JP5621947B2 - Continuously variable transmission - Google Patents

Description

  The present invention relates to a continuously variable transmission.

  As a conventional transmission of a so-called traction drive system, for example, Patent Document 1 discloses a transmission shaft serving as a rotation center, and a plurality of rotational elements capable of relative rotation with the center axis of the transmission shaft as a first rotation center axis. A continuously variable transmission (CONTINUOUSLY VARIABLE TRANSMISSION) including a plurality of planetary balls as rolling members arranged radially about a first rotation center axis is disclosed. This continuously variable transmission includes an input / output ring that sandwiches a planetary ball, a carrier that supports the planetary ball in a tiltable manner, a sun roller whose outer peripheral surface is in contact with the planetary ball, and the like as a plurality of rotating elements. The gear ratio is steplessly changed by tilting the ball. In the continuously variable transmission, for example, guide end portions are provided at both ends of the support shaft (spindle) of the planetary ball, and the guide end portion of the support shaft is guided while the fixed carrier and the movable carrier are relatively rotated. The planetary ball is tilted together with the support shaft to change the gear ratio.

US Patent Application Publication No. 2010/0267510

  By the way, the continuously variable transmission described in Patent Document 1 as described above has room for further improvement, for example, in terms of a shift operation involving a tilting operation of a planetary ball.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a continuously variable transmission capable of realizing a smooth speed change operation.

  In order to achieve the above-mentioned object, a continuously variable transmission according to the present invention is arranged such that a transmission shaft serving as a rotation center and the transmission shaft are opposed to each other in the axial direction, with a common first rotation center axis as the rotation center. A first rotation element and a second rotation element that are rotatable relative to each other; a rotation center that is different from the first rotation center axis; and the first rotation element and the second rotation element. A rolling member that is sandwiched between the first rotating element and the second rotating element and that supports the rolling member with the second rotation center axis as a center of rotation, and both end portions are A support shaft projecting from a rolling member; and the support shaft is disposed on the transmission shaft so as to be rotatable relative to the first rotation element and the second rotation element about the first rotation center axis. Phase with the transmission shaft A fixed element provided in a non-rotatable manner, and a movable element provided opposite to the fixed element on the other end side of the support shaft and provided to be rotatable relative to the transmission shaft, and holds the support shaft A support rotation element, the support rotation element is formed in the fixed element so as to extend in a direction perpendicular to the first rotation center axis and open toward the rolling member. A first guide end, which is one end, is inserted to guide the movement of the first guide end, and the movable element is inclined with respect to a direction orthogonal to the first rotation center axis. The second guide end that is the other end of the support shaft is inserted and can be guided to move along the second guide end. The support shaft is moved forward by the second guide part. The rolling member is held in a state where tilting operation is possible, and together with the support shaft by the relative displacement of the first guide part and the second guide part with relative rotation of the fixed element and the movable element, The speed change ratio, which is the rotational speed ratio between the rotating elements, can be changed by tilting the rolling member, and the support shaft can be moved with the moving distance of the first guide end when tilting together with the rolling member. The movement distance of one of the second guide end portions is relatively large and the other movement distance is relatively small. The first guide end portion and the second guide end portion are The outer diameter of the relatively large moving distance is relatively larger than the outer diameter of the relatively small moving distance.

  In the continuously variable transmission, the ratio of the outer diameter of the first guide end to the outer diameter of the second guide end is set so that the first support shaft is tilted together with the rolling member. The moving distance of the guide end portion may be equivalent to the ratio of the moving distance of the second guide end portion.

  Further, in the continuously variable transmission, the movement distance of the first guide end when the support shaft tilts together with the rolling member is the contact between the first guide end and the first guide. The movement distance of the second guide end when the support shaft is tilted together with the rolling member is defined based on the distance from the rolling center of the rolling member. It can be defined based on the distance between the contact point with the second guide part and the rolling center of the rolling member.

  In the continuously variable transmission, the ratio of the outer diameter of the first guide end to the outer diameter of the second guide end is determined by the contact between the first guide end and the first guide It shall be equivalent to the ratio of the distance between the rolling center of the rolling member and the distance between the contact point between the second guide end and the second guide portion and the rolling center of the rolling member. Can do.

  Further, in the continuously variable transmission, at least one of the first guide end and the second guide end is between the first guide end and the second guide end of the support shaft. It can be configured separately from the intermediate part and assembled to the intermediate part.

  Further, in the continuously variable transmission, at least one of the first guide end and the second guide end is between the first guide end and the second guide end of the support shaft. It may be configured to include a roller assembled so as to be rotatable relative to the intermediate portion.

  In the continuously variable transmission, the support shaft is provided so as to be rotatable integrally with the rolling member, and the first guide end portion includes a first bearing interposed between the first guide portion and the first guide end portion. The second guide end portion includes a second bearing interposed between the second guide portion and the second guide end portion.

  The continuously variable transmission according to the present invention has an effect that a smooth speed change operation can be realized.

FIG. 1 is a schematic cross-sectional view of a continuously variable transmission according to a first embodiment. FIG. 2 is a partial cross-sectional view of the continuously variable transmission according to the first embodiment. FIG. 3 is a plan view illustrating a fixed carrier of the continuously variable transmission according to the first embodiment. FIG. 4 is a plan view illustrating the movable carrier of the continuously variable transmission according to the first embodiment. FIG. 5 is a plan view for explaining a plate of the continuously variable transmission according to the first embodiment. FIG. 6 is a configuration diagram illustrating a configuration of a support shaft of the continuously variable transmission according to the first embodiment. FIG. 7 is a partial cross-sectional view of the continuously variable transmission according to the second embodiment. FIG. 8 is a configuration diagram illustrating a configuration of a support shaft of a continuously variable transmission according to a modification. FIG. 9 is a configuration diagram illustrating a configuration of a support shaft of a continuously variable transmission according to a modification. FIG. 10 is a configuration diagram illustrating a configuration of a support shaft of a continuously variable transmission according to a modification.

  Embodiments according to the present invention will be described below in detail with reference to the drawings. In addition, this invention is not limited by this embodiment. In addition, constituent elements in the following embodiments include those that can be easily replaced by those skilled in the art or those that are substantially the same.

[Embodiment 1]
1 is a schematic sectional view of a continuously variable transmission according to a first embodiment, FIG. 2 is a partial sectional view of the continuously variable transmission according to the first embodiment, and FIG. 3 is a sectional view of the continuously variable transmission according to the first embodiment. FIG. 4 is a plan view illustrating a movable carrier of the continuously variable transmission according to the first embodiment, and FIG. 5 is a plan view illustrating a plate of the continuously variable transmission according to the first embodiment. FIG. 6 is a configuration diagram illustrating the configuration of the support shaft of the continuously variable transmission according to the first embodiment.

  The continuously variable transmission of the present embodiment is mounted on a vehicle and transmits power (torque) generated by a power source such as an internal combustion engine to drive wheels of the vehicle. This continuously variable transmission is a so-called traction drive type continuously variable transmission that can transmit power between the rotating elements by a fluid such as traction oil (transmitted oil) interposed between the rotating elements in contact with each other. The continuously variable transmission uses the resistance force (traction force, shear force of the traction oil film) generated when shearing the traction oil intervening on the contact surface between one rotating element and the other rotating element to provide power (torque). To communicate. The continuously variable transmission according to the present embodiment is a so-called ball planetary continuously variable transmission (CVP: Continuously Variable Planetary).

  Specifically, as shown in FIGS. 1 and 2, the continuously variable transmission mechanism that forms the main part of the continuously variable transmission 1 of the present embodiment has a common first rotation center axis R <b> 1. The first rotating member 10 as the first rotating element capable of relative rotation, the second rotating member 20 as the second rotating element, the sun roller 30 as the third rotating element, and the carrier as the fourth rotating element and the supporting rotating element 40. Further, the continuously variable transmission 1 includes a planetary ball 50 as a plurality of rolling members each having a second rotation center axis R2 different from the first rotation center axis R1, the first rotation member 10, and the second rotation member 20. And a transmission shaft 60 serving as a rotation center of the sun roller 30 or the like. The continuously variable transmission 1 tilts the second rotation center axis R2 with respect to the first rotation center axis R1 and tilts the planetary ball 50 that is tiltably held by the carrier 40, so The gear ratio is changed.

  In the following description, unless otherwise specified, a direction along the first rotation center axis R1 or the second rotation center axis R2 is referred to as an axial direction, and a direction around the first rotation center axis R1 is referred to as a circumferential direction. Further, a direction orthogonal to the first rotation center axis R1 is referred to as a radial direction, and among these, a side facing inward is referred to as a radial inner side, and a side facing outward is referred to as a radial outer side.

  In the continuously variable transmission 1, torque is typically transmitted between the first rotating member 10, the second rotating member 20, the sun roller 30, and the carrier 40 via each planetary ball 50. For example, in the continuously variable transmission 1, one of the first rotating member 10, the second rotating member 20, the sun roller 30, and the carrier 40 serves as a torque (power) input unit, and at least one of the remaining rotating elements is Torque output section. In the continuously variable transmission 1, the ratio of the rotation speed (the number of rotations) between any rotation element serving as an input unit and any rotation element serving as an output unit is a gear ratio. Here, the continuously variable transmission 1 will be described with respect to a case where the first rotating member 10 is an input unit and the second rotating member 20 is an output unit.

  In the continuously variable transmission 1, a plurality of planetary balls 50 are arranged radially about the center axis (first rotation center axis R <b> 1) of the transmission shaft 60. The planetary ball 50 can rotate (spin) about the second rotation center axis R2 as the rotation center. The planetary ball 50 is sandwiched between the first rotating member 10 and the second rotating member 20 that are disposed on the transmission shaft 60 so as to face the transmission shaft 60 in the axial direction. The planetary ball 50 is supported by the carrier 40 so as to be able to rotate. The continuously variable transmission 1 presses at least one of the first rotating member 10 and the second rotating member 20 against the planetary ball 50, whereby the first rotating member 10, the second rotating member 20, the sun roller 30 and the planetary ball 50. Appropriate frictional force (traction force) is generated between them and torque can be transmitted between them. The continuously variable transmission 1 tilts the planetary ball 50 on a tilt plane including the second rotation center axis R2 and the first rotation center axis R1, and the first rotation member 10 and the second rotation member 20 By changing the ratio of the rotational speed (rotational speed) between the input and output, the ratio of the rotational speed (rotational speed) between the input and output is changed.

  Note that the continuously variable transmission 1 includes the first rotating member 10, the second rotating member 20, the sun roller 30, and the carrier 40 that are all rotatable relative to the transmission shaft 60. There is a configuration in which any one of the second rotating member 20, the sun roller 30, and the carrier 40 cannot be rotated relative to the transmission shaft 60. In the following, an example in which a part of the carrier 40 is fixed to the transmission shaft 60 will be described, but the present invention is not limited to this. Here, the transmission shaft 60 is formed in a columnar shape with the center axis coinciding with the first rotation center axis R1, and is fixed to a fixed portion of the continuously variable transmission 1 in a housing or a vehicle body (not shown). It is the fixed axis | shaft comprised so that it may not be rotated relative to.

  Hereinafter, each component of the continuously variable transmission 1 will be described in detail.

  The first rotating member 10 and the second rotating member 20 are a disk member (disk) or an annular member (ring) whose center axis coincides with the first rotation center axis R1, and the axial direction of the first rotation center axis R1 The planetary balls 50 are disposed so as to face each other. In this example, both are circular members. The first rotating member 10 and the second rotating member 20 are relatively rotatable with the common first rotation center axis R1 as the rotation center.

  The first rotating member 10 and the second rotating member 20 have contact surfaces 10 a and 20 a that are in contact with the outer peripheral curved surface on the radially outer side of each planetary ball 50 on the inner peripheral surface. The contact surfaces 10a and 20a of the first rotating member 10 and the second rotating member 20 are, for example, a concave arc surface having a curvature equivalent to the curvature of the outer peripheral curved surface of the planetary ball 50, and a concave arc having a curvature different from the curvature of the outer peripheral curved surface. It has a shape such as a surface, a convex arc surface, or a flat surface. Here, each contact surface 10a, 20a is in a state of a reference position described later (a state in which the first rotation center axis R1 and the second rotation center axis R2 are parallel), and the planetary ball from the first rotation center axis R1. 50 so that the distance to the contact portion is equal to each other, and the contact angles θ of the first rotating member 10 and the second rotating member 20 with respect to the planetary balls 50 are equal to each other. Yes.

  Here, the contact angle θ is an angle from the reference to the contact portion between the planetary ball 50 and each contact surface 10a, 20a. Here, the radial direction is used as a reference. Contact surfaces 10 a and 20 a of the first rotating member 10 and the second rotating member 20 with the planetary ball 50 are in point contact or surface contact with the outer peripheral curved surface of the planetary ball 50. Further, the contact surfaces 10 a and 20 a of the first rotating member 10 and the second rotating member 20 with the planetary ball 50 are subjected to an axial force from the first rotating member 10 and the second rotating member 20 toward the planetary ball 50. In this case, a force (normal force Fn) is applied to the planetary ball 50 radially inward and in an oblique direction (normal force Fn).

  The continuously variable transmission 1 causes the first rotating member 10 to function as a torque input unit (input ring) when the continuously variable transmission 1 is driven forward (when torque is input to a rotating element as an input unit). The continuously variable transmission 1 causes the second rotating member 20 to function as a torque output unit (output ring) when the continuously variable transmission 1 is driven forward. In the continuously variable transmission 1, the input shaft 11 is connected to the first rotating member 10 via a torque cam 70. In the continuously variable transmission 1, the output shaft 21 is connected to the second rotating member 20 via a torque cam 71. The input shaft 11 includes a cylindrical part 11a, a disk part 11b, and the like. The input shaft 11 is connected to the first rotating member 10 via the torque cam 70 on the disk portion 11b side, and connected to the power source side of the vehicle on the cylindrical portion 11a side. The output shaft 21 includes a first cylindrical portion 21a, a disk portion 21b, a second cylindrical portion 21c, and the like. The output shaft 21 is connected to the second rotating member 20 through the annular member 72 and the torque cam 71 on the first cylindrical portion 21a side, and is connected to the drive wheel side of the vehicle on the second cylindrical portion 21c side. The input shaft 11 and the output shaft 21 are provided so as to be rotatable relative to the transmission shaft 60 about the first rotation center axis R1. The input shaft 11 and the output shaft 21 can be rotated relative to each other via the bearing B1 and the thrust bearing TB.

  The torque cams 70 and 71 are torque axial force conversion mechanisms that convert rotational torque into axial force along the first rotation center axis R1, and are pressing force generation mechanisms. The axial force generated by the torque cams 70 and 71 is a pressing force for pressing the first rotating member 10 and the second rotating member 20 against each planetary ball 50. The torque cam 70 is disposed between the first rotating member 10 and the input shaft 11. The torque cam 71 is disposed between the second rotating member 20 and the output shaft 21. When the torque cam 70 transmits the rotational torque between the input shaft 11 and the first rotating member 10, each planet along the axial direction with respect to the first rotating member 10 according to the magnitude of the transmitted torque. A thrust (axial force) toward the ball 50 is generated. When the torque cam 71 transmits the rotational torque between the output shaft 21 and the second rotating member 20, each planet along the axial direction with respect to the second rotating member 20 according to the magnitude of the transmitted torque. A thrust (axial force) toward the ball 50 is generated.

  In the continuously variable transmission 1, the first rotating member 10 can be used as a torque output unit, and the second rotating member 20 can be used as a torque input unit. Is used as the output shaft, and the one provided as the output shaft 21 is used as the input shaft. In the continuously variable transmission 1, when the sun roller 30 or the carrier 40 is used as a torque input unit or a torque output unit, an input shaft or an output shaft that is separately configured is connected to the sun roller 30 or the carrier 40 described later. .

  The sun roller 30 has a cylindrical shape with a center axis coinciding with the first rotation center axis R1, and is supported by the bearings RB1 and RB2 so as to be able to rotate relative to the transmission shaft 60 in the circumferential direction. That is, the sun roller 30 is disposed on the transmission shaft 60 so as to be relatively rotatable with respect to the transmission shaft 60, the first rotating member 10, the second rotating member 20, and the carrier 40 described later, with the first rotation center axis R1 as the rotation center. . Further, the sun roller 30 is positioned with respect to the axial direction of the transmission shaft 60 by the outer ring of the bearing RB1, the outer ring of the bearing RB2, and the like, and is fixed so as not to move relative to the axial direction of the transmission shaft 60.

  The outer surface 31 of the sun roller 30 is in contact with a plurality of planetary balls 50. On the outer peripheral surface 31 of the sun roller 30, a plurality of planetary balls 50 are radially arranged at substantially equal intervals. Therefore, the outer surface 31 of the sun roller 30 becomes 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 (rotational) movement of each planetary ball 50.

  The sun roller 30 of the present embodiment includes a bearing RB1, a first divided structure 32 supported by the bearing RB2, a second divided structure 33 fixed to the outer peripheral surface of the first divided structure 32, and a first divided structure. It has a divided structure consisting of three parts of a third divided structure 34 supported on the outer peripheral surface of the body 32 via an angular bearing AB. Thereby, this continuously variable transmission 1 can reduce the spin loss between the sun roller 30 and the planetary ball 50, and can suppress the fall of power transmission efficiency. In this case, the outer peripheral surface 31 of the sun roller 30 is constituted by the outer peripheral surface of the second divided structure 33 and the outer peripheral surface of the third divided structure 34. The sun roller 30 may not have such a divided structure.

  The carrier 40 is disposed on the transmission shaft 60 and is rotatable relative to the first rotating member 10, the second rotating member 20, the sun roller 30, etc. with the first rotation center axis R <b> 1 as the rotation center, and a support shaft ( The spindle 51 is held in a state in which the planetary ball 50 can be tilted.

  Here, the planetary ball 50 is tiltably held by the carrier 40 via the support shaft 51. The planetary ball 50 is a rolling member that rolls on the outer peripheral surface 31 of the sun roller 30. The planetary ball 50 is preferably a perfect sphere, but 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 support shaft 51 supports the planetary ball 50 with the second rotation center axis R <b> 2 as the rotation center, and both end portions protrude from the planetary ball 50. For example, the planetary ball 50 can be rotated relative to the support shaft 51 with the second rotation center axis R2 as the rotation axis (that is, rotation) by the radial bearings RB3 and RB4 disposed between the outer periphery of the support shaft 51. I am doing so. Therefore, the planetary ball 50 can roll on the outer peripheral surface 31 of the sun roller 30 around the second rotation center axis R2 of the support shaft 51.

  As shown in FIG. 1, 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. The support shaft 51 includes a reference position and a position inclined from the reference position in a tilt plane including the rotation center axis (second rotation center axis R2) and the first rotation center axis R1 formed at the reference position. Can be swung (tilted) together with the planetary ball 50. This tilt is performed with the center of the planetary ball 50 as a fulcrum in the tilt plane. Then, both ends of the support shaft 51 protruding from the planetary ball 50 are held in a state where the planetary balls 50 can be tilted by the carrier 40 as described below.

  The carrier 40 supports the end portion of the support shaft 51 that supports the planetary ball 50 so as not to prevent the tilting operation of each planetary ball 50. The carrier 40 of this embodiment includes a fixed carrier 41 as a fixed element, a movable carrier 42 as a movable element, and a plate 43. Each of the fixed carrier 41, the movable carrier 42, and the plate 43 is an annular plate having a central axis that coincides with the first rotation central axis R1, and is provided on the transmission shaft 60. Here, the fixed carrier 41 is disposed on the radially inner side of the first rotating member 10, the torque cam 70, and the like, and the movable carrier 42 and the plate 43 are disposed on the radially inner side of the second rotating member 20, the torque cam 71, and the like. .

  The fixed carrier 41 is provided on the first guide end 52 side, which is one end of the support shaft 51, so as not to rotate relative to the transmission shaft 60. The fixed carrier 41 is fixed to the flange portion of the transmission shaft 60 via a bolt or the like on the inner peripheral surface side. The movable carrier 42 is disposed on the second guide end 53 side, which is the other end of the support shaft 51, so as to face the fixed carrier 41, and is provided so as to be rotatable relative to the transmission shaft 60. That is, the fixed carrier 41 and the movable carrier 42 are disposed so as to face each other with the planetary ball 50 interposed therebetween in the axial direction of the first rotation center axis R1. The movable carrier 42 is supported on the outer peripheral surface of the transmission shaft 60 via a bearing or the like on the inner peripheral surface side so as to be relatively rotatable about the first rotation center axis R1. Therefore, the movable carrier 42 and the fixed carrier 41 are relatively rotatable with the first rotation center axis R1 as the rotation center. The plate 43 is disposed between the planetary ball 50 and the movable carrier 42 with respect to the axial direction of the first rotation center axis R1, and is provided so as not to rotate relative to the fixed carrier 41. The plate 43 is fixed to the fixed carrier 41 via a plurality of connecting shafts along the axial direction of the first rotation center axis R1. The fixed carrier 41 and the plate 43 have a bowl-like structure as a whole by being connected via a connecting shaft or the like. Therefore, the movable carrier 42 and the plate 43 can be rotated relative to each other about the first rotation center axis R1. The fixed carrier 41 has a first guide part 44, the movable carrier 42 has a second guide part 45, and the plate 43 has a slit part 46.

  As shown in FIGS. 1, 2, and 3, the first guide portion 44 is formed on the fixed carrier 41 so as to extend in the radial direction perpendicular to the first rotation center axis R <b> 1 and open toward the planetary ball 50. Is done. The first guide portion 44 is formed as a bottomed guide groove portion, that is, has a configuration that does not penetrate the fixed carrier 41 with respect to the axial direction of the first rotation center axis R1. Here, the first guide portion 44 is formed in a linear shape, and an end portion on the opposite side to the first rotation center axis R1 side, that is, an end portion on the radially outer side is opened. A plurality (eight here) of first guide portions 44 are provided radially around the first rotation center axis R1 corresponding to the plurality of planetary balls 50 (eight here). The plurality of first guide portions 44 are provided at equal intervals around the first rotation center axis R1. In the first guide portion 44, the first guide end portion 52 of the support shaft 51 is inserted, and the movement of the first guide end portion 52 of the support shaft 51 can be guided. Here, the first guide end portion 52 of the support shaft 51 functions as a guide end portion that is guided by the first guide portion 44 in the radial direction.

  As shown in FIGS. 1, 2, and 4, the second guide portion 45 extends on the movable carrier 42 in a direction inclined with respect to the radial direction orthogonal to the first rotation center axis R <b> 1 and is connected to the planetary ball 50. An opening is formed. The second guide portion 45 is formed as a bottomed guide groove portion, that is, has a configuration that does not penetrate the movable carrier 42 with respect to the axial direction of the first rotation center axis R1. Here, the second guide portion 45 is formed in a linear shape and at a position offset substantially parallel to a straight line along the radial direction passing through the first rotation center axis R1. In addition, the second guide portion 45 is open at the radially outer end. Similarly to the first guide portion 44, a plurality of (here, eight) second guide portions 45 are provided corresponding to a plurality of planetary balls 50 (here, eight). Each second guide portion 45 partially overlaps the corresponding first guide portion 44 when viewed in the axial direction of the first rotation center axis R1 (when viewed in the direction of arrow A in FIG. 1). It is formed at a crossing position. The intersection of the first guide portion 44 and the second guide portion 45 moves along the radial direction by the relative rotation of the fixed carrier 41 and the movable carrier 42 with the first rotation center axis R1 as the rotation center. It will be. The second guide portion 45 can guide the movement of the second guide end portion 53 of the support shaft 51 by inserting the second guide end portion 53 of the support shaft 51. Here, the second guide end portion 53 of the support shaft 51 functions as a guide end portion whose movement is guided by the second guide portion 45. The second guide portion 45 supports the second guide end portion 53 and is positioned at a predetermined radial position by abutting the inner wall surface with the outer peripheral surface of the second guide end portion 53.

  The second guide portion 45 is formed in an arc shape extending in a direction inclined with respect to the radial direction orthogonal to the first rotation center axis R1, and when viewed in the axial direction of the first rotation center axis R1. The first guide portion 44 may be formed at a position that partially overlaps the first guide portion 44.

  As shown in FIGS. 1, 2, and 5, the slit portion 46 extends in the radial direction perpendicular to the first rotation center axis R1 and penetrates the plate 43 in the axial direction of the first rotation center axis R1. It is formed. That is, the slit portion 46 is formed as a slit hole penetrating the plate 43 in the axial direction of the first rotation center axis R1. Here, the slit portion 46 is formed in a straight line, and the end portion on the radially outer side is opened. Similar to the first guide portion 44, the slit portion 46 is provided in a plurality (eight here) in a radial manner around the first rotation center axis R1 corresponding to the plurality of planetary balls 50 (eight here). . The plurality of slit portions 46 are provided at equal intervals around the first rotation center axis R1. Each slit portion 46 opposes the corresponding first guide portion 44 and the axial direction of the first rotation center axis R1 in a state where the fixed carrier 41 and the plate 43 are fixed. Accordingly, each slit portion 46 partially overlaps the corresponding second guide portion 45 when viewed in the axial direction of the first rotation center axis R1 (when viewed in the direction of arrow A in FIG. 1). It is formed at a crossing position. The intersection part of the slit part 46 and the second guide part 45 is the same as the intersection part of the first guide part 44 and the second guide part 45, and the fixed carrier 41 and the movable carrier 42 have the first rotation center axis R1. Is moved along the radial direction by relative rotation about the rotation center. The slit portion 46 is inserted into both end portions of the support shaft 51, that is, the intermediate portion 54 between the first guide end portion 52 and the second guide end portion 53, and moves the intermediate portion 54 of the support shaft 51. Allow.

  The carrier 40 configured as described above holds the support shaft 51 in a state in which the planetary ball 50 can be tilted by the first guide portion 44, the second guide portion 45, and the slit portion 46. Then, the carrier 40 tilts the planetary ball 50 together with the support shaft 51 by the relative displacement of the first guide portion 44 and the second guide portion 45 accompanying the relative rotation of the fixed carrier 41 and the movable carrier 42, and each rotating element. The speed ratio, which is the rotational speed ratio between, can be changed.

  Here, in the continuously variable transmission 1, when the tilt angle of the planetary ball 50 is the reference position, that is, 0 degrees, the first rotating member 10 and the second rotating member 20 have the same rotational speed (the same rotational speed). Rotate with. That is, at this time, the rotation ratio (ratio of rotation speed or rotation speed) between the first rotation member 10 and the second rotation member 20 is 1, and the speed ratio γ is 1. For example, if the rotation speeds of the first rotating member 10 and the second rotating member 20 are “V1” and “V2”, respectively, the rotation ratio is “V1 / V2”. On the other hand, as shown by a one-dot chain line in FIG. 2, when the planetary ball 50 is tilted together with the support shaft 51 from the reference position, the distance from the central axis of the support shaft 51 to the contact portion with the first rotating member 10. Changes, and the distance from the central axis of the support shaft 51 to the contact portion with the second rotating member 20 changes. As a result, the continuously variable transmission 1 rotates at a higher speed than when either the first rotating member 10 or the second rotating member 20 is at the reference position, and the other rotates at a lower speed. For example, 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). Therefore, in this continuously variable transmission 1, the rotation ratio (transmission ratio γ) between the rotating elements can be changed steplessly by changing the tilt angle. At the time of acceleration here (γ <1), the upper planetary ball 50 in FIG. 1 is tilted counterclockwise on the paper surface and the lower planetary ball 50 is tilted clockwise on the paper surface. Further, at the time of deceleration (γ> 1), the upper planetary ball 50 in FIG. 1 is tilted in the clockwise direction on the paper, and the lower planetary ball 50 is tilted in the counterclockwise direction on the paper.

  The continuously variable transmission 1 of the present embodiment functions as a mechanism in which the carrier 40 changes the speed ratio γ. The continuously variable transmission 1 tilts each planetary ball 50 by inclining the second rotation center axis R2 of each planetary ball 50 by the carrier 40, thereby changing the tilt angle of the planetary ball 50 and changing the gear ratio γ. Is changed.

  Here, the carrier 40 tilts the planetary ball 50 together with the support shaft 51 by applying a tilting force to the support shaft 51 according to the relative rotation of the movable carrier 42 and the fixed carrier 41, that is, a tilting force. That is, the carrier 40 is transmitted to the movable carrier 42 via a transmission member such as a worm gear from a driving device such as a motor in accordance with control by an ECU (not shown), so that the movable carrier 42 is fixed to the fixed carrier 41. Rotates relative to. Thereby, the intersection part of the 2nd guide part 45, the 1st guide part 44, and the slit part 46 is because the phase shifts by the relative displacement of the 1st guide part 44, the slit part 46, and the 2nd guide part 45, It moves along the radial direction. At this time, the support shaft 51 is pushed up while the second guide end portion 53 is guided along the second guide portion 45 by the tilting force generated according to the relative rotation of the movable carrier 42 and the fixed carrier 41. The first guide end 52 is moved while being guided along the first guide portion 44. That is, in the support shaft 51, the first guide end 52 moves radially outward and the second guide end 53 moves radially inward, or the second guide end 53 is radially outward and the first guide end. When 52 moves radially inward, the second rotation center axis R2 swings with respect to the first rotation center axis R1.

  Thus, the carrier 40 is in a state where the second rotation center axis R2 of each planetary ball 50 is located in a plane including the first rotation center axis R1 and is parallel to the first rotation center axis R1 in the plane. That is, it can be tilted between the state at the reference position and the state in which it is inclined from the parallel state. As a result, the support shaft 51 moves the second rotation center axis R2 relative to the first rotation center axis R1 according to the deviation between the radial position of the first guide end 52 and the radial position of the second guide end 53. The tilt angle, which is the tilt angle, is changed, and the planetary ball 50 tilts accordingly. In this way, the carrier 40 applies a tilting force to the support shaft 51, and tilts the support shaft 51, thereby tilting the second rotation center axis R2 and tilting the planetary ball 50. Accordingly, in the continuously variable transmission 1, the distance from the central axis of the support shaft 51 to the contact portion between the first rotating member 10 and the planetary ball 50 changes due to the tilt of the planetary ball 50, and the support shaft 51 The distance from the central axis to the contact portion between the planetary ball 50 and the second rotating member 20 changes, and the gear ratio is changed. At this time, the carrier 40 is allowed to swing in the radial direction of the intermediate portion 54 of the support shaft 51 by the slit portion 46 in the plate 43. In the continuously variable transmission 1 of the present embodiment, the second guide end portion 53 is moved to the center side (first rotation center axis R1) when the movable carrier 42 rotates counterclockwise in FIG. The gear ratio is changed to the speed increasing side within a predetermined speed range. In the continuously variable transmission 1, the movable guide 42 rotates in the clockwise direction in FIG. 4 so that the second guide end 53 moves outward (opposite to the first rotation center axis R1). The gear ratio is changed to the deceleration side within a predetermined speed range.

  The continuously variable transmission 1 configured as described above, for example, when torque is transmitted to the input shaft 11, the torque is transmitted to the torque cam 70, the first rotating member 10, the planetary ball 50, the second rotating member 20, and the torque cam. It can be transmitted to the output shaft 21 via 71 or the like. At this time, for example, when the torque is transmitted from the input shaft 11 to the first rotating member 10, the continuously variable transmission 1 changes the first torque according to the magnitude of the torque transmitted by the action of the torque cam 70, the torque cam 71, and the like. A pressing force (pressing load) is generated in a direction in which the first rotating member 10 and each planetary ball 50 and the second rotating member 20 and each planetary ball 50 are relatively approached and pressed against each other. As a result, the continuously variable transmission 1 has a transmission torque capacity corresponding to the pressing force, and between the first rotating member 10 and each planetary ball 50 according to this transmission torque capacity, each planetary ball 50 and the second planetary ball 50. A traction force (friction force) is generated between the rotating member 20 and the rotating member 20. As a result, the continuously variable transmission 1 can transmit power (torque) between the first rotating member 10 and each planetary ball 50 and between each planetary ball 50 and the second rotating member 20. .

  Further, the pressing force by the torque cam 70 and the torque cam 71 is caused by the action according to the shape and positional relationship between the contact surfaces 10a and 20a of the first rotating member 10 and the second rotating member 20 and the outer surface of each planetary ball 50. It is also transmitted to the sun roller 30 via the ball 50. Thereby, the continuously variable transmission 1 generates a traction force (friction force) between each planetary ball 50 and the sun roller 30 according to the pressing force by the torque cam 70 and the torque cam 71, and each planetary ball 50 and the sun roller 30. Can transmit power (torque) to each other.

  Therefore, the continuously variable transmission 1 generates a frictional force (traction force) between the first rotating member 10 and each planetary ball 50 as the first rotating member 10 rotates, and each planetary ball 50 starts to rotate. . The continuously variable transmission 1 generates a frictional force between each planetary ball 50 and the second rotating member 20 and between each planetary ball 50 and the sun roller 30 due to the rotation of each planetary ball 50. The two-rotating member 20 and the sun roller 30 also start to rotate. Similarly, in the continuously variable transmission 1, each planetary ball 50 starts rotating as the second rotating member 20 rotates, and the first rotating member 10 and the sun roller 30 also start rotating. In the continuously variable transmission 1, the carrier 40 tilts each planetary ball 50 and changes the tilt angle of each planetary ball 50 as described above by the power from the driving device, thereby changing the gear ratio γ continuously. Can be changed.

  In the continuously variable transmission 1 of the present embodiment, oil as a lubricating medium (may also be used as traction oil) is supplied to the sliding portions of the respective portions. For example, as shown in FIG. 2, the continuously variable transmission 1 uses a shaft axial oil passage for the oil discharged by the oil pump 80 to the axial center (center) of the planetary ball 50 as a sliding portion. 81, shaft radial oil passage 82, shaft annular oil passage 83, movable carrier radial oil passage 84, second guide portion 45, support shaft oil passage 85, etc. doing.

  Here, the shaft portion axial oil passage 81, the shaft portion radial oil passage 82, and the shaft portion annular oil passage 83 are oil supply passages formed in the transmission shaft 60. The shaft portion axial oil passage 81 is formed in the transmission shaft 60 along the axial direction, one end portion is opened, and the other end portion is connected to the discharge port side of the oil pump 80. The shaft portion radial oil passage 82 is formed along the radial direction inside the transmission shaft 60, the radially inner end portion communicates with the shaft portion axial oil passage 81, and the radially outer end portion is the shaft portion annular oil. It communicates with the road 83. The shaft-shaped annular oil passage 83 is formed in an annular shape on the outer peripheral surface of the transmission shaft 60 and opens toward the radially outer side. The movable carrier radial oil passage 84 is formed in the movable carrier 42 along the radial direction, and the radially inner end opens to a position facing the axial annular oil passage 83, and the radially outer end is the first. 2 Open in the radially outer portion of the guide portion 45. The support axial oil passage 85 is a supply passage for supplying the oil supplied into the second guide portion 45 to the planetary ball 50. The support axial oil passage 85 is formed in the support shaft 51 along the axial direction, the end on the second guide end portion 53 side opens into the second guide portion 45, and the other end is the planetary ball 50. Open in the vicinity of the axial center part (center part).

  Therefore, the oil discharged from the oil pump 80 is contained in the second guide portion 45 via the shaft portion axial oil passage 81, the shaft portion radial oil passage 82, the shaft portion annular oil passage 83, and the movable carrier radial oil passage 84. Dripped and supplied. Then, the oil supplied into the second guide portion 45 is supplied from the second guide end portion 53 side of the support shaft 51 to the axial center portion of the planetary ball 50 via the support shaft direction oil passage 85, and this planetary ball. The sliding portions such as the shaft center portion 50, the support shaft 51, and the radial bearings RB3 and RB4 are lubricated.

  By the way, the continuously variable transmission 1 of the present embodiment is moved along with the planetary ball 50, that is, when the gear ratio is changed, the moving distance of the first guide end 52 (hereinafter referred to as “first guide end 52”). The travel distance of the second guide end portion 53 (hereinafter, sometimes referred to as “travel amount of the second guide end portion 53”) is different. That is, the support shaft 51 has a relatively large one travel amount of the travel amount of the first guide end portion 52 and the travel amount of the second guide end portion 53 during the tilting operation, and the other travel amount is small. It is constructed relatively small. The travel amounts of the first guide end 52 and the second guide end 53 during the tilting operation are the first guide end 52 and the second guide end 53 during the tilting operation of the planetary ball 50 and the support shaft 51, respectively. Corresponds to the rolling distance when moving while being guided along the first guide portion 44 and the second guide portion 45.

  In the continuously variable transmission 1, for example, the planetary ball 50 and the fixed carrier 41 are disposed adjacent to each other with respect to the axial direction of the first rotation center axis R <b> 1, while the planetary ball 50 and the movable carrier 42 are disposed between them. The plate 43 is interposed. Therefore, as shown in FIG. 2, the continuously variable transmission 1 has a distance between a contact point between the first guide end 52 and the guide surface (wall surface) of the first guide 44 and the rolling center of the planetary ball 50. The distance L2 between L1 and the contact point between the second guide end portion 53 and the guide surface (wall surface) of the second guide portion 45 and the rolling center of the planetary ball 50 is different. As a result, the continuously variable transmission 1 has different trajectory lengths of the first guide end 52 and the second guide end 53 during the tilting operation, that is, the travel amount is different. Here, the continuously variable transmission 1 is configured such that the distance L1 is relatively small and the distance L2 is relatively large due to the positional relationship between the fixed carrier 41, the movable carrier 42, and the plate 43. As a result, the continuously variable transmission 1 is configured such that the travel amount of the first guide end 52 during the tilting operation is relatively small and the travel amount of the second guide end 53 is relatively large. .

  In the continuously variable transmission 1 of the present embodiment, as shown in FIG. 2, the outer diameter d1 of the first guide end 52 and the outer diameter d2 of the second guide end 53 have a predetermined magnitude relationship. As a result, a smooth shifting operation is realized.

  Specifically, the first guide end portion 52 and the second guide end portion 53 have a relatively large outer diameter during the tilting operation and a relatively large travel amount during the tilting operation. It is relatively larger than the outer diameter of the smaller one. Here, as described above, the continuously variable transmission 1 has a relatively small travel amount of the first guide end portion 52 during the tilting operation (see, for example, the travel amount T1 illustrated in FIG. 4). 2 The travel amount of the guide end 53 (see, for example, the travel amount T2 illustrated in FIG. 4) is configured to be relatively large. Therefore, the continuously variable transmission 1 is configured such that the outer diameter d2 of the second guide end portion 53 is relatively larger and the outer diameter d1 of the first guide end portion 52 is relatively smaller.

  More specifically, the continuously variable transmission 1 is configured such that the ratio of the outer diameter d1 of the first guide end 52 and the outer diameter d2 of the second guide end 53 is the travel of the first guide end 52 during the tilting operation. It is configured to be equivalent to the ratio of the amount and the travel amount of the second guide end portion 53. Here, as described above, the travel amount of the first guide end 52 during the tilting operation is defined based on the distance L1, and the travel amount of the second guide end 53 during the tilting operation is It is defined based on the distance L2. Therefore, the ratio between the outer diameter d1 of the first guide end 52 and the outer diameter d2 of the second guide end 53 is equal to the ratio between the distance L1 and the distance L2.

  For example, the continuously variable transmission 1 has a configuration in which the travel amount of the first guide end portion 52 and the travel amount of the second guide end portion 53 during the tilting operation are different as described above. When the outer diameter d1 of 52 and the outer diameter d2 of the second guide end portion 53 are configured to be equal, smooth shifting operation may be hindered. In this case, the continuously variable transmission 1 is caused by a difference in travel amount even when one end portion rolls smoothly when the support shaft 51 tilts together with the planetary ball 50. Therefore, a large frictional force may be generated at the other end. Further, in this case, the continuously variable transmission 1 uses, for example, traction oil, so that high torque is applied to the support shaft 51, so that the traction oil is solidified, and the first guide end 52 and the second guide end 53. Torque (shift torque) required for the tilting operation may increase between the first guide portion 44 and the second guide portion 45.

  On the other hand, in the continuously variable transmission 1 configured as described above, the outer diameter d2 of the second guide end portion 53 having a relatively large amount of travel during the tilting operation has a travel amount during the tilting operation. Is relatively larger than the outer diameter d1 of the first guide end 52. Therefore, the continuously variable transmission 1 has a support shaft in accordance with an operation in which both ends of the first guide end portion 52 and the second guide end portion 53 are guided by rolling in the first guide portion 44 and the second guide portion 45. When 51 inclines with the planetary ball 50, it can suppress that a big frictional force arises in the said both ends resulting from the difference in travel amount. For example, the continuously variable transmission 1 slips at a contact portion between the first guide end portion 52, the second guide end portion 53, the first guide portion 44, and the guide surfaces of the second guide portion 45 accompanying the tilting operation. Friction can be wiped off, and wear due to this sliding friction can be suppressed. Here, in the continuously variable transmission 1, the ratio of the outer diameter d1 of the first guide end 52 and the outer diameter d2 of the second guide end 53 is the travel amount of the first guide end 52 during the tilting operation. The second guide end portion 53 is configured to be equivalent to the travel amount (or the ratio between the distance L1 and the distance L2). Therefore, the continuously variable transmission 1 can reliably suppress friction at both ends of the first guide end 52 and the second guide end 53, and can minimize shift torque due to friction. Thereby, the continuously variable transmission 1 can implement a smooth shifting operation. Accordingly, the continuously variable transmission 1 has a torque (shift torque) required for the tilting operation between the first guide end portion 52 and the second guide end portion 53 and the first guide portion 44 and the second guide portion 45. Can be suppressed, and controllability can be improved.

  Here, the continuously variable transmission 1 of the present embodiment has at least one of the first guide end portion 52 and the second guide end portion 53 and the intermediate portion 54 (the main body portion of the support shaft 51) as a divided structure. It is preferable. That is, at least one of the first guide end portion 52 and the second guide end portion 53 is preferably configured separately from the intermediate portion 54 of the support shaft 51 and assembled to the intermediate portion 54.

  As shown in FIGS. 1, 2, and 6, the support shaft 51 of the present embodiment has a second guide end portion 53 formed integrally with the intermediate portion 54, and a first guide end portion 52 defined as the intermediate portion 54. It is formed separately. The support shaft 51 is formed in a cylindrical shape as a whole including the first guide end portion 52, the second guide end portion 53, and the intermediate portion 54. The support shaft 51 is configured such that the outer diameter d1 of the first guide end portion 52, the outer diameter d2 of the second guide end portion 53, and the outer diameter d3 of the intermediate portion 54 satisfy [d3 <d1 <d2].

  The second guide end portion 53 is integrally formed with the intermediate portion 54. On the other hand, the first guide end 52 is configured to include a roller 52 a that is separate from the intermediate portion 54, and the roller 52 a is assembled to the intermediate portion 54 so as to be rotatable relative to the intermediate portion 54. Consists of. The roller 52a is assembled by the snap ring 52b or the like so as not to drop off from the intermediate portion 54.

  In the continuously variable transmission 1, the first guide end portion 52 is configured separately from the intermediate portion 54, and is assembled to the intermediate portion 54, so that the radial bearing RB 3, between the planetary ball 50 and the support shaft 51, When providing RB4 etc., the assembly | attachment property of the said radial bearing RB3, RB4 can be improved. The continuously variable transmission 1 is assembled such that at least one of the first guide end portion 52 and the second guide end portion 53, here, the first guide end portion 52 is rotatable relative to the intermediate portion 54. It includes a roller 52a. Thereby, the continuously variable transmission 1 can further reliably suppress the occurrence of friction during the tilting operation at either the first guide end portion 52 or the second guide end portion 53.

  The continuously variable transmission 1 according to the embodiment described above includes the transmission shaft 60, the first rotating member 10 and the second rotating member 20, the planetary ball 50, the support shaft 51, and the carrier 40. . The transmission shaft 60 is the center of rotation. The first rotating member 10 and the second rotating member 20 are disposed so as to face the transmission shaft 60 in the axial direction, and can be relatively rotated about the common first rotation center axis R1. The planetary ball 50 is rotatable about a second rotation center axis R2 different from the first rotation center axis R1. The planetary ball 50 is sandwiched between the first rotating member 10 and the second rotating member 20 and can transmit torque between the first rotating member 10 and the second rotating member 20. The support shaft 51 supports the planetary ball 50 with the second rotation center axis R <b> 2 as the rotation center, and the first guide end portions 52 and 53 protrude from the planetary ball 50. The carrier 40 is disposed on the transmission shaft 60 so as to be rotatable relative to the first rotating member 10 and the second rotating member 20 around the first rotation center axis R1. The carrier 40 has a fixed carrier 41 and a movable carrier 42 and holds the support shaft 51. The fixed carrier 41 is provided on the first guide end portion 52 side of the support shaft 51 so as not to rotate relative to the transmission shaft 60. The movable carrier 42 is arranged on the second guide end 53 side of the support shaft 51 so as to face the fixed carrier 41 and is provided so as to be rotatable relative to the transmission shaft 60. The carrier 40 holds the support shaft 51 in a state where the planetary ball 50 can be tilted by the first guide portion 44 and the second guide portion 45. The first guide portion 44 is formed in the fixed carrier 41 so as to extend in a direction orthogonal to the first rotation center axis R <b> 1 and open toward the planetary ball 50. The first guide portion 44 can guide the movement of the first guide end portion 52 by inserting the first guide end portion 52 of the support shaft 51. The second guide portion 45 is formed in the movable carrier 42 so as to extend in a direction inclined with respect to a direction orthogonal to the first rotation center axis R <b> 1 and to open toward the planetary ball 50. The second guide portion 45 can guide the movement of the second guide end portion 53 by inserting the second guide end portion 53 of the support shaft 51. The carrier 40 tilts the planetary ball 50 together with the support shaft 51 by the relative displacement of the first guide portion 44 and the second guide portion 45 accompanying the relative rotation of the fixed carrier 41 and the movable carrier 42, so that the rotation between the rotating elements The speed ratio that is the rotation speed ratio can be changed. The support shaft 51 moves in one of the movement distance (travel amount) of the first guide end portion 52 and the movement distance (travel amount) of the second guide end portion 53 when tilting together with the planetary ball 50. The distance is relatively large and the other moving distance is relatively small. The first guide end portion 52 and the second guide end portion 53 have a relatively large outer diameter (here, the outer diameter d2 of the second guide end portion 53), and the moving distance is relatively small. It is relatively larger than the outer diameter (here, the outer diameter d1 of the first guide end 52).

  Therefore, the continuously variable transmission 1 is configured such that the outer diameter d2 of the second guide end 53 having a relatively large travel amount during the tilting operation is relatively larger than the outer diameter d1 of the first guide end 52. Thus, when the support shaft 51 tilts together with the planetary ball 50, it is possible to suppress the generation of a large frictional force at the first guide end portion 52 and the second guide end portion 53. As a result, the continuously variable transmission 1 can realize a smooth speed change operation.

[Embodiment 2]
FIG. 7 is a partial cross-sectional view of a continuously variable transmission according to the second embodiment, and FIGS. 8, 9, and 10 are configuration diagrams illustrating a configuration of a support shaft of a continuously variable transmission according to a modification. The continuously variable transmission according to the second embodiment is different from the first embodiment in the configuration of the support shaft. In addition, about the structure, operation | movement, and effect which are common in embodiment mentioned above, the overlapping description is abbreviate | omitted as much as possible.

  The continuously variable transmission 1 described with reference to FIG. 1 has a configuration in which the planetary ball 50 and the support shaft 51 can be rotated relative to each other by radial bearings RB3 and RB4 disposed between the outer peripheral surface of the support shaft 51 and the planetary ball 50. It was described as being present (see FIG. 1).

  In contrast, the continuously variable transmission 201 of the present embodiment shown in FIG. 7 is provided with a support shaft 251 that can rotate integrally with the planetary ball 50. That is, the planetary ball 50 and the support shaft 251 are fixed so as not to rotate relative to the circumferential direction of the second rotation axis R1, in other words, relative to the rotation direction. The support shaft 251 includes a bolt 251a that forms the intermediate portion 54, and a nut 251b that is fastened to the bolt 251a. In the support shaft 251, a bolt 251 a is inserted from one end of a through hole formed in the planetary ball 50, and a nut 251 b is fastened to the bolt 251 a on the other end side. The support shaft 251 is provided so as not to rotate relative to the planetary ball 50 by the fastening force between the bolt 251a and the nut 251b, in other words, to be able to rotate integrally.

  The first guide end portion 52 includes a needle bearing RB23 serving as a first bearing interposed between the first guide portion 44 and the second guide end portion 53 is connected to the second guide portion 45. It includes a needle bearing RB24 as a second bearing interposed therebetween. In other words, the support shaft 251 is supported such that the first guide end portion 52 is rotatably supported by the first guide portion 44 by the needle bearing RB23, and the second guide end portion 53 is rotated by the needle bearing RB24 to the second guide portion 45. Supported as possible.

  Here, in the first guide portion 44, the first guide end portion 52 is inserted together with the needle bearing RB23, and the movement of the first guide end portion 52 can be guided together with the needle bearing RB23. The second guide portion 45 is inserted with the second guide end portion 53 together with the needle bearing RB24, and can guide the movement of the second guide end portion 53 together with the needle bearing RB24. Here, the outer diameter d1 of the first guide end portion 52 corresponds to the outer diameter of the outer ring of the needle bearing RB23. The outer diameter d2 of the second guide end portion 53 corresponds to the outer diameter of the outer ring of the needle bearing RB24.

  The planetary ball 50 and the support shaft 251 configured as described above are provided with the needle bearing RB23 and the needle bearing RB24 of the first guide end 52 and the second guide end 53 with respect to the fixed carrier 41 and the movable carrier 42, respectively. Supported through. Therefore, the planetary ball 50 and the support shaft 251 can rotate integrally with the second rotation center axis R2 as a rotation center and can be tilted integrally.

  Here, the continuously variable transmission 201 includes a shaft portion radial oil passage 286, a fixed carrier diameter, instead of the support shaft oil passage 85 as a supply passage for supplying oil to the sliding portions of the respective portions. A directional oil passage 287 is included. The shaft portion radial oil passage 286 is formed along the radial direction inside the transmission shaft 60, the radially inner end portion communicates with the shaft portion axial oil passage 81, and the radially outer end portion is radially outward. Open toward. The fixed carrier radial oil passage 287 is formed along the radial direction inside the fixed carrier 41, and the radially inner end opens at a position facing the opening of the shaft radial oil passage 286. The part opens to a part on the radially outer side of the first guide part 44 and the like.

  Therefore, the oil discharged from the oil pump 80 is dropped and supplied into the first guide portion 44 through the shaft portion axial oil passage 81, the shaft portion radial oil passage 286, and the fixed carrier radial oil passage 287. Accordingly, the oil supplied into the first guide portion 44 is supplied to the needle bearing RB23 at the first guide end portion 52 of the support shaft 251 and lubricates the sliding portion such as the needle bearing RB23. Further, a part of the oil discharged from the oil pump 80 is branched to the axial radial oil path 82 side by the axial axial oil path 81, and the axial annular oil path 83 and the movable carrier radial oil path 84 are separated. And supplied into the second guide portion 45 via the second guide portion 45. Thereby, the oil supplied into the second guide portion 45 is supplied to the needle bearing RB24 at the second guide end portion 53 of the support shaft 251 and lubricates the sliding portion such as the needle bearing RB24.

  As a result, the continuously variable transmission 201 is configured such that the sliding portions such as the needle bearing RB23 and the needle bearing RB24 that support the planetary ball 50 so as to be rotatable (spinned) are disposed at the end of the support shaft 251. Oil can be reliably supplied to the needle bearing RB23 and the needle bearing RB24 regardless of the inclination degree of 251, in other words, the inclination angle or the like. Therefore, the continuously variable transmission 201 can reliably lubricate the needle bearing RB23 and the needle bearing RB24.

  In the continuously variable transmission 201 according to the embodiment described above, the outer diameter d2 of the second guide end portion 53 having a relatively large travel amount during the tilting operation is relatively larger than the outer diameter d1 of the first guide end portion 52. When the support shaft 251 is tilted together with the planetary ball 50, it is possible to suppress a large frictional force from being generated at the first guide end portion 52 and the second guide end portion 53. As a result, the continuously variable transmission 201 can achieve a smooth speed change operation.

  Furthermore, according to the continuously variable transmission 201 according to the embodiment described above, the support shaft 251 is provided so as to be able to rotate integrally with the planetary ball 50, and the first guide end portion 52 is connected to the first guide portion 44. The second guide end portion 53 includes a needle bearing RB24 interposed between the second guide portion 45 and the needle bearing RB23 interposed therebetween. Therefore, the continuously variable transmission 201 supplies the lubricating medium to the sliding portion by disposing the needle bearing RB23 and the needle bearing RB24 that support the planetary ball 50 so as to be rotatable (spinning) at the end of the support shaft 251. An easy structure can be obtained, and the needle bearing RB23 and the needle bearing RB24 can be reliably lubricated. As a result, the continuously variable transmission 201 can prevent seizure and deterioration of durability due to poor lubrication.

  The structure for fixing the planetary ball 50 and the support shaft 251 in the rotational direction is not limited to the type using the bolts 251a and nuts 251b. For example, the types as shown in FIGS. It may be.

  The support shaft 251 shown in FIG. 8 includes a spline engaging portion 251c instead of the bolt 251a and the nut 251b as a structure for fixing the planetary ball 50 and the support shaft 251 in the rotational direction. The spline engaging portion 251 c is interposed between the outer peripheral surface of the intermediate portion 54 of the support shaft 251 and the inner peripheral surface of the through hole of the planetary ball 50. The spline engaging portion 251c connects the intermediate portion 54 of the support shaft 251 and the planetary ball 50 so as to be capable of rotating integrally and relatively movable in a direction along the second rotation center axis R2. Accordingly, the support shaft 251 is provided so as not to rotate relative to the planetary ball 50 by the spline engaging portion 251c, in other words, to be able to rotate integrally.

  The support shaft 251 shown in FIG. 9 includes circumferential welds 251d and 251e as a structure for fixing the planetary ball 50 and the support shaft 251 in the rotational direction, instead of the bolts 251a and nuts 251b. The circumferential welds 251d and 251e fix the intermediate part 54 of the support shaft 251 and the planetary ball 50 by welding in the vicinity of the first guide end 52 and the second guide end 53 of the support shaft 251. Thereby, the support shaft 251 is fixed so as not to rotate relative to the planetary ball 50 by the circumferential welded portions 251d and 251e, in other words, to be able to rotate integrally.

  The support shaft 251 shown in FIG. 10 has a structure in which the planetary ball 50 and the support shaft 251 are integrally formed in place of the bolt 251a and the nut 251b as a structure for fixing the planetary ball 50 and the support shaft 251 in the rotation direction. It has become. The support shaft 251 has a portion corresponding to the intermediate portion 54 formed integrally with the planetary ball 50, and projections 251 f and 251 g corresponding to the first guide end portion 52 and the second guide end portion 53 of the planetary ball 50. Provided on the outer peripheral surface. Thus, the support shaft 251 is fixed so as not to rotate relative to the planetary ball 50, in other words, so as to be able to rotate integrally.

  The continuously variable transmission according to the above-described embodiment of the present invention is not limited to the above-described embodiment, and various modifications can be made within the scope described in the claims.

1,201 continuously variable transmission 10 first rotating member (first rotating element)
20 Second rotating member (second rotating element)
30 Sun Roller 40 Carrier (Support Rotating Element)
41 Fixed carrier (fixed element)
42 Movable carrier (movable element)
43 Plate 44 1st guide part 45 2nd guide part 46 Slit part 50 Planetary ball (rolling member)
51, 251 Support shaft 52 First guide end portion 52a Roller 53 Second guide end portion 54 Intermediate portion 60 Transmission shaft 80 Oil pump R1 First rotation center axis R2 Second rotation center axis RB23 Needle bearing (first bearing)
RB24 needle bearing (second bearing)

Claims (7)

A transmission shaft as a center of rotation;
A first rotation element and a second rotation element that are arranged opposite to the transmission shaft in the axial direction and are capable of relative rotation about a common first rotation center axis;
The second rotation center axis that is different from the first rotation center axis is rotatable about the rotation center, and is sandwiched between the first rotation element and the second rotation element, and the first rotation element and the second rotation element A rolling member capable of transmitting torque between,
A support shaft that supports the rolling member with the second rotation center axis as the center of rotation, and both ends project from the rolling member;
The first rotation element is disposed on the transmission shaft so as to be rotatable relative to the first rotation element and the second rotation element with the first rotation center axis as a rotation center, and relative to the transmission shaft on one end side of the support shaft. A fixed element provided in a non-rotatable manner, and a movable element provided opposite to the fixed element on the other end side of the support shaft and provided to be rotatable relative to the transmission shaft, and holds the support shaft A support rotation element,
The support rotation element is formed in the fixed element in a direction orthogonal to the first rotation center axis and is open toward the rolling member, and is a first guide that is one end of the support shaft. A first guide portion into which the end portion is inserted and capable of guiding the movement of the first guide end portion; the movable element extending in a direction inclined with respect to a direction orthogonal to the first rotation center axis; and A second guide portion that is formed to open toward the rolling member and that can be inserted into the second guide end portion, which is the other end portion of the support shaft, to guide the movement of the second guide end portion. The support shaft is held in a state in which the rolling member can be tilted, and by the relative displacement of the first guide portion and the second guide portion accompanying relative rotation of the fixed element and the movable element. The rolling member is tilted together with the support shaft to rotate each time. Can vary the gear ratio is the rotational speed ratio between the elements,
The support shaft has a relatively large moving distance of one of a moving distance of the first guide end and a moving distance of the second guide end when tilting together with the rolling member, The travel distance is relatively small,
The first guide end portion and the second guide end portion are configured such that an outer diameter having a relatively large moving distance is relatively larger than an outer diameter having a relatively small moving distance. Features
Continuously variable transmission. The ratio of the outer diameter of the first guide end to the outer diameter of the second guide end is determined by the distance traveled by the first guide end when the support shaft is tilted together with the rolling member and the first guide end. It is equivalent to the ratio with the movement distance of the two guide ends.
The continuously variable transmission according to claim 1. The moving distance of the first guide end when the support shaft tilts together with the rolling member is the contact point between the first guide end and the first guide, and the rolling center of the rolling member. And based on the distance
The moving distance of the second guide end when the support shaft tilts together with the rolling member is the contact point between the second guide end and the second guide, and the rolling center of the rolling member. Stipulated based on the distance to
The continuously variable transmission according to claim 1 or 2. The ratio of the outer diameter of the first guide end portion to the outer diameter of the second guide end portion is the contact between the first guide end portion and the first guide portion and the rolling center of the rolling member. The distance is equal to the ratio of the distance between the contact point between the second guide end and the second guide part and the rolling center of the rolling member,
The continuously variable transmission according to any one of claims 1 to 3. At least one of the first guide end and the second guide end is configured separately from an intermediate portion between the first guide end and the second guide end of the support shaft. Assembled in the middle part,
The continuously variable transmission according to any one of claims 1 to 4. At least one of the first guide end and the second guide end is rotatable relative to an intermediate portion of the support shaft between the first guide end and the second guide end. Composed of assembled rollers,
The continuously variable transmission according to any one of claims 1 to 5. The support shaft is provided so as to be integrally rotatable with the rolling member,
The first guide end portion includes a first bearing interposed between the first guide portion,
The second guide end portion includes a second bearing interposed between the second guide portion and the second guide portion.
The continuously variable transmission according to any one of claims 1 to 6.

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