planetary gear mechanism type transmission. An alignment error occurs.
  • the present invention has been made in view of the above points, and an object thereof is to provide a continuously variable transmission that can suppress alignment errors.
  • the present invention is arranged rotatably in a transmission case, and has an input shaft to which a driving force from a traveling drive source is transmitted, and is rotatable in the transmission case. And an output shaft disposed in parallel with the input shaft, and a swing link pivotally supported by the output shaft, and the rotational motion of the input shaft is determined by the swing motion of the swing link.
  • the swing link is attached to the output shaft when attempting to rotate relative to the output shaft in one direction.
  • a one-way rotation prevention mechanism that idles the swing link with respect to the output shaft when attempting to rotate relative to the other side, and the lever crank mechanism has a radius of rotational motion on the input shaft side.
  • the transmission case includes one end wall portion positioned on one end side of the input shaft and the output shaft, the other end wall portion positioned on the other end side of the input shaft and the output shaft, and the lever crank.
  • a peripheral wall portion connecting the other end wall portion and the one end wall portion so as to cover the mechanism with a gap, and one end input side bearing is provided on one end side of the input shaft, and the one end
  • the wall portion is provided with one end input side fixing portion that receives and fixes the one end input side bearing, and the one end wall portion rotatably supports one end side of the input shaft via the one end input side bearing,
  • One end output side bearing is provided on one end side of the output shaft, and one end output side fixing portion that receives and fixes the one end output side bearing is provided on the one end wall portion.
  • One end side of the output shaft is rotated through the one end output side bearing.
  • the one end wall portion is provided with one end side cutout portion
  • the peripheral wall portion is provided with a peripheral wall side cutout portion
  • the peripheral wall side cutout portion and the one end side cutout portion are formed by the transmission case. It is characterized by being configured to have flexibility.
  • the transmission case can be bent in accordance with the bending of the input shaft and the output shaft due to the load transmission from the lever crank mechanism.
  • the outer ring of the bearing also changes its angle so as to follow the change in the angle of the inner ring of the bearing. Therefore, the difference in angle between the inner ring and the outer ring of the bearing can be reduced, and alignment errors can be suppressed. .
  • the peripheral wall portion is formed in a truss shape by forming the peripheral wall side cutout portion, and the peripheral wall side cutout portion is covered with a resin provided on the peripheral wall portion by molding.
  • the vibration damping characteristics of the peripheral wall portion are enhanced by the resin, and the noise and vibration of the continuously variable transmission can be reduced. Further, it is possible to prevent the lubricating oil from spilling from the peripheral wall side notch, and to circulate the lubricating oil in the transmission.
  • the turning radius adjustment mechanism includes an adjustment drive source, the adjustment drive source is fixed to the one end wall portion via the differential mechanism, and the differential mechanism flows out from the notch portion on the one end side. It is preferable to lubricate with a lubricating oil.
  • the one-end-side notch has the function of the oil passage for the lubricating oil to the differential mechanism, and the lubricating-oil oil passage for the differential mechanism is provided in the transmission case or the like separately from the one-end-side notch.
  • the transmission can be downsized.
  • the other end wall portion is located on the traveling drive source side.
  • the other end wall portion on the traveling drive source side is not provided with the notch portion, and the one end wall portion on the opposite side to the traveling drive source side is provided with the one end side notch portion. It becomes. Therefore, the other end wall portion is unlikely to bend unlike the one end wall portion, and it is possible to prevent the bending of the input shaft from affecting the traveling drive source.
  • Sectional drawing which shows one Embodiment of the continuously variable transmission of this invention.
  • Explanatory drawing which shows the turning radius adjustment mechanism, connecting rod, and rocking
  • Explanatory drawing explaining the change of the rotation radius of the rotation radius adjustment mechanism of this embodiment.
  • It is explanatory drawing which shows the relationship between the change of the rotation radius of the rotation radius adjustment mechanism of this embodiment, and the rocking
  • (C) shows the rocking angle of the rocking motion of the rocking link when the radius is medium and the rotation radius is small.
  • 6 is a graph showing a state in which the output shaft is rotated by six lever crank mechanisms each having a phase difference of 60 degrees in the continuously variable transmission of the present embodiment.
  • the continuously variable transmission 1 of the present embodiment receives an input central axis P1 by receiving a rotational driving force from a traveling drive source such as an internal combustion engine (not shown) or an electric motor.
  • a traveling drive source such as an internal combustion engine (not shown) or an electric motor.
  • a hollow input shaft 2 that rotates around the shaft and an output shaft 3 that is arranged in parallel to the input shaft 2 and that transmits rotational power to drive wheels (not shown) of the vehicle via a differential gear, a propeller shaft, etc. (not shown).
  • six turning radius adjusting mechanisms 4 provided on the input shaft 2.
  • Each turning radius adjusting mechanism 4 includes a cam disk 5 and a rotating disk 6.
  • the cam disks 5 have a disk shape, and are provided in pairs on the input shaft 2 so as to be eccentric from the input center axis P1 and rotate integrally with the input shaft 2.
  • Each set of cam disks 5 is arranged so as to make a round in the circumferential direction of the input shaft 2 with six sets of cam disks 5 with a phase difference of 60 degrees.
  • Each set of cam disks 5 is fitted with a disc-shaped rotating disk 6 having a receiving hole 6a for receiving the cam disk 5 so as to be eccentric and rotatable.
  • the center point of the cam disk 5 is P2
  • the center point of the rotating disk 6 is P3
  • the distance Rb between the center point P2 and the center point P3 are the same. So that it is eccentric with respect to the cam disk 5.
  • an internal tooth 6 b is provided between the pair of cam disks 5.
  • the input shaft 2 is formed with a notch hole 2 a that is positioned between a pair of cam disks 5 and that communicates the inner peripheral surface and the outer peripheral surface at a location facing the eccentric direction of the cam disk 5.
  • a pinion shaft 7 that is disposed concentrically with the input shaft 2 and has external teeth 7 a at locations corresponding to the rotary disk 6 is disposed so as to be rotatable relative to the input shaft 2.
  • the external teeth 7 a of the pinion shaft 7 mesh with the internal teeth 6 b of the rotating disk 6 through the cutout holes 2 a of the input shaft 2.
  • a differential mechanism 8 is connected to the pinion shaft 7.
  • the differential mechanism 8 is configured by a planetary gear mechanism, and includes a sun gear 9, a first ring gear 10 connected to the input shaft 2, a second ring gear 11 connected to the pinion shaft 7, a sun gear 9 and
  • a carrier 13 is provided that supports a stepped pinion 12 including a large-diameter portion 12a that meshes with the first ring gear 10 and a small-diameter portion 12b that meshes with the second ring gear 11 so as to rotate and revolve freely.
  • the rotating shaft 14a of the adjusting drive source 14 composed of an electric motor for the pinion shaft 7 is connected to the sun gear 9. If the rotational speed of the adjustment drive source 14 is the same as the rotational speed of the input shaft 2, the sun gear 9 and the first ring gear 10 rotate at the same speed, and the sun gear 9, the first ring gear 10, and the second ring The four elements of the gear 11 and the carrier 13 are locked so as not to rotate relative to each other, and the pinion shaft 7 connected to the second ring gear 11 rotates at the same speed as the input shaft 2.
  • the rotational speed of the adjustment drive source 14 is made slower than the rotational speed of the input shaft 2
  • the rotational speed of the sun gear 9 is Ns
  • the rotational speed of the first ring gear 10 is Nr1
  • the gear ratio of the sun gear 9 and the first ring gear 10 The number of rotations of the carrier 13 is (j ⁇ Nr1 + Ns) / (j + 1) where j is the number of teeth of the first ring gear 10 / the number of teeth of the sun gear 9.
  • the gear ratio between the sun gear 9 and the second ring gear 11 ((number of teeth of the second ring gear 11 / number of teeth of the sun gear 9) ⁇ (number of teeth of the large diameter portion 12a of the stepped pinion 12 / tooth of the small diameter portion 12b)
  • the number of revolutions of the second ring gear 11 is ⁇ j (k + 1) Nr1 + (k ⁇ j) Ns ⁇ / ⁇ k (j + 1) ⁇ .
  • the rotating disk 6 is eccentric with respect to the cam disk 5 so that the distance Ra and the distance Rb are the same, and therefore the center point P3 of the rotating disk 6 is the same as the input center axis P1.
  • the distance between the input center axis P1 and the center point P3, that is, the amount of eccentricity R1 can be set to “0” so as to be positioned on the axis.
  • a connecting rod 15 having a large-diameter large-diameter annular portion 15a at one end and a small-diameter annular portion 15b having a smaller diameter than the large-diameter annular portion 15a at the other end is provided at the periphery of the rotating disk 6.
  • a large-diameter annular portion 15a is rotatably fitted via a connecting rod bearing 16 made of a ball bearing.
  • the output shaft 3 is provided with six swing links 18 corresponding to the connecting rod 15 via a one-way clutch 17 as a one-way rotation prevention mechanism.
  • the one-way clutch 17 as a one-way rotation prevention mechanism is provided between the swing link 18 and the output shaft 3, and swings on the output shaft 3 when attempting to rotate relative to the output shaft 3 on one side.
  • the link 18 is fixed, and the swing link 18 is idled with respect to the output shaft 3 when attempting to rotate relative to the other side.
  • the swing link 18 is swingable with respect to the output shaft 3 when the one-way clutch 17 is idle with respect to the output shaft 3.
  • the swing link 18 is formed in an annular shape, and a swing end portion 18a connected to the small-diameter annular portion 15b of the connecting rod 15 is provided above the swing link 18.
  • the swing end portion 18a is provided with a pair of projecting pieces 18b projecting so as to sandwich the small-diameter annular portion 15b in the axial direction.
  • the pair of projecting pieces 18b are formed with through holes 18c corresponding to the inner diameter of the small-diameter annular portion 15b.
  • a connecting pin 19 is inserted into the through hole 18c and the small diameter annular portion 15b. Thereby, the connecting rod 15 and the swing link 18 are connected.
  • FIG. 3 shows a positional relationship between the pinion shaft 7 and the rotating disk 6 in a state where the eccentricity R1 of the turning radius adjusting mechanism 4 is changed.
  • FIG. 3A shows a state in which the amount of eccentricity R1 is “maximum”, so that the input center axis P1, the center point P2 of the cam disk 5, and the center point P3 of the rotating disk 6 are aligned.
  • the pinion shaft 7 and the rotating disk 6 are located. At this time, the gear ratio i is minimized.
  • FIG. 3B shows a state in which the eccentric amount R1 is set to “medium” which is smaller than that in FIG. 3A
  • FIG. 3C illustrates that the eccentric amount R1 is smaller than that in FIG. Is shown.
  • the gear ratio i is “medium” which is larger than the gear ratio i in FIG. 3A in FIG. 3B
  • “large” which is larger than the gear ratio i in FIG. 3B in FIG.
  • FIG. 3D shows a state where the amount of eccentricity R1 is “0”, and the input center axis P1 and the center point P3 of the rotary disk 6 are located concentrically.
  • the gear ratio i at this time is infinite ( ⁇ ).
  • the continuously variable transmission 1 of the present embodiment can adjust the radius of rotational motion on the input shaft 2 side by changing the amount of eccentricity R1 by the rotational radius adjusting mechanism 4.
  • the turning radius adjusting mechanism 4, the connecting rod 15, and the swing link 18 of the present embodiment constitute a lever crank mechanism 20 (four-bar link mechanism). Then, the lever crank mechanism 20 converts the rotational motion of the input shaft 2 into the swing motion of the swing link 18.
  • the continuously variable transmission 1 of this embodiment includes a total of six lever crank mechanisms 20.
  • the swing link 18 Since the small-diameter annular portion 15b of the connecting rod 15 is connected to the swing link 18 provided on the output shaft 3 via the one-way clutch 17, the swing link 18 is pushed and pulled by the connecting rod 15 to swing. Then, the output shaft 3 rotates only when the swing link 18 rotates in either the pushing direction side or the pulling direction side, and the output shaft 3 rotates when the swing link 18 rotates in the other direction. Thus, the force of the swing motion of the swing link 18 is not transmitted to the swing link 18, and the swing link 18 is idled. Since each turning radius adjusting mechanism 4 is arranged with a phase changed every 60 degrees, the output shaft 3 is rotated in turn by each turning radius adjusting mechanism 4.
  • FIG. 4A shows the case where the eccentric amount R1 is “maximum” in FIG. 3A (when the gear ratio i is the minimum)
  • FIG. 4B shows the case where the eccentric amount R1 is “ 4 (c) shows the case where the eccentric amount R1 is “small” in FIG. 3 (c) (when the gear ratio i is large).
  • the swing range ⁇ 2 of the swing link 18 with respect to the rotational movement of the turning radius adjusting mechanism 4 is shown.
  • the swing range ⁇ 2 of the swing link 18 decreases.
  • the eccentric amount R1 is “0”, the swing link 18 does not swing.
  • the position closest to the input shaft 2 in the swing range ⁇ 2 of the swing end 18a of the swing link 18 is the internal dead center, and the position farthest from the input shaft 2 is the external dead center. .
  • FIG. 5 shows the angular velocity ⁇ accompanying the change in the eccentric amount R1 of the rotational radius adjusting mechanism 4 with the rotational angle ⁇ of the rotational radius adjusting mechanism 4 of the continuously variable transmission 1 as the horizontal axis and the angular velocity ⁇ of the swing link 18 as the vertical axis.
  • the relationship of changes is shown.
  • the angular velocity ⁇ of the swing link 18 increases as the eccentric amount R1 increases (the transmission ratio i decreases).
  • FIG. 6 shows the rotation of the turning radius adjusting mechanism 4 when the six turning radius adjusting mechanisms 4 having different phases by 60 degrees are rotated (when the input shaft 2 and the pinion shaft 7 are rotated at the same speed).
  • the angular velocity ⁇ of each swing link 18 with respect to the angle ⁇ is shown.
  • the output shaft 3 is smoothly rotated by the six lever crank mechanisms 20.
  • the six lever crank mechanisms 20 are covered with the transmission case 30 at intervals.
  • the transmission case 30 is disposed opposite to the one end wall portion 32 where the adjustment drive source 14 is disposed via the differential mechanism 8 and the one end wall portion 32, and is disposed on the travel drive source side (the other end side).
  • the other end wall portion 34 is provided, and a peripheral wall portion 40 that extends integrally from the end edge of the one end wall portion 32 toward the other end wall portion 34 and is fixed to the other end wall portion 34 with a bolt 36.
  • the one end wall portion 32 is provided with a hole-like one end input side fixing portion 44 for rotatably supporting one end side of the input shaft 2 via one end input side bearings 42.
  • the one end input side bearing 42 is received and fixed to the one end input side fixing portion 44.
  • the one end wall portion 32 is provided with a hole-like one end output side fixing portion 48 for rotatably supporting one end side of the output shaft 3 via one end output side bearings 46.
  • the one end output side bearing 46 is received and fixed to the one end output side fixing portion 48.
  • the one end wall portion 32 is provided with a plurality of one end side cutout portions 50 that are cut out through in the thickness direction.
  • the one-end-side notch portion 50 includes a plurality of radial-side notch portions 52 that are formed in the periphery of the hole-shaped one-end input-side fixing portion 44, one-end input-side fixing portion 44, and one-end output-side fixing portion 48. And a plurality of inter-axis notch portions 54 formed between them.
  • the peripheral wall portion 40 is provided with a plurality of triangular peripheral wall side cutout portions 56. By the peripheral wall side cutout portion 56, the peripheral wall portion 40 is formed in a truss shape as shown in FIG.
  • some of the inter-axis notches 54 and the peripheral wall-side notches 56 located on the radially outer side of the plurality of inter-axis notches 54 are a resin 58 provided by molding. It is obscured by. According to this, the damping characteristic of the vibration of the peripheral wall portion 40 is enhanced by the resin 58, and the noise and vibration of the continuously variable transmission 1 can be reduced. Further, it is possible to prevent the lubricating oil from spilling from the peripheral wall side notch portion 56 and a part of the notch portions 54 between the shafts, and to circulate the lubricating oil in the continuously variable transmission 1.
  • the radial side cutout portion 52 of the one end wall portion 32 is covered with a differential mechanism case 8 a of the differential mechanism 8. Then, the lubricating oil in the transmission case 30 that flows out from the radial side cutout portion 52, which is a part of the one end cutout portion 50, flows into the differential mechanism case 8a. As a result, the differential mechanism 8 is lubricated with the lubricating oil that flows into the differential mechanism case 8a from the radial-side cutout portion 52.
  • the one-end-side notch 50 has a function of the oil passage for the lubricating oil to the differential mechanism 8, and separately from the one-end-side notch 50, the lubricating oil passage for the differential mechanism 8 is provided in the transmission case 30 and the like.
  • the continuously variable transmission 1 can be downsized as compared with the case where it is provided.
  • the elasticity (flexibility) of the transmission case 30 becomes larger than the conventional one by the one end side cutout portion 50 and the peripheral wall side cutout portion 56, and the input shaft 2 and the output shaft 3.
  • the transmission case 30 can also bend due to elasticity in accordance with the bending.
  • the outer ring of the one end input side bearing 42 also changes its angle so as to follow the change in the angle of the inner ring of the one end input side bearing 42, and therefore the angle between the inner ring and the outer ring of the one end input side bearing 42 (of the input shaft 2).
  • the difference between the plane orthogonal to the input center axis P1 and the angle formed by the inner ring or the outer ring of the one-end input side bearing 42 can be reduced, and alignment errors can be suppressed.
  • the rigidity of the transmission case is high (elasticity is low), and when the load from the connecting rod 15 is applied to the input shaft 2, the input shaft 2 is greatly bent. Accordingly, the bending angle of the input shaft 2 tends to be large, and there is a possibility that a large alignment error may occur between the inner ring and the outer ring of the connecting rod bearing 16 formed of a ball bearing.
  • the elasticity of the transmission case 30 is high, and even if a large load is applied to the input shaft 2 from the connecting rod 15, the transmission case 30 receives this load, The curvature of the input shaft 2 can be suppressed. Therefore, according to the continuously variable transmission 1 of the present embodiment, the angle between the inner ring and the outer ring of the connecting rod bearing 16 (the plane perpendicular to the input center axis P1 of the input shaft 2 and the inner ring or the outer ring of the one end input side bearing 42). Angle) can be reduced, and alignment errors between the inner ring and the outer ring of the connecting rod bearing 16 can be suppressed.
  • the other end wall portion 34 on the traveling drive source side is not provided with a notch. Therefore, unlike the one end wall part 32, the other end wall part 34 is hard to bend, and it is possible to prevent the bending of the input shaft 2 from affecting the travel drive source.
  • the radial side cutout portion 52 is provided only around the one-end input-side fixing portion 44 and is not provided around the one-end output-side bearing 46.
  • the radial cutout portion of the one end side cutout portion of the present invention is not limited to this, and a radial cutout portion may also be provided around the one end output side fixing portion 48.
  • the one-way clutch 17 is used as the one-way rotation prevention mechanism.
  • the one-way rotation prevention mechanism of the present invention is not limited to this, and torque is applied from the swing link 18 to the output shaft 3.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • General Details Of Gearings (AREA)
  • Retarders (AREA)
PCT/JP2013/069544 2012-09-04 2013-07-18 Transmission à variation continue Ceased WO2014038296A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2014534234A JP5882478B2 (ja) 2012-09-04 2013-07-18 無段変速機
CN201380031110.8A CN104364557B (zh) 2012-09-04 2013-07-18 无级变速器

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012194530 2012-09-04
JP2012-194530 2012-09-04

Publications (1)

Publication Number Publication Date
WO2014038296A1 true WO2014038296A1 (fr) 2014-03-13

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/069544 Ceased WO2014038296A1 (fr) 2012-09-04 2013-07-18 Transmission à variation continue

Country Status (3)

Country Link
JP (1) JP5882478B2 (fr)
CN (1) CN104364557B (fr)
WO (1) WO2014038296A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015151373A1 (fr) * 2014-03-31 2015-10-08 本田技研工業株式会社 Dispositif de commande de transmission
JPWO2015166611A1 (ja) * 2014-04-28 2017-04-20 本田技研工業株式会社 車両用動力伝達装置の構造
JP2017101785A (ja) * 2015-12-04 2017-06-08 本田技研工業株式会社 車両用動力伝達装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006162039A (ja) * 2004-12-10 2006-06-22 Aisin Ai Co Ltd 自動車等の変速装置
JP2008175305A (ja) * 2007-01-18 2008-07-31 Toyota Motor Corp 変速制御装置
JP2009058022A (ja) * 2007-08-30 2009-03-19 Toyota Motor Corp 駆動装置
JP2012506003A (ja) * 2008-10-16 2012-03-08 シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト 自動車の伝動装置のための駆動軸アッセンブリ
JP2012051539A (ja) * 2010-09-03 2012-03-15 Honda Motor Co Ltd 自動車用駆動システム及びその制御方法

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000136868A (ja) * 1998-10-30 2000-05-16 Suzuki Motor Corp トランスファケースの構造

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006162039A (ja) * 2004-12-10 2006-06-22 Aisin Ai Co Ltd 自動車等の変速装置
JP2008175305A (ja) * 2007-01-18 2008-07-31 Toyota Motor Corp 変速制御装置
JP2009058022A (ja) * 2007-08-30 2009-03-19 Toyota Motor Corp 駆動装置
JP2012506003A (ja) * 2008-10-16 2012-03-08 シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト 自動車の伝動装置のための駆動軸アッセンブリ
JP2012051539A (ja) * 2010-09-03 2012-03-15 Honda Motor Co Ltd 自動車用駆動システム及びその制御方法

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015151373A1 (fr) * 2014-03-31 2015-10-08 本田技研工業株式会社 Dispositif de commande de transmission
JPWO2015151373A1 (ja) * 2014-03-31 2017-04-13 本田技研工業株式会社 変速制御装置
JPWO2015166611A1 (ja) * 2014-04-28 2017-04-20 本田技研工業株式会社 車両用動力伝達装置の構造
JP2017101785A (ja) * 2015-12-04 2017-06-08 本田技研工業株式会社 車両用動力伝達装置

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