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WO2013042226A1 - Transmission à variation continue - Google Patents

Transmission à variation continue Download PDF

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Publication number
WO2013042226A1
WO2013042226A1 PCT/JP2011/071487 JP2011071487W WO2013042226A1 WO 2013042226 A1 WO2013042226 A1 WO 2013042226A1 JP 2011071487 W JP2011071487 W JP 2011071487W WO 2013042226 A1 WO2013042226 A1 WO 2013042226A1
Authority
WO
WIPO (PCT)
Prior art keywords
cam
rotating
continuously variable
center axis
variable transmission
Prior art date
Application number
PCT/JP2011/071487
Other languages
English (en)
Japanese (ja)
Inventor
大輔 友松
村上　新
小川　裕之
有希 荒津
Original Assignee
トヨタ自動車株式会社
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 トヨタ自動車株式会社 filed Critical トヨタ自動車株式会社
Priority to JP2013534530A priority Critical patent/JP5783260B2/ja
Priority to PCT/JP2011/071487 priority patent/WO2013042226A1/fr
Publication of WO2013042226A1 publication Critical patent/WO2013042226A1/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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/48—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members with members having orbital motion
    • F16H15/50—Gearings providing a continuous range of gear ratios
    • F16H15/52—Gearings providing a continuous range of gear ratios in which a member of uniform effective diameter mounted on a shaft may co-operate with different parts of another member

Definitions

  • the present invention includes a first and second rotating element having a common first rotation center axis, and a rolling member having a plurality of second rotation center axes arranged radially with respect to the first rotation center axis.
  • the present invention relates to a continuously variable transmission that continuously changes the speed ratio between input and output by tilting each rolling member held between a first rotating element and a second rotating element.
  • the traction planetary gear mechanism includes a third rotating element in which each rolling member is disposed on the outer peripheral surface, and a support shaft. Some include a fourth rotating element that holds the rolling member in a tiltable manner, and a transmission shaft that serves as a rotation center of the first to fourth rotating elements. In this traction planetary gear mechanism, any one of the rotating elements is fixed to the transmission shaft. In this continuously variable transmission, the gear ratio between input and output is continuously changed by tilting the rolling member. Further, some continuously variable transmissions are provided with torque cams that press at least one of the first rotating element and the second rotating element against each rolling member.
  • the torque cam includes a first cam member, a second cam member, a plurality of rollers sandwiched between the first cam member and the second cam member, and a cage that holds each roller.
  • Patent Document 1 discloses this type of continuously variable transmission.
  • a torque cam is disposed at a position sandwiched between the input disk (first rotating element) and the input shaft in the axial direction.
  • An annular portion protruding in the axial direction and toward the torque cam is formed on the radially inner portion of the input disk.
  • the outer peripheral surface of the annular portion is covered with the inner peripheral surface of the retainer of the torque cam, and the retainer is guided by the outer peripheral surface of the annular portion.
  • Patent Document 2 in this type of continuously variable transmission, an annular portion that protrudes toward the ring (first or second rotating element) side on the radially outer portion of the torque cam retainer is provided.
  • a ring formed by covering the outer peripheral surface of the ring with the inner peripheral surface of the annular portion is disclosed. In this continuously variable transmission, the cage is guided on the outer peripheral surface of the ring.
  • the annular portion for guiding the retainer of the torque cam is provided on the radially outer side or the radially inner side with respect to the retainer and the disk (ring).
  • the annular portion is provided on the radially outer side, the physique in the radial direction of the continuously variable transmission is increased.
  • an increase in the physique in the radial direction of the continuously variable transmission can be suppressed.
  • the inner diameter of the disk (ring) is reduced by the thickness of the annular part, so that the support shaft protrudes from the rolling member.
  • the width of the tilt angle of the rolling member may be reduced to reduce the gear ratio width (between the maximum gear ratio and the minimum gear ratio).
  • a disk (ring) is extended in the axial direction away from the rolling member, and is formed on the radially inner portion of the extended portion. It is necessary to provide an annular portion, which increases the axial length of the continuously variable transmission.
  • an object of the present invention is to provide a continuously variable transmission that can improve the disadvantages of the conventional example and can secure a sufficient speed ratio width while suppressing an increase in size.
  • the present invention provides a first and second rotational elements that are rotatable relative to each other and have a transmission shaft serving as a rotation center and a common first rotation center shaft disposed opposite to each other on the transmission shaft. And a second rotation center axis parallel to the first rotation center axis, and a plurality of radial rotations centered on the first rotation center axis and sandwiched between the first and second rotation elements.
  • a rolling member, a support shaft for the rolling member having both ends projecting from the rolling member, and each rolling member tilted with respect to the first rotating center axis
  • a third rotation that allows the relative rotation with respect to the transmission shaft and the first and second rotating elements to be arranged on the outer peripheral surface.
  • the rotation shaft is provided on at least one of the transmission shaft and the fourth rotation element capable of relative rotation with respect to the first to third rotation elements, and the first or second rotation element.
  • a torque cam for applying an axial force to the rolling member side.
  • the torque cam includes a first cam portion provided on a rotating element side to be disposed on the torque cam, and a second cam capable of relative rotation about the first rotation center axis with respect to the first cam portion.
  • a guide portion provided inside the radial direction of the second cam portion and the cage.
  • the guide portion extends from the radially inner portion of the cage toward the second cam portion, and is formed so that an outer peripheral surface thereof is covered with an inner peripheral surface of the second cam portion. It is desirable to be an installation part.
  • the guide portion extends from a radially inner portion of the second cam portion to a radially inner side of the cage, and is formed so that an outer peripheral surface thereof is covered with an inner peripheral surface of the cage. Part is desirable.
  • the guide portion is provided on the radially inner side of the cage, an increase in the size of the physique in the radial direction can be suppressed. Furthermore, in this continuously variable transmission, since the guide portion is provided radially inside the cage and the second cam portion, contact of the tilted support shaft with the guide portion can be avoided, and the guide portion is Since the tilting operation of the rolling member is not hindered, a sufficient speed ratio width can be ensured without increasing the axial length. Therefore, according to this continuously variable transmission, even if such a guide portion is provided, it is possible to ensure a sufficient speed ratio width without causing an increase in size in the radial direction or the axial direction. .
  • FIG. 1 is a partial sectional view showing the configuration of an embodiment of a continuously variable transmission according to the present invention.
  • FIG. 2 is a view of the torque cam as viewed from the inside in the radial direction.
  • FIG. 3 is a diagram illustrating a gap between the guide portion and each portion formed by the guide portion.
  • FIG. 4 is a diagram for explaining the guide portion of the support shaft in the carrier.
  • FIG. 5 is a diagram illustrating the iris plate.
  • FIG. 6 is a view for explaining the gap between the guide portions of other forms and the respective portions by the guide portions.
  • FIG. 1 indicates a continuously variable transmission according to this embodiment.
  • the traction planetary gear mechanism constituting the main part of the continuously variable transmission 1 includes first to fourth rotating elements 10, 20, 30, which are capable of relative rotation with each other and have a common first rotation center axis R 1.
  • 50 and a shaft 60 as a transmission shaft disposed at the rotation center of the first to fourth rotating elements 10, 20, 30, 40.
  • the continuously variable transmission 1 changes the speed ratio ⁇ between input and output by inclining the second rotation center axis R2 with respect to the first rotation center axis R1 and tilting the rolling member 50. .
  • the direction along the first rotation center axis R1 and the second rotation center axis R2 is referred to as the axial direction, and the direction around the first rotation center axis R1 is referred to as the circumferential direction.
  • the direction orthogonal to the first rotation center axis R1 is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side.
  • the first rotating element 10 and the second rotating element 20 that are arranged to face each other hold the respective rolling members 50, and each of the rolling members 50 is used as the third rotating element. It arrange
  • all of the first to fourth rotating elements 10, 20, 30, and 40 can rotate relative to the shaft 60, while the first to fourth rotations. Some of the elements 10, 20, 30, and 40 are fixed elements that cannot rotate relative to the shaft 60. In the following, the latter having a fixing element will be described as an example.
  • the shaft 60 is fixed to a fixed portion of the continuously variable transmission 1 in a housing or a vehicle body (not shown), and is a cylindrical or columnar fixed shaft configured not to rotate relative to the fixed portion. is there.
  • the continuously variable transmission 1 torque is transmitted via each rolling member 50 between the first to fourth rotating elements 10, 20, 30, 40 that do not become fixed elements. Accordingly, any one of the first to fourth rotating elements 10, 20, 30, and 40 that is not a fixed element serves as a torque (power) input unit, and another one serves as a torque output unit. It becomes.
  • the ratio of the rotational speed (the number of rotations) between any rotation element serving as an input unit and any rotation element serving as an output unit is the gear ratio ⁇ .
  • the continuously variable transmission 1 is disposed on the power transmission path of the vehicle. In that case, the input part is connected with the power source side, such as an engine and a motor, and the output part is connected with the drive wheel side.
  • each rotation element when torque is input to the rotation element as the input unit is referred to as normal drive
  • the rotation element as the output unit is in the direction opposite to that during normal drive.
  • the rotating operation of each rotating element when torque is input is called reverse driving.
  • Driving when the torque is input from the power source side to the rotating element as the input unit and the rotating element is rotated as in acceleration or the like, Driving is performed, and reverse driving is performed when torque in the opposite direction to that during forward driving is input to the rotating rotating element serving as the output unit from the driving wheel side, such as deceleration.
  • the continuously variable transmission 1 is configured to roll with the first to third rotating elements 10, 20, 30 by pressing at least one of the first and second rotating elements 10, 20 against the rolling member 50.
  • An appropriate tangential force (traction force) is generated between the member 50 and the member 50.
  • the continuously variable transmission 1 tilts each rolling member 50 on the tilt plane including the second rotation center axis R2 and the first rotation center axis R1 thereof, so Change the ratio of rotation speed (number of rotations).
  • the first and second rotating elements 10 and 20 function as a ring gear, which is called a traction planetary gear mechanism.
  • the third rotating element 30 and the fourth rotating element 40 function as a sun roller and a carrier in the traction planetary gear mechanism, respectively.
  • the rolling member 50 functions as a ball-type pinion in the traction planetary gear mechanism.
  • the first and second rotating elements 10 and 20 are referred to as “first and second rotating members 10 and 20”, respectively.
  • the third rotating element 30 is referred to as “sun roller 30”, and the fourth rotating element 40 is referred to as “carrier 40”.
  • the rolling member 50 is referred to as a “planetary ball 50”.
  • the carrier 40 is a fixing element and is fixed to the shaft 60.
  • the first and second rotating members 10 and 20 are disk members (disks) or ring members (rings) whose center axes coincide with the first rotation center axis R1, and each planetary ball is opposed in the axial direction. 50 is interposed. In this example, both are circular members.
  • the first and second rotating members 10 and 20 have a contact surface that comes into contact with an outer peripheral curved surface on the radially outer side of each planetary ball 50 described in detail later.
  • Each of the contact surfaces has, for example, a concave arc surface having a curvature equal to the curvature of the outer peripheral curved surface of the planetary ball 50, a concave arc surface having a curvature different from the curvature of the outer peripheral curved surface, a convex arc surface, or a flat surface. is doing.
  • the first and second contact surfaces are formed so that the distance from the first rotation center axis R1 to the contact point with each planetary ball 50 becomes the same length in the state of a reference position described later.
  • the contact angles ⁇ of the rotating members 10 and 20 with respect to the planetary balls 50 are set to the same angle.
  • the contact angle ⁇ is an angle from the reference to the contact point with each planetary ball 50.
  • the radial direction is used as a reference.
  • the respective contact surfaces are in point contact or surface contact with the outer peripheral curved surface of the planetary ball 50.
  • Each contact surface is radially inward with respect to the planetary ball 50 when an axial force (pressing force) is applied from the first and second rotating members 10, 20 toward the planetary ball 50. And an oblique force (normal force) is applied.
  • the first rotating member 10 acts as a torque input portion when the continuously variable transmission 1 is positively driven
  • the second rotating member 20 acts as a torque output portion when the continuously variable transmission 1 is positively driven.
  • the input shaft (first rotation shaft) 11 is connected to the first rotation member 10
  • the output shaft (second rotation shaft) 21 is connected to the second rotation member 20.
  • the input shaft 11 and the output shaft 21 can rotate relative to the shaft 60 in the circumferential direction. Further, the input shaft 11 and the output shaft 21 can perform relative rotation in the circumferential direction between the input shaft 11 and the output shaft 21 via the bearing B1 and the thrust bearing TB.
  • the input shaft 11 includes a cylindrical portion 11a and a disk portion 11b, and is disposed on the first rotating member 10 side as a torque input portion as viewed from the continuously variable transmission.
  • the input shaft 11 may be integrally molded having a cylindrical part 11a and a disk part 11b, and is formed by connecting the cylindrical part 11a and the disk part 11b with a fixing member such as a bolt. Also good.
  • the cylindrical portion 11a is a cylindrical member that covers the cylindrical or columnar rotating shaft 12 from the outside in the radial direction and is fixed to the rotating shaft 12, and the center axis thereof is the first rotation center axis R1.
  • a spline bearing is formed between the inner peripheral surface of the cylindrical portion 11a and the outer peripheral surface of the rotary shaft 12, and the cylindrical portion 11a and the rotary shaft 12 are fixed by spline fitting.
  • the rotary shaft 12 is an input rotary shaft concentrically disposed at one end of the shaft 60 and performs relative rotation in the circumferential direction with respect to the shaft 60 via a bearing (for example, a roller bearing or a needle bearing) B1. be able to. Therefore, the illustrated input shaft 11 performs relative rotation in the circumferential direction with respect to the shaft 60 via the rotary shaft 12 to which the cylindrical portion 11a is fixed and the bearing B1.
  • the disk part 11b is a disk-shaped part extending radially outward from one end of the cylindrical part 11a, and its central axis is made to coincide with the first rotation central axis R1.
  • the disk portion 11 b is formed so that the outer diameter thereof is approximately the same as the outer diameter of the first rotating member 10.
  • the output shaft 21 includes a first cylindrical portion 21a, a disk portion 21b, and a second cylindrical portion 21c.
  • the output shaft 21 may be integrally formed having a first cylindrical portion 21a, a disc portion 21b, and a second cylindrical portion 21c, and the first cylindrical portion 21a, the disc portion 21b, and the second cylindrical portion 21b. What connected the cylindrical part 21c with fixing members, such as a volt
  • the first cylindrical portion 21a is a cylindrical member that covers the first and second rotating members 10 and 20 from the outside in the radial direction, and the center axis thereof is made to coincide with the first rotation center axis R1. Further, the first cylindrical portion 21a extends in the axial direction so as to cover an axial force generating portion 70 and a disk portion 11b of the input shaft 11 which will be described later from the radially outer side.
  • the disc portion 21b is a disc-like portion extending radially inward from the extending end portion of the first cylindrical portion 21a and toward the outer peripheral surface of the cylindrical portion 11a of the input shaft 11, and its central axis Is made to coincide with the first rotation center axis R1. That is, the disk portion 21 b is disposed so as to face the disk portion 11 b of the input shaft 11.
  • the second cylindrical portion 21c has a cylindrical shape that covers the cylindrical portion 11a of the input shaft 11 from the outside in the radial direction.
  • the central axis of the second cylindrical portion 21c coincides with the first rotation center axis R1, and the inner diameter side of the disk portion 21b. Extends in the axial direction.
  • a bearing for example, a roller bearing or a needle bearing
  • a thrust bearing here, a thrust roller bearing or a thrust needle bearing
  • the output shaft 21 can rotate relative to the input shaft 11 via the bearing B2 and the thrust bearing TB.
  • an axial force generator that generates axial force in the axial direction between the input shaft 11 and the first rotating member 10 and between the output shaft 21 and the second rotating member 20. 70 and 80 are provided.
  • the axial force becomes a pressing force for pressing the first rotating member 10 and the second rotating member 20 against each planetary ball 50.
  • torque cams are used as the axial force generating portions 70 and 80.
  • the torque cam includes an annular first and second cam members opposed in the axial direction, a plurality of rotating members (rollers) sandwiched between cam surfaces of the first and second cam members, and each roller. And a retainer for holding.
  • the first and second cam members each have an annular cam portion formed with a cam surface that contacts the rolling surface of the roller.
  • the axial force generators 70 and 80 are referred to as “torque cams 70 and 80”, respectively.
  • the torque cam 70 on the input side is provided on the first cam portion 71 provided on the rotating element side to be arranged on its own side, and on the portion on the opposite side in the axial direction across the torque cam 70 with respect to the rotating element side.
  • the input-side torque cam 70 is disposed between the first rotating member 10 and the radially outer portion of the disk portion 11 b of the input shaft 11. Therefore, here, the first rotating member 10 side is the rotating element side to be disposed, and the input shaft 11 side is the side facing the rotating element side in the axial direction with the torque cam 70 interposed therebetween.
  • the torque cam 70 is attached so that the first cam member rotates integrally with the first rotating member 10, and the second cam member rotates integrally with the radially outer portion of the disk portion 11b. You may attach.
  • the first rotating member 10 and the first cam member are integrally formed, and the radially outer portion of the disk portion 11b and the second cam member are integrally formed. That is, here, as shown in FIG. 2 and FIG. 3, the first cam portion 71 of the first cam member is formed on the first rotating member 10, and the second cam member is formed on the radially outer portion of the disk portion 11b.
  • a second cam portion 72 is formed.
  • the roller 73 disposed between the first and second cam portions 71 and 72 is similarly rotatably held by an annular retainer 74 disposed therebetween.
  • the torque cam 70 generates axial force between the first rotating member 10 and the input shaft 11 and rotational torque when the first and second cam portions 71 and 72 and the roller 73 are engaged with each other. , And rotate them together.
  • the torque cam 70 includes the rollers 73 and the cage 74 along the second cam portion 72 in the circumferential direction on the radially inner side of the cage 74 and the second cam portion 72 on the input shaft 11 side.
  • a guide portion 75 for guiding is provided. That is, the guide portion 75 is provided in a region extending radially inward of the cage 74 and between the cage 74 and the second cam portion 72.
  • the guide portion 75 of the present embodiment is formed so as to extend from the radially inner portion of the cage 74 toward the second cam portion 72, and its outer peripheral surface is covered with the inner peripheral surface of the second cam portion 72. It is an annular extension part. In this example, the outer peripheral surface of the guide portion 75 is brought into contact with the inner peripheral surface of the second cam portion 72.
  • the output side torque cam 80 is configured in the same manner as the input side.
  • the torque cam 80 on the output side is provided on the first cam portion 81 provided on the rotating element side to be disposed on itself, and on the portion facing the rotating element side in the axial direction across the torque cam 80.
  • the torque cam 80 is disposed between the second rotating member 20 and the output shaft 21. Therefore, here, the second rotating member 20 side is the rotating element side to be disposed, and the output shaft 21 side is the side facing the rotating element side in the axial direction with the torque cam 80 interposed therebetween.
  • the output side torque cam 80 is connected to the output shaft 21 via the annular member 22.
  • the annular member 22 is connected to the other end of the first cylindrical portion 21a of the output shaft 21 (an end portion opposite to the extending end portion) by a fixing member such as a bolt.
  • the annular member 22 extends radially inward from the first cylindrical portion 21a.
  • the torque cam 80 is disposed between the radially inner portion of the extended annular member 22 and the second rotating member 20. As with the input side, the torque cam 80 is attached so that the first cam member rotates integrally with the second rotating member 20, and the second cam member is attached to the radially inner portion of the annular member 22. You may attach so that it may rotate integrally.
  • the torque cam 80 may be formed by integrally molding the second rotating member 20 and the first cam member, and may integrally mold the radially inner portion of the annular member 22 and the second cam member. That is, here, as shown in FIG. 2, the first cam portion 81 of the first cam member is formed on the second rotating member 20, and the second cam of the second cam member is formed on the radially inner portion of the annular member 22. The part 82 may be formed. Here, the latter is applied according to the input side.
  • a roller 83 is disposed between the first and second cam portions 81 and 82. Each roller 83 is rotatably held by an annular retainer 84 disposed between the first and second cam portions 81 and 82.
  • the torque cam 80 generates an axial force between the second rotating member 20 and the output shaft 21 and the rotational torque when the first and second cam portions 81 and 82 and the roller 83 are engaged with each other. , And rotate them together.
  • the torque cam 80 also has the rollers 83 and the retainer 84 in the second cam portion 82 on the radially inner side of the retainer 84 and the second cam portion 82 on the output shaft 21 side.
  • a guide portion 85 that guides in the circumferential direction is provided. That is, the guide portion 85 is provided in a region extending radially inside the retainer 84 and between the retainer 84 and the second cam portion 82 on the output shaft 21 side.
  • the guide portion 85 of the present embodiment is formed so as to extend from the radially inner portion of the cage 84 toward the second cam portion 82, and its outer peripheral surface is covered with the inner peripheral surface of the second cam portion 82. It is an annular extension part. In this example, the outer peripheral surface of the guide portion 85 is brought into contact with the inner peripheral surface of the second cam portion 82.
  • the continuously variable transmission 1 narrows the clearance CL1 between the first rotating member 10 and the disk portion 11b of the input shaft 11 and the first cylindrical portion 21a of the output shaft 21, as shown in FIG. Can do. Furthermore, the continuously variable transmission 1 can also narrow the gap CL2 between the second rotating member 20 and the first cylindrical portion 21a of the output shaft 21. Therefore, the continuously variable transmission 1 can suppress an increase in the size of the physique in the radial direction while providing the guide portions 75 and 85.
  • the guide portion 75 is provided radially inside the retainer 74 and the second cam portion 72 on the input shaft 11 side, and the guide portion 85 is disposed on the retainer 84 and the output shaft. It is provided on the inner side in the radial direction of the second cam portion 82 on the 21 side.
  • the guide portions 75 and 85 are disposed on the outer side (in the direction away from the planetary ball 50) in the axial direction than the first rotating member 10 and the second rotating member 20. Therefore, in the continuously variable transmission 1, as shown in FIG. 3, it is possible to avoid contact of the tilted support shaft 51 with the guide portions 75 and 85, and the support shaft 51 and the guide portions 75 and 85 A gap CL3 can be secured between the two. Therefore, in the continuously variable transmission 1, since the guide portions 75 and 85 do not hinder the tilting operation of the planetary ball 50, a sufficient speed ratio width can be secured without increasing the axial length.
  • the first rotating member 10 can be used as a torque input unit
  • the second rotating member 20 can be used as a torque output unit.
  • Is used as the output shaft and the one provided as the output shaft 21 is used as the input shaft.
  • an input shaft or an output shaft that is separately configured is connected to the sun roller 30 or the carrier 40.
  • the sun roller 30 is disposed concentrically with the shaft 60 and performs relative rotation in the circumferential direction with respect to the shaft 60.
  • a plurality of planetary balls 50 are radially arranged at substantially equal intervals on the outer peripheral surface of the sun roller 30. Accordingly, the outer peripheral surface of the sun roller 30 is a rolling surface when the planetary ball 50 rotates.
  • the sun roller 30 can roll (rotate) each planetary ball 50 by its own rotation, or it can rotate along with the rolling operation (spinning) of each planetary ball 50.
  • the sun roller 30 has a two-divided structure of a first divided structure 31 and a second divided structure 32, and each of the first divided structure 31 and the second divided structure 32 is connected to each planetary ball 50.
  • the respective contacts are located at the same distance from the center of gravity of each planetary ball 50 and at the same distance from the first rotation center axis R1.
  • the first divided structure 31 includes a first annular member 31a attached to the shaft 60 via radial bearings RB1 and RB2, and a second annular member 31b having one contact point with each planetary ball 50.
  • the first annular member 31a and the second annular member 31b are connected by a fixing member such as a bolt, for example, and can integrally rotate relative to the shaft 60 in the circumferential direction.
  • the first annular member 31a is longer in the axial direction than the second annular member 31b, and the second annular member 31b is disposed on the outer peripheral surface of the first annular member 31a via, for example, an angular bearing AB.
  • the second annular member 31b can rotate relative to the first annular member 31a in the circumferential direction, and the angular bearing AB absorbs the thrust load, Since the loss energy between the sun roller 30 and the planetary ball 50 is reduced, it is possible to suppress a reduction in power transmission efficiency.
  • the planetary ball 50 is a rolling member that rolls on the outer peripheral surface of the sun roller 30.
  • the planetary ball 50 is preferably a perfect spherical body, but it may have a spherical shape at least in the rolling direction, for example, a rugby ball having an elliptical cross section.
  • the planetary ball 50 is rotatably supported by a support shaft 51 that passes through the center of the planetary ball 50.
  • the planetary ball 50 can be rotated relative to the support shaft 51 with the second rotation center axis R2 as a rotation axis (that is, rotation) by a bearing disposed between the outer periphery of the support shaft 51.
  • the planetary ball 50 can roll on the outer peripheral surface of the sun roller 30 around the support shaft 51. Both ends of the support shaft 51 are projected from the planetary ball 50.
  • the reference position of the support shaft 51 is a position where the second rotation center axis R2 is parallel to the first rotation center axis R1, as shown in FIG.
  • the support shaft 51 is tilted from the reference position and within the tilt plane including the rotation center axis (second rotation center axis R2) and the first rotation center axis R1 formed at the reference position. It can swing (tilt) with the planetary ball 50 between the positions. The tilt is performed with the center of the planetary ball 50 as a fulcrum in the tilt plane.
  • the carrier 40 holds each protruding portion of the support shaft 51 so as not to disturb the tilting operation of each planetary ball 50.
  • the carrier 40 includes, for example, first and second disk portions 41 and 42 having a center axis coinciding with the first rotation center axis R1.
  • the first and second disk portions 41 and 42 are opposed to each other, and are disposed with a space therebetween so that the sun roller 30 and the planetary ball 50 can be disposed therebetween.
  • the carrier 40 fixes the inner diameter side of the first and second disk portions 41 and 42 to the outer diameter side of the shaft 60 and cannot perform relative rotation in the circumferential direction or relative movement in the axial direction with respect to the shaft 60. I am doing so.
  • the continuously variable transmission 1 is provided with guide portions 43 and 44 for guiding the support shaft 51 in the tilting direction when the respective planetary balls 50 are tilted.
  • the guide portions 43 and 44 are provided on the carrier 40.
  • the guide portions 43 and 44 are guide grooves and guide holes in the radial direction for guiding the support shaft 51 protruding from the planetary ball 50 in the tilt direction, and the first and second disk portions 41 and 42 are respectively provided.
  • For each planetary ball 50 (FIG. 4). That is, all the guide portions 43 and 44 are radially formed when viewed from the axial direction (for example, the direction of arrow A in FIG. 1).
  • the distance from the center axis of the support shaft 51 (second rotation center axis R2) to the contact point with the first rotation member 10 changes.
  • the distance from the central axis of the support shaft 51 to the contact point with the second rotating member 20 changes. Therefore, one of the first rotating member 10 and the second rotating member 20 rotates at a higher speed than when it is at the reference position, and the other rotates at a lower speed.
  • the second rotating member 20 has a lower rotation (deceleration) than the first rotating member 10 when the planetary ball 50 is tilted in one direction, and the first rotating member 10 is tilted in the other direction. (High speed).
  • the rotation ratio (gear ratio ⁇ ) of the first rotating member 10 with respect to the second rotating member 20 can be changed steplessly by changing the tilt angle.
  • the speed is increased ( ⁇ ⁇ 1)
  • the upper planetary ball 50 in FIG. 1 is tilted counterclockwise on the paper and the lower planetary ball 50 is tilted clockwise on the paper.
  • the time of deceleration ⁇ > 1
  • the upper planetary ball 50 in FIG. 1 is tilted in the clockwise direction on the paper
  • the lower planetary ball 50 is tilted in the counterclockwise direction on the paper.
  • the continuously variable transmission 1 is provided with a transmission that changes its transmission ratio ⁇ . Since the gear ratio ⁇ changes as the tilt angle of the planetary ball 50 changes, a tilting device that tilts each planetary ball 50 is used as the speed change device.
  • the transmission is provided with a disk-shaped iris plate (tilting element) 90.
  • the iris plate 90 is attached to the shaft 60 via, for example, a radially inner bearing, and can rotate relative to the shaft 60 about the first rotation center axis R1.
  • An actuator such as a motor (not shown) is used for the relative rotation.
  • the driving force of the driving unit is transmitted to the outer peripheral portion of the iris plate 90 via the worm gear 91 shown in FIG.
  • the iris plate 90 is on the input side (contact portion side with the first rotating member 10) or output side (contact portion side with the second rotating member 20) of each planetary ball 50 and on the outside or inside of the carrier 40. Deploy. In this example, it is arranged on the output side and inside the carrier 40, that is, between the sun roller 30 and each planetary ball 50 and the second disk portion 42.
  • the iris plate 90 is formed with a throttle hole (iris hole) 92 into which one protrusion of the support shaft 51 is inserted. If the radial direction starting from the radial inner end is assumed to be the reference line L, the throttle hole 92 has an arc shape that moves away from the reference line L in the circumferential direction from the radial inner side toward the radial outer side. (FIG. 5).
  • FIG. 5 is a view seen from the direction of arrow A in FIG.
  • One projecting portion of the support shaft 51 moves to the center side of the iris plate 90 along the aperture hole 92 when the iris plate 90 rotates in the clockwise direction in FIG.
  • the respective protrusions of the support shaft 51 are inserted into the guide grooves 43 and 44 of the carrier 40, one of the protrusions inserted into the throttle hole 92 moves radially inward.
  • one of the protrusions moves to the outer peripheral side of the iris plate 90 along the aperture hole 92 when the iris plate 90 rotates counterclockwise in FIG.
  • the one protrusion moves outward in the radial direction by the action of the guide grooves 43 and 44.
  • the support shaft 51 can move in the radial direction by the guide grooves 43 and 44 and the throttle hole 92. Therefore, the planetary ball 50 can be tilted as described above.
  • the continuously variable transmission 1 has the guide portion 75 disposed radially inside the cage 74 and the second cam portion 72 on the input shaft 11 side, and the guide portion 85 is disposed. It arrange
  • the guide portions 75 and 85 extend from the radially inner portions of the cages 74 and 84 toward the second cam portions 72 and 82, for example.
  • the outer peripheral surface may be a plurality of arc-shaped extending portions formed so as to be covered with the inner peripheral surfaces of the second cam portions 72 and 82.
  • the respective arcuate guide portions 75 and 85 have the same outer diameter and inner diameter.
  • it is desirable that the arc-shaped extending portions are arranged radially at substantially equal intervals and centered on the first rotation center axis R1.
  • the guide portion is formed so as to extend from the radially inner portion of the cage 74 toward the second cam portion 72 and to cover the outer peripheral surface thereof with the inner peripheral surface of the second cam portion 72.
  • 75 and a guide portion 85 that extends from the radially inner portion of the cage 84 toward the second cam portion 82 and is formed so that its outer peripheral surface is covered with the inner peripheral surface of the second cam portion 82.
  • guide portions 175 and 185 shown in FIG. 6 may be applied instead of the guide portions 75 and 85, and the same effects as when the guide portions 75 and 85 are applied are obtained. Obtainable.
  • the guide portion 175 on the input side extends from the radially inner portion of the second cam portion 72 to the radially inner side of the cage 74 and is formed so that its outer peripheral surface is covered with the inner peripheral surface of the cage 74 Or a plurality of arc-shaped extending portions.
  • the output-side guide portion 185 is formed so as to extend from the radially inner portion of the second cam portion 82 to the radially inner side of the cage 84, and its outer peripheral surface is covered with the inner peripheral surface of the cage 84. It is the cyclic

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

L'invention concerne une transmission à variation continue comportant : un premier et un second éléments rotatifs (10, 20) arrangés de manière opposée l'un par rapport à l'autre ; de multiple billes planétaires (50) arrangées selon une configuration radiale et prises en sandwich entre le premier et le second éléments rotatifs (10, 20) ; un rouleau planétaire (30) au niveau de la surface circonférentielle extérieure sur laquelle chaque bille planétaire (50) est arrangée ; un support (40) qui supporte les billes planétaires (50) d'une manière inclinable par le biais des pièces saillantes des arbres de support respectifs (51) ; et des cames de couple (70, 80), qui sont mises en œuvre sur l'un ou les deux parmi le premier et le second éléments rotatifs (10, 20), et qui exercent une force axiale par rapport à ces éléments rotatifs vers chaque bille planétaire (50). Les cames de couple (70, 80) comportent : des premières pièces de came (71, 81) côté élément rotatif ; des secondes pièces de came (72, 82) ; des rouleaux multiples (73, 83) arrangés entre celles-ci ; des pièces de retenue (74, 84) qui sont arrangées entre les rouleaux et qui retiennent chaque rouleau (73, 83) ; et des pièces de guidage (75, 85) mises en œuvre sur l'intérieur, dans le sens radial, des pièces de retenue (74, 84) et des secondes pièces de came (72, 82).
PCT/JP2011/071487 2011-09-21 2011-09-21 Transmission à variation continue WO2013042226A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2013534530A JP5783260B2 (ja) 2011-09-21 2011-09-21 無段変速機
PCT/JP2011/071487 WO2013042226A1 (fr) 2011-09-21 2011-09-21 Transmission à variation continue

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2011/071487 WO2013042226A1 (fr) 2011-09-21 2011-09-21 Transmission à variation continue

Publications (1)

Publication Number Publication Date
WO2013042226A1 true WO2013042226A1 (fr) 2013-03-28

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JP (1) JP5783260B2 (fr)
WO (1) WO2013042226A1 (fr)

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WO2017201078A1 (fr) * 2016-05-20 2017-11-23 Fallbrook Intellectual Property Company Llc Systèmes et procédés de génération de force axiale
US9950608B2 (en) 2005-10-28 2018-04-24 Fallbrook Intellectual Property Company Llc Electromotive drives
US10047861B2 (en) 2016-01-15 2018-08-14 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
US10056811B2 (en) 2007-04-24 2018-08-21 Fallbrook Intellectual Property Company Llc Electric traction drives
US10066713B2 (en) 2008-06-23 2018-09-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10066712B2 (en) 2010-03-03 2018-09-04 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10094453B2 (en) 2007-02-16 2018-10-09 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10100927B2 (en) 2007-11-16 2018-10-16 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US10197147B2 (en) 2010-11-10 2019-02-05 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10253880B2 (en) 2008-10-14 2019-04-09 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10260607B2 (en) 2007-02-12 2019-04-16 Fallbrook Intellectual Property Company Llc Continuously variable transmissions and methods therefor
US10260629B2 (en) 2007-07-05 2019-04-16 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10323732B2 (en) 2013-04-19 2019-06-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10400872B2 (en) 2015-03-31 2019-09-03 Fallbrook Intellectual Property Company Llc Balanced split sun assemblies with integrated differential mechanisms, and variators and drive trains including balanced split sun assemblies
US10428915B2 (en) 2012-01-23 2019-10-01 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10428939B2 (en) 2003-02-28 2019-10-01 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10458526B2 (en) 2016-03-18 2019-10-29 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, systems and methods
US10634224B2 (en) 2008-06-06 2020-04-28 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10704657B2 (en) 2008-08-26 2020-07-07 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10704687B2 (en) 2007-12-21 2020-07-07 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
US10703372B2 (en) 2007-02-01 2020-07-07 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US10711869B2 (en) 2005-11-22 2020-07-14 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10746270B2 (en) 2009-04-16 2020-08-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US11174922B2 (en) 2019-02-26 2021-11-16 Fallbrook Intellectual Property Company Llc Reversible variable drives and systems and methods for control in forward and reverse directions
US11215268B2 (en) 2018-11-06 2022-01-04 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same
US11454303B2 (en) 2005-12-09 2022-09-27 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US11598397B2 (en) 2005-12-30 2023-03-07 Fallbrook Intellectual Property Company Llc Continuously variable gear transmission
US11667351B2 (en) 2016-05-11 2023-06-06 Fallbrook Intellectual Property Company Llc Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmission

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US10428939B2 (en) 2003-02-28 2019-10-01 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US9950608B2 (en) 2005-10-28 2018-04-24 Fallbrook Intellectual Property Company Llc Electromotive drives
US10711869B2 (en) 2005-11-22 2020-07-14 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US11454303B2 (en) 2005-12-09 2022-09-27 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US11598397B2 (en) 2005-12-30 2023-03-07 Fallbrook Intellectual Property Company Llc Continuously variable gear transmission
US10703372B2 (en) 2007-02-01 2020-07-07 Fallbrook Intellectual Property Company Llc Systems and methods for control of transmission and/or prime mover
US10260607B2 (en) 2007-02-12 2019-04-16 Fallbrook Intellectual Property Company Llc Continuously variable transmissions and methods therefor
US10094453B2 (en) 2007-02-16 2018-10-09 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10056811B2 (en) 2007-04-24 2018-08-21 Fallbrook Intellectual Property Company Llc Electric traction drives
US10260629B2 (en) 2007-07-05 2019-04-16 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US11125329B2 (en) 2007-11-16 2021-09-21 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US10100927B2 (en) 2007-11-16 2018-10-16 Fallbrook Intellectual Property Company Llc Controller for variable transmission
US10704687B2 (en) 2007-12-21 2020-07-07 Fallbrook Intellectual Property Company Llc Automatic transmissions and methods therefor
US10634224B2 (en) 2008-06-06 2020-04-28 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10066713B2 (en) 2008-06-23 2018-09-04 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10704657B2 (en) 2008-08-26 2020-07-07 Fallbrook Intellectual Property Company Llc Continuously variable transmission
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US10746270B2 (en) 2009-04-16 2020-08-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10066712B2 (en) 2010-03-03 2018-09-04 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10197147B2 (en) 2010-11-10 2019-02-05 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10428915B2 (en) 2012-01-23 2019-10-01 Fallbrook Intellectual Property Company Llc Infinitely variable transmissions, continuously variable transmissions, methods, assemblies, subassemblies, and components therefor
US10323732B2 (en) 2013-04-19 2019-06-18 Fallbrook Intellectual Property Company Llc Continuously variable transmission
US10400872B2 (en) 2015-03-31 2019-09-03 Fallbrook Intellectual Property Company Llc Balanced split sun assemblies with integrated differential mechanisms, and variators and drive trains including balanced split sun assemblies
US11306818B2 (en) 2016-01-15 2022-04-19 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
US10047861B2 (en) 2016-01-15 2018-08-14 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
US10920882B2 (en) 2016-01-15 2021-02-16 Fallbrook Intellectual Property Company Llc Systems and methods for controlling rollback in continuously variable transmissions
US10458526B2 (en) 2016-03-18 2019-10-29 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, systems and methods
US11667351B2 (en) 2016-05-11 2023-06-06 Fallbrook Intellectual Property Company Llc Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmission
US12145690B2 (en) 2016-05-11 2024-11-19 Enviolo B.V. Systems and methods for automatic configuration and automatic calibration of continuously variable transmissions and bicycles having continuously variable transmissions
WO2017201078A1 (fr) * 2016-05-20 2017-11-23 Fallbrook Intellectual Property Company Llc Systèmes et procédés de génération de force axiale
US10253881B2 (en) 2016-05-20 2019-04-09 Fallbrook Intellectual Property Company Llc Systems and methods for axial force generation
CN109154384A (zh) * 2016-05-20 2019-01-04 福博科知识产权有限责任公司 用于产生轴向力的系统和方法
US11215268B2 (en) 2018-11-06 2022-01-04 Fallbrook Intellectual Property Company Llc Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same
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US12173778B2 (en) 2018-11-06 2024-12-24 Enviolo B.V. Continuously variable transmissions, synchronous shifting, twin countershafts and methods for control of same
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US11530739B2 (en) 2019-02-26 2022-12-20 Fallbrook Intellectual Property Company Llc Reversible variable drives and systems and methods for control in forward and reverse directions
US12000458B2 (en) 2019-02-26 2024-06-04 Fallbrook Intellectual Property Company Llc Reversible variable drives and systems and methods for control in forward and reverse directions

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