JP2014077468A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission capable of securing proper lubrication performance.SOLUTION: A continuously variable transmission 1 includes: a transmission shaft 60; a first rotary element 10; a second rotary element 20; a rolling member 50; a support shaft 51; a support rotary element 40; and a movable element supply path 82. The movable element supply path 82 extends in a direction intersecting with a first rotation center axis R1 in a movable element 42 of the support rotary element 40, and can supply a lubrication medium supplied in the transmission shaft 60 to a side of the rolling member 50 according to a transmission gear ratio between each of the rotary elements. Accordingly, the continuously variable transmission 1 can secure proper lubrication performance.

Description

  The present invention relates to a continuously variable transmission.

  As a conventional transmission of a so-called traction drive system, for example, in Patent Document 1, a planetary shaft of a spherical planet (planetary ball) supported by a pivot arm is tilted to perform a shift between a plurality of rotating elements. A transmission is disclosed. This transmission supplies lubricating oil from the main shaft to the planetary pivot arm to lubricate the planet.

Special table 2010-519467

  By the way, the continuously variable transmission described in Patent Document 1 as described above has room for further improvement in terms of more appropriate lubrication according to various configurations, for example.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a continuously variable transmission that can ensure appropriate lubrication performance.

In order to achieve the above object, a continuously variable transmission according to the present invention includes a transmission shaft serving as a rotation center,
A first rotation element and a second rotation element, which are disposed to face the transmission shaft in the axial direction and are relatively rotatable with a common first rotation center axis as a rotation center, are different from the first rotation center axis. Rolling that can rotate about a center axis of two rotations and that is sandwiched between the first and second rotating elements and that can transmit torque between the first and second rotating elements. A member, a support shaft that supports the rolling member with the second rotation center axis as a center of rotation and both ends project from the rolling member, and the first rotation element with the first rotation center axis as a center of rotation, And a fixed element that is disposed on the transmission shaft so as to be rotatable relative to the second rotating element and is provided on one end of the support shaft so as not to rotate relative to the transmission shaft, and the other end of the support shaft On the opposite side of the fixing element And a movable element provided to be rotatable relative to the transmission shaft, and holding both ends of the support shaft in a state in which the rolling member can be tilted by the fixed element and the movable element, A support rotation element capable of changing a transmission gear ratio, which is a rotation speed ratio between the rotation elements, by tilting the rolling member together with the support shaft by relative rotation between the fixed element and the movable element; and The lubrication medium provided in the direction intersecting the first rotation center axis and supplied to the transmission shaft can be supplied to the rolling member side according to the gear ratio between the rotary elements. And a movable element supply path.

  In the continuously variable transmission, the movable element supply path may be configured such that the lubricating medium is transferred from the transmission shaft side to the rolling member when the transmission ratio between the rotating elements is a predetermined transmission ratio on the acceleration side. It can have a 1st supply path supplied to the side.

  In the continuously variable transmission, the movable element supply path may be configured such that the lubricating medium is transferred from the transmission shaft side to the rolling member side when the transmission ratio between the rotating elements is a predetermined reduction gear ratio. It is possible to have a second supply path for supplying to the battery.

  Further, the continuously variable transmission includes a transmission shaft supply path that is provided in the transmission shaft and is supplied with the lubricating medium, and the movable element supply path is associated with relative rotation between the movable element and the fixed element. The communication state with the transmission shaft supply path can be switched according to the relative rotation between the movable element and the transmission shaft.

  Further, in the continuously variable transmission, the support shaft is provided along the second rotation center axis, and the lubricating medium supplied to the rolling member side via the movable element supply path is used as the fixed element. A support shaft supply path for supplying to the side may be provided.

  In the continuously variable transmission, the rolling member is capable of transmitting torque input to the first rotating element to the second rotating element, and the movable element supply path is between the rotating elements. When the gear ratio is a predetermined gear ratio on the speed increasing side, the supply amount of the lubricating medium to the contact point side between the first rotating element and the rolling member is set to the second rotating element and the rolling member. The contact point between the second rotating element and the rolling member is greater than the supply amount of the lubricating medium to the contact point side, and the gear ratio between the rotating elements is a predetermined gear ratio on the deceleration side. The supply amount of the lubricating medium to the side can be made larger than the supply amount of the lubricating medium to the contact point side of the first rotating element and the rolling member.

  In the continuously variable transmission, the predetermined gear ratio on the speed increasing side is a minimum gear ratio that can be realized, and the predetermined gear ratio on the deceleration side is a maximum gear ratio that can be realized. be able to.

  The continuously variable transmission according to the present invention has an effect of ensuring appropriate lubrication performance.

FIG. 1 is a schematic cross-sectional view of a continuously variable transmission according to an embodiment. FIG. 2 is a partial cross-sectional view of the continuously variable transmission according to the embodiment. FIG. 3 is a plan view illustrating a fixed carrier of the continuously variable transmission according to the embodiment. FIG. 4 is a plan view illustrating the movable carrier of the continuously variable transmission according to the embodiment. FIG. 5 is a plan view illustrating the cover plate of the continuously variable transmission according to the embodiment. FIG. 6 is a diagram for explaining the dependency of the spin loss on the gear ratio in the continuously variable transmission according to the embodiment. FIG. 7 is a schematic cross-sectional view of the transmission shaft in the continuously variable transmission according to the embodiment. FIG. 8 is a partial cross-sectional view for explaining the operation of the continuously variable transmission according to the embodiment. FIG. 9 is a partial cross-sectional view for explaining the operation of the continuously variable transmission according to the embodiment.

  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 is a schematic cross-sectional view of a continuously variable transmission according to an embodiment, FIG. 2 is a partial cross-sectional view of the continuously variable transmission according to the embodiment, and FIG. 3 is a stationary carrier of the continuously variable transmission according to the embodiment. FIG. 4 is a plan view for explaining the movable carrier of the continuously variable transmission according to the embodiment, FIG. 5 is a plan view for explaining the cover plate of the continuously variable transmission according to the embodiment, and FIG. FIG. 7 is a diagram for explaining the dependency of the spin loss on the transmission ratio in the continuously variable transmission according to the embodiment, FIG. 7 is a schematic sectional view of the transmission shaft in the continuously variable transmission according to the embodiment, and FIGS. It is a fragmentary sectional view explaining operation of a continuously variable transmission concerning an embodiment.

  The continuously variable transmission according to 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). This continuously variable transmission is, for example, a CVP having a mechanism for tilting (tilting) the rotation axis of a ball by rotating a part of a carrier by an actuator or the like.

  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. A first rotating member 10 as a first rotating element capable of relative rotation, a second rotating member 20 as a second rotating element, a sun roller 30 as a third rotating element, and a fourth rotating element as a supporting rotating element Carrier 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 ring-shaped annular 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 flange 11 is connected to the first rotating member 10 via a torque cam 70. In the continuously variable transmission 1, the output flange 21 is connected to the second rotating member 20 via a torque cam 71. The input flange 11 and the output flange 21 are provided so as to be rotatable relative to the transmission shaft 60 about the first rotation center axis R1.

  The input flange 11 can rotate integrally with the first rotating member 10 via the torque cam 70, and transmits power to the first rotating member 10 during normal driving. The input flange 11 includes a cylindrical part 11a, a disk part 11b, and the like. The input flange 11 is connected to the first rotating member 10 via the torque cam 70 on the disk part 11b side, and connected to the power source side of the vehicle on the cylindrical part 11a side. 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. The central axis thereof is the first rotation central axis R1. Match. In this example, 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. Here, the rotary shaft 12 is an input rotary shaft concentrically disposed at one end of the transmission shaft 60, and is arranged in the circumferential direction with respect to the transmission shaft 60 via a bearing (for example, a roller bearing or a needle bearing) B1. Relative rotation can be performed. Therefore, the input flange 11 performs relative rotation in the circumferential direction with respect to the transmission shaft 60 via the rotary shaft 12 to which the cylindrical portion 11a is fixed and the bearing B1. The disc portion 11b is a disc-like one extending from one end of the cylindrical portion 11a toward the outside in the radial direction, and its central axis coincides with the first rotation center 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 disk portion 11b is adjacent to and faces the fixed carrier 41 described later with respect to the axial direction of the first rotation center axis R1. The disk part 11b is disposed between the fixed carrier 41 described later and the disk part 21b of the output flange 21 with respect to the axial direction of the first rotation center axis R1.

  The output flange 21 can rotate integrally with the second rotating member 20 via the torque cam 71, and power is transmitted from the second rotating member 20 during normal driving. The output flange 21 includes a first cylindrical part 21a, a disk part 21b, a second cylindrical part 21c, and the like. The output flange 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 connected to the drive wheel side of the vehicle on the second cylindrical portion 21c side. The 1st cylindrical part 21a is a cylindrical thing which covers the 1st rotation member 10 and the 2nd rotation member 20 from a radial direction outer side, and makes the center axis correspond to 1st rotation center axis line R1. Further, the first cylindrical portion 21a extends in the axial direction so as to cover the torque cam 70, the torque cam 71 and the disk portion 11b of the input flange 11 from the radially outer side. The disc portion 21b is a disc-like one extending radially inward from the extending end portion of the first cylindrical portion 21a toward the outer peripheral surface of the cylindrical portion 11a of the input flange 11, and its central axis Is made to coincide with the first rotation center axis R1. The disk portion 21b is disposed adjacent to and opposed to the disk portion 11b of the input flange 11 with respect to the axial direction of the first rotation center axis R1. The second cylindrical portion 21c is a cylindrical one that covers the cylindrical portion 11a of the input flange 11 from the outside in the radial direction, and has a central axis that coincides with the first rotation center axis R1 to the inner diameter side of the disk portion 21b. Extends in the axial direction.

  In the continuously variable transmission 1, a bearing (for example, a roller bearing or a needle bearing) B2 is provided between the inner peripheral surface of the second cylindrical portion 21c of the output flange 21 and the outer peripheral surface of the cylindrical portion 11a of the input flange 11. It is arranged. In the continuously variable transmission 1, a thrust bearing (here, a thrust roller bearing, a thrust needle bearing, a thrust ball bearing, etc.) TB is disposed between the disk portions 11b and 21b of the input flange 11 and the output flange 21, respectively. Yes. Therefore, the input flange 11 and the output flange 21 can be rotated relative to each other via the bearing B2 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 flange 11. The torque cam 71 is disposed between the second rotating member 20 and the output flange 21. When the torque cam 70 transmits rotational torque between the input flange 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 torque transmitted. A thrust (axial force) toward the ball 50 is generated. When the torque cam 71 transmits the rotational torque between the output flange 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 flange 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 bearing RB and the angular bearing AB 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 RB, the outer ring of the angular bearing AB, 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.

  Note that the sun roller 30 of the present embodiment has a divided structure including two parts, a first divided structure 32 supported by the angular bearing AB and a second divided structure 33 supported by the bearing RB. Here, the 1st division structure 32 is arranged on the 1st rotation member 10 side with angular bearing AB, and the 2nd division structure 33 is arranged on the 2nd rotation member 20 side with bearing RB. The first divided structure 32 and the second divided structure 33 oppose each other in proximity to the axial direction of the first rotation center axis R1. 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 configured by the outer peripheral surface of the first divided structure 32 and the outer peripheral surface of the second divided structure 33. 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, and the like around the first rotation center axis R1. The carrier 40 holds a support shaft (also called a spindle or a pinion pin) 51 of the planetary ball 50 in a state where the planetary ball 50 can be tilted. The carrier 40 has a first guide portion 44 and a second guide portion as guide portions for holding the end portion of the support shaft 51 and holding the end portion of the support shaft 51 in a state in which the planetary ball 50 can be tilted. 45. The first guide portion 44 and the second guide portion 45 are the first guide end portion 52 and the second guide end portion 53 as guide end portions that are ends of the support shaft 51 and are formed in a cylindrical shape or a columnar shape, respectively. Is inserted. The first guide portion 44 and the second guide portion 45 hold the first guide end portion 52 and the second guide end portion 53 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 rotatable about a second rotation center axis R2 that is different from the first rotation center axis R1, and is sandwiched between the first rotation member 10 and the second rotation member 20, and the first rotation member 10 and Torque can be transmitted to and from the second rotating member 20. As will be described later, the planetary ball 50 can change a gear ratio, which is a rotation speed ratio between the rotating elements, by a tilting operation. 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. Here, the planetary ball 50 has a through hole 50a into which the support shaft 51 is inserted. The planetary ball 50 is rotatably supported by radial bearings RB3 and RB4 provided in the through hole 50a. 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 carrier 40 holds both ends of the support shaft 51 in a state in which the planetary balls 50 can be tilted by the fixed carrier 41 and the movable carrier 42. The carrier 40 can change the speed ratio, which is the rotational speed ratio between the rotating elements, by tilting the planetary balls 50 together with the support shaft 51 by the relative rotation of the fixed carrier 41 and the movable carrier 42.

  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 can rotate relative to the transmission shaft 60 within a range of a predetermined rotation angle. 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.

  Here, the support shaft 51 of the present embodiment has a divided structure of 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). The support shaft 51 is formed such that the outer diameters of the first guide end portion 52 and the second guide end portion 53 are larger than the outer diameter of the intermediate portion 54. The support shaft 51 has a second guide end portion 53 formed integrally with the intermediate portion 54, and a first guide end portion 52 formed separately from the intermediate portion 54 and assembled to the intermediate portion 54. Thereby, the continuously variable transmission 1 can improve the assemblability of the radial bearings RB3 and RB4 when the radial bearings RB3 and RB4 are provided between the planetary ball 50 and the support shaft 51.

  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. The carrier 40 may be configured without the plate 43.

  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, when the planetary ball 50 is tilted to one side (see, for example, the speed ratio γmax position indicated by a one-dot chain line in FIG. 2), the second rotating member 20 is rotated at a lower speed than the first rotating member 10 (deceleration). ), When it is tilted to the other side (see, for example, the gear ratio γmin position indicated by a one-dot chain line in FIG. 2), the rotation speed is higher than that of the first rotating member 10 (acceleration). 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 with respect to the support shaft 51 in accordance with the relative rotation of the movable carrier 42 and the fixed carrier 41. Let The carrier 40 is configured such that, for example, rotational power is transmitted from a driving device such as a motor to a movable carrier 42 via a transmission member such as a worm gear in accordance with control of an ECU (not shown). 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.

  In the continuously variable transmission 1 configured as described above, for example, when torque is transmitted to the input flange 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 flange 21 via 71 or the like. At this time, for example, when the torque is transmitted from the input flange 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. 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.

  By the way, in the continuously variable transmission 1 of the present embodiment, the amount of heat generated at the input / output contact tends to vary greatly according to the speed ratio γ. For example, when the continuously variable transmission 1 tilts the planetary ball 50 toward the acceleration side (see, for example, the support shaft 51 (γmin) in FIG. 2), the contact surface of the first rotating member 10 that is a torque input unit. While the spin speed (or spin amount) resulting from the peripheral speed difference at the contact point (contact ellipse) P1 between 10a and the planetary ball 50 is relatively large, the contact surface 20a of the second rotating member 20 that is the torque output unit. And the planetary ball 50 tend to have a relatively small spin speed (or spin amount) due to the peripheral speed difference at the contact point (contact ellipse) P2. On the other hand, when the continuously variable transmission 1 tilts the planetary ball 50 toward the deceleration side (see, for example, the support shaft 51 (γmax) in FIG. 2), the contact surface 10a of the first rotating member 10 and the planetary ball 50 The spin speed at the contact point P1 with the contact point P1 becomes relatively small, while the spin speed at the contact point P2 between the contact surface 20a of the second rotating member 20 and the planetary ball 50 tends to become relatively high. Then, the spin loss caused by the heat generated by the spin at the contact points P1 and P2 is the spin speed (spin amount), the contact point area (in other words, the contact ellipse radius) and the contact point surface pressure (for example, contact points P1 and P2). , The contact surface pressure of the outer periphery of the contact ellipse). For example, the spin loss at the contact points P1 and P2 becomes relatively larger as the spin speed at the contact points P1 and P2 is relatively larger, and becomes relatively larger as the contact point area is relatively larger. The surface pressure tends to increase as the surface pressure increases.

  FIG. 6 is a diagram illustrating an example of the dependency of the spin loss on the transmission ratio in the continuously variable transmission 1. FIG. 6 represents the relationship between the gear ratio and the loss, with the horizontal axis representing the gear ratio [γ] and the vertical axis representing the loss [W]. In FIG. 6, a region T1 represents spin loss at the contact point P1 on the first rotating member 10 side. A region T2 represents the spin loss at the contact point P2 on the second rotating member 20 side. The region T3 represents the spin loss at the contact point P3 (see FIG. 2) between the first divided structure 32 (input side) of the sun roller 30 and the planetary ball 50. A region T4 represents the spin loss at the contact point P4 (see FIG. 2) between the second divided structure 33 (output side) of the sun roller 30 and the planetary ball 50.

  As shown in FIG. 6, when the continuously variable transmission 1 tilts the planetary ball 50 to the speed increasing side as described above (see, for example, the support shaft 51 (γmin) in FIG. 2), the first rotating member While the spin loss at the contact point P1 on the 10 side is relatively large, the spin loss at the contact point P2 on the second rotating member 20 side tends to be relatively small. On the other hand, when the continuously variable transmission 1 tilts the planetary ball 50 to the deceleration side as described above (see, for example, the support shaft 51 (γmax) in FIG. 2), the contact point on the first rotating member 10 side. While the spin loss at P1 is relatively small, the spin loss at the contact point P2 on the second rotating member 20 side tends to be relatively large.

  Therefore, the continuously variable transmission 1 according to the present embodiment improves the lubrication performance by changing the lubrication state with respect to the contact points P1 and P2 in accordance with the gear ratio γ between the rotating elements.

  Specifically, as shown in FIGS. 1 and 2, the continuously variable transmission 1 of the present embodiment supplies oil as a lubricating medium (which may also be used as traction oil) to the sliding portions of the respective portions. As a mechanism for this, an oil pump 80, a transmission shaft supply path 81, a movable carrier supply path 82 as a movable element supply path, a support shaft supply path 83, and the like are configured. The oil pump 80 is driven by power generated by a traveling power source of a vehicle on which the continuously variable transmission 1 is mounted, for example, so as to pressurize and discharge the oil to a predetermined hydraulic pressure. The continuously variable transmission 1 supplies the oil discharged from the oil pump 80 to the contact points P1 to P4 and the sliding portions of each part via the transmission shaft supply path 81, the movable carrier supply path 82, the support shaft supply path 83, and the like. These are lubricated.

  The transmission shaft supply path 81 is an oil (lubricating medium) supply path formed in the transmission shaft 60. The transmission shaft supply path 81 is provided in the transmission shaft 60 and is supplied with oil. The transmission shaft supply path 81 includes an axial supply path 81a, a sun roller side radial supply path 81b (hereinafter also referred to as “roller side radial supply path 81b”), a speed increasing radial direction supply path 81c, and a deceleration time. A radial supply path 81d and the like are included.

  The axial supply path 81 a is formed along the axial direction inside the transmission shaft 60, one end is opened, and the other end is connected to the discharge port side of the oil pump 80.

  The roller side radial supply path 81b, the speed increasing radial direction supply path 81c, and the deceleration radial direction supply path 81d are formed along the radial direction inside the transmission shaft 60, respectively, and the radially inner end is axial. It communicates with the supply path 81a, and its radially outer end opens toward the radially outer side.

  The roller-side radial supply path 81 b is formed at a position where the radially outer opening faces the oil reservoir 34 of the sun roller 30. A plurality of roller side radial supply paths 81b are provided radially (for example, eight corresponding to the plurality of planetary balls 50) about the first rotation center axis R1. The plurality of roller side radial direction supply paths 81b are provided at equal intervals around the first rotation center axis R1.

  Here, the oil reservoir 34 of the sun roller 30 is an annular recess formed between the first divided structure 32 and the second divided structure 33 with respect to the axial direction of the first rotation center axis R1. . The oil reservoir 34 is a space that can temporarily store the oil supplied from the roller-side radial supply path 81b. The oil reservoir 34 is connected to a sun roller supply path 35 formed between the first divided structure 32 and the second divided structure 33. In the sun roller supply path 35, the radially inner end communicates with the oil reservoir 34, and the radially outer end opens at the outer peripheral surface 31.

  The speed increasing radial direction supply path 81 c and the speed reducing radial direction supply path 81 d are formed at positions where the radially outer opening faces the inner peripheral surface of the movable carrier 42. The speed increasing radial direction supply path 81c and the speed reducing radial direction supply path 81d are formed at different positions with respect to the axial direction of the first rotation center axis R1. Here, the speed increasing radial direction supply path 81c and the speed reducing radial direction supply path 81d are formed such that the speed reducing radial direction supply path 81d is closer to the first rotating member 10 than the speed increasing radial direction supply path 81c. As shown in FIG. 7, the speed increasing radial direction supply path 81c is radially plural about the first rotation center axis R1 (here, eight corresponding to a plurality of speed increasing supply paths 82a described later). Provided. The plurality of speed increasing radial direction supply paths 81c are provided at equal intervals around the first rotation center axis R1. A plurality of deceleration-time radial supply paths 81d are provided radially (here, eight corresponding to a plurality of deceleration-time supply paths 82b described later) centering on the first rotation center axis R1. The plurality of deceleration radial supply paths 81d are provided at equal intervals around the first rotation center axis R1. The plurality of deceleration-time radial supply paths 81d are formed so as to be out of phase with the plurality of acceleration-time radial supply paths 81c. That is, when viewed in the axial direction of the first rotation center axis R1 (when viewed in the direction of arrow A in FIG. 1), a plurality of speed increasing radial supply paths 81c and a plurality of deceleration radial supplying paths 81d. Is formed so as not to overlap at positions shifted from each other around the first rotation center axis R1.

  The movable carrier supply path 82 is provided in the movable carrier 42 so as to extend along the direction intersecting the first rotation center axis R <b> 1, here, the radial direction. The movable carrier supply path 82 is capable of supplying the oil supplied to the transmission shaft supply path 81 in the transmission shaft 60 to the planetary ball 50 side according to the speed ratio γ between the rotating elements. The movable carrier supply path 82 includes a plurality of supply paths corresponding to the speed ratio γ. The movable carrier supply path 82 of the present embodiment includes a speed increase supply path 82a as a first supply path and a deceleration supply path 82b as a second supply path.

  The speed increasing supply path 82a supplies oil to the transmission shaft 60 when the speed ratio γ between the rotating elements (between the first rotating member 10 and the second rotating member 20) is a predetermined speed ratio on the speed increasing side. Is supplied from the side to each planetary ball 50 side. The deceleration supply path 82b supplies oil from the transmission shaft 60 side to each planetary ball 50 side when the gear ratio γ between the rotating elements is a predetermined gear ratio on the deceleration side. The predetermined speed ratio on the acceleration side and the predetermined speed ratio on the deceleration side are typically set in advance according to the required lubrication performance or the like based on actual vehicle evaluation or the like. Here, the predetermined speed ratio on the speed increasing side is set to, for example, the minimum speed ratio γmin at which the spin loss at the contact point P1 on the first rotating member 10 side becomes relatively large. The predetermined gear ratio on the deceleration side is set to the maximum gear ratio γmax at which the spin loss at the contact point P2 on the second rotating member 20 side is relatively large, for example. The speed increasing supply path 82a supplies oil from the transmission shaft 60 side to each planetary ball 50 side when the speed ratio γ is the minimum speed ratio γmin. The deceleration supply path 82b supplies oil from the transmission shaft 60 side to each planetary ball 50 side when the speed ratio γ is the maximum speed ratio γmax.

  The movable carrier supply path 82 of the present embodiment has a communication state with the transmission shaft supply path 81 according to the relative rotation of the movable carrier 42 and the transmission shaft 60 accompanying the relative rotation of the movable carrier 42 and the fixed carrier 41. Switch. As a result, the state of oil supply to the planetary ball 50 is switched in the movable carrier supply path 82 in accordance with the speed ratio γ. Here, the movable carrier supply path 82 is a communication state between the speed increasing supply path 82a and the transmission shaft supply path 81 according to the relative rotation of the movable carrier 42 and the transmission shaft 60, and the deceleration supply path 82b and the transmission shaft. The communication state with the supply path 81 is switched.

  Specifically, a plurality of speed increasing supply paths 82a are provided radially (eight corresponding to the plurality of second guide portions 45) centered on the first rotation center axis R1. The plurality of speed increasing supply paths 82a are provided at equal intervals around the first rotation center axis R1. The plurality of speed increasing supply paths 82 a are formed in the movable carrier 42 along the radial direction. Each speed increasing supply path 82a has a position where the radially inner end opens to the corresponding speed increasing radial supply path 81c when the speed ratio γ is a predetermined speed ratio, here, the minimum speed ratio γmin. Formed. That is, each speed increasing supply path 82a has a speed increasing speed corresponding to the radially inner end when the rotational angle of the movable carrier 42 with respect to the transmission shaft 60 is the minimum speed ratio rotating angle corresponding to the minimum speed ratio γmin. It faces the radial supply path 81c. Each speed increasing supply passage 82a opens to the second guide portion 45 corresponding to the radially outer end. Here, the speed increasing supply path 82a is formed at a position where the radially outer opening faces the second guide end 53 of the support shaft 51 when the speed ratio γ is the minimum speed ratio γmin. (See FIG. 8 described later).

  A plurality of deceleration supply paths 82b are provided radially (here, eight corresponding to the plurality of second guide portions 45) about the first rotation center axis R1. The plurality of deceleration supply paths 82b are provided at equal intervals around the first rotation center axis R1. The plurality of deceleration supply paths 82b are formed in the movable carrier 42 along the radial direction. Each deceleration supply path 82b is formed at a position where the radially inner end portion opens to the corresponding deceleration radial supply path 81d when the speed ratio γ is a predetermined speed ratio, here, the maximum speed ratio γmax. Is done. That is, each deceleration supply path 82b has a radial direction at the time of deceleration corresponding to the radially inner end when the rotation angle of the movable carrier 42 with respect to the transmission shaft 60 is the maximum transmission ratio rotation angle corresponding to the maximum transmission ratio γmax. Opposite the supply path 81d. Each deceleration supply path 82b opens to the second guide portion 45 corresponding to the radially outer end. Here, the deceleration supply path 82b is formed such that the opening on the outer side in the radial direction is positioned in the vicinity of the opening of the acceleration supply path 82a.

  The support shaft supply path 83 is a supply path provided for each support shaft 51, and supplies oil supplied to the planetary ball 50 side via the movable carrier supply path 82 to the fixed carrier 41 side. Here, each support shaft supply path 83 can guide the oil supplied into the second guide portion 45 via the movable carrier supply path 82 and the like from the movable carrier 42 side to the fixed carrier 41 side. The support shaft supply path 83 is formed in the support shaft 51 along the axial direction, and penetrates from the first guide end portion 52 to the second guide end portion 53. The support shaft supply path 83 has an end portion on the first guide end portion 52 side opened to the first guide portion 44, and an end portion on the second guide end portion 53 side opened to the second guide portion 45.

  In the continuously variable transmission 1 configured as described above, for example, oil discharged from the oil pump 80 is supplied to the axial supply path 81a of the transmission shaft supply path 81 as shown in FIG. The oil supplied to the axial supply path 81a is stored in the oil reservoir 34 through the roller side radial supply path 81b. The oil stored in the oil reservoir 34 is sprayed from the opening on the outer peripheral surface 31 side to the planetary ball 50 side through the sun roller supply path 35 by the discharge pressure from the oil pump 80 and the centrifugal force accompanying the rotation of the sun roller 30. . As a result, the continuously variable transmission 1 causes the contact points P1, P2, P3, P4 between the first rotating member 10, the second rotating member 20, the sun roller 30 and each planetary ball 50 by the oil sprayed on the planetary ball 50. Etc. are lubricated and cooled. Further, a part of the oil sprayed on the planetary balls 50 is blown off as each planetary ball 50 rotates (rotates), and the rolling surfaces of the first guide end 52 and the second guide end 53 It is supplied to the sliding parts of each part and lubricates and cools them. For example, a part of the oil blown off by the planetary ball 50 is supplied into the through hole 50a, and the shaft center part of the planetary ball 50, the support shaft 51, the sliding parts of the radial bearings RB3, RB4, and the like. Lubricate and cool. The radial bearings RB3 and RB4 may employ tapered roller bearings or the like in order to positively receive oil on the inner peripheral side of the sun roller 30.

  At this time, as shown in FIG. 2, the continuously variable transmission 1 has a gear ratio γ of 1, that is, when the first rotation center axis R1 and the second rotation center axis R2 are parallel to each other. The communication between the speed increasing supply path 82a and the speed increasing radial direction supply path 81c and the communication between the deceleration time supplying path 82b and the speed decreasing radial direction supply path 81d are both blocked. Therefore, in the continuously variable transmission 1, when the gear ratio γ is 1, the oil supply to the planetary ball 50 side through the movable carrier supply path 82 is stopped (via the movable carrier supply path 82). Oil is not supplied). As a result, the continuously variable transmission 1 can relatively suppress the amount of oil supplied to the planetary ball 50 side in a shift state in which spin loss or the like is not so great, thereby reducing stirring loss and Pump load can be suppressed. As a result, the continuously variable transmission 1 can improve power transmission efficiency.

  The continuously variable transmission 1 has a speed change state in which spin loss and the like tend to be relatively large, and here, at least a speed change ratio γ is a minimum speed ratio γmin that can be realized, and a maximum speed ratio γmax that can be realized. If so, oil can be supplied to the planetary ball 50 side via the movable carrier supply path 82. As a result, the continuously variable transmission 1 can relatively increase the amount of oil supplied to the planetary ball 50 side in a shift state in which spin loss or the like is relatively large. As a result, the continuously variable transmission 1 is in contact with the contact points P1, P2, and the oil supplied to the planetary ball 50 via the movable carrier supply path 82 in a shift state where spin loss or the like is relatively large. P3, P4, etc. can be more actively lubricated and cooled.

  More specifically, in the continuously variable transmission 1, as shown in FIG. 8, when the speed ratio γ is the minimum speed ratio γmin, that is, the second rotation center axis R2 increases with respect to the first rotation center axis R1. When it inclines to the high speed side, the communication between the deceleration supply path 82b and the deceleration radial supply path 81d is maintained in a blocked state. That is, the deceleration-time radial supply path 81d and the deceleration-time supply path 82b are both closed. On the other hand, in the continuously variable transmission 1, the movable carrier 42 rotates relative to the transmission shaft 60 in the course of the shifting operation in which the transmission ratio γ is the minimum transmission ratio γmin, and the rotation angle of the movable carrier 42 is the minimum transmission ratio rotation. When it becomes a corner, the speed increasing supply path 82a opens and communicates with the speed increasing radial direction supply path 81c. As a result, the continuously variable transmission 1 allows a part of the oil supplied to the axial supply path 81a to pass through the speed increasing radial direction supply path 81c, the speed increasing supply path 82a, the second guide portion 45, and the like. It can be supplied to the planetary ball 50 side. Therefore, the continuously variable transmission 1 can lubricate each part by increasing the amount of oil supplied to the planetary ball 50 side in a gear shifting state in which spin loss or the like tends to be relatively large.

  At this time, in the support shaft supply path 83, the end of the support shaft 51 on the second guide end 53 side of the second guide portion 45 is an opening (exit) on the radially outer side of the speed increasing supply path 82a. It is located in the vicinity (here, a position facing the opening and continuing). For this reason, a part of the oil supplied to the planetary ball 50 side through the speed increasing supply path 82a, the second guide portion 45, etc. is supplied into the support shaft supply path 83 and supplied to the fixed carrier 41 side. The Then, the oil supplied to the fixed carrier 41 side via the support shaft supply path 83 is directly supplied to the vicinity of the position corresponding to the contact point P1 on the outer peripheral surface of the planetary ball 50. That is, the movable carrier supply path 82 is in contact with the first rotating member 10 and the planetary ball 50 when the speed ratio γ between the rotating elements is a predetermined speed ratio on the acceleration side, here, the minimum speed ratio γmin. The oil supply amount to the point P1 side can be made larger than the oil supply amount to the contact point P2 side between the second rotating member 20 and the planetary ball 50. As a result, the continuously variable transmission 1 suppresses the supply of oil to the contact point P2 and the portion other than the contact point P1, where the spin loss tends to be small when the speed ratio γ is the minimum speed ratio γmin ( Or, while maintaining the normal amount), the amount of oil supplied to the contact point P1, where the spin loss tends to increase when the speed ratio γ is the minimum speed ratio γmin, is increased to efficiently supply the oil. be able to.

  On the other hand, as shown in FIG. 9, in the continuously variable transmission 1, when the speed ratio γ is the maximum speed ratio γmax, that is, the second rotation center axis R2 is inclined toward the deceleration side with respect to the first rotation center axis R1. In this case, the communication between the speed increasing supply path 82a and the speed increasing radial direction supply path 81c is maintained in a blocked state. That is, the speed increasing radial direction supply path 81c and the speed increasing supply path 82a are both closed. On the other hand, in the continuously variable transmission 1, the movable carrier 42 rotates relative to the transmission shaft 60 in the course of the shifting operation in which the speed ratio γ is the maximum speed ratio γmax, and the rotation angle of the movable carrier 42 is the maximum speed ratio rotation. When it becomes a corner, the deceleration supply path 82b opens and communicates with the deceleration radial supply path 81d. As a result, the continuously variable transmission 1 transfers a part of the oil supplied to the axial supply path 81a via the deceleration radial supply path 81d, the deceleration supply path 82b, the second guide portion 45, and the like. 50 side can be supplied. Therefore, the continuously variable transmission 1 can lubricate each part by increasing the amount of oil supplied to the planetary ball 50 side in a gear shifting state in which spin loss or the like tends to be relatively large.

  At this time, in the support shaft supply path 83, the end on the second guide end 53 side of the support shaft 51 is separated from the opening (exit) in the radial direction of the deceleration supply path 82 b in the second guide portion 45. Is located. For this reason, the oil supplied to the planetary ball 50 side through the supply path 82b during deceleration, the second guide portion 45, etc. is basically not supplied into the support shaft supply path 83, but the planetary ball 50 Is directly supplied in the vicinity of the position corresponding to the contact point P2 on the outer peripheral surface of the. That is, the movable carrier supply path 82 has a contact point between the second rotating member 20 and the planetary ball 50 when the speed ratio γ between the rotating elements is a predetermined speed ratio on the deceleration side, here, the maximum speed ratio γmax. The oil supply amount to the P2 side can be made larger than the oil supply amount to the contact point P1 side between the first rotating member 10 and the planetary ball 50. As a result, the continuously variable transmission 1 suppresses oil supply to portions other than the contact point P1 and the contact point P2 where the spin loss tends to be small when the speed ratio γ is the maximum speed ratio γmax ( (Alternatively, while maintaining the normal amount), the amount of oil supplied to the contact point P2, where the spin loss tends to increase when the speed ratio γ is the maximum speed ratio γmax, is increased to efficiently supply the oil. be able to.

  As a result, the continuously variable transmission 1 is required to have a relatively large amount of oil supply while suppressing the supply of oil to a location where a relatively small amount of oil supply is sufficient according to the gear ratio γ. The oil can be positively supplied to the place where the planetary ball 50 is located via the movable carrier supply path 82 and the like, and the planetary ball 50 and its peripheral parts can be appropriately lubricated. That is, the continuously variable transmission 1 can increase or decrease the amount of oil supplied to the lubrication target parts (for example, the contact points P1 and P2) according to the magnitude of the spin loss of each part according to the speed ratio γ. Appropriate lubrication performance according to the gear ratio γ can be ensured. As a result, the continuously variable transmission 1 can achieve both suppression of agitation loss and pump load and suppression of spin loss, and improve power transmission efficiency. Further, when the continuously variable transmission 1 is applied to a vehicle, basically, the frequency of use of the gear ratio on the speed increasing side tends to be relatively high. For example, the gear ratio γ is a predetermined speed change on the speed increasing side. When the ratio (maximum transmission ratio γmax) is obtained, the amount of oil supplied to the contact point P1 and the like on the first rotating member 10 side can be increased and the rolling life can be improved along with the loss reduction. .

  According to the continuously variable transmission 1 according to the embodiment described above, the transmission shaft 60, the first rotating member 10 and the second rotating member 20, the planetary ball 50, the support shaft 51, the carrier 40, and the movable And a carrier supply path 82. 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 that is different from the first rotation center axis R1, and is sandwiched between the first rotation member 10 and the second rotation member 20, and the first rotation member 10 and Torque can be transmitted to and from 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 both end portions 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 rotation member 10 and the second rotation member 20 with the first rotation center axis R1 as the rotation center, and the transmission shaft on one end side of the support shaft 51. 60, a fixed carrier 41 provided so as not to rotate relative to the support shaft 51, and a movable carrier 42 disposed on the other end side of the support shaft 51 so as to face the fixed carrier 41 and provided so as to be rotatable relative to the transmission shaft 60. The carrier 40 holds both ends of the support shaft 51 in a state where the planetary ball 50 can be tilted by the fixed carrier 41 and the movable carrier 42. The carrier 40 can change the gear ratio, which is the rotation speed ratio between the rotating elements, by tilting the planetary ball 50 together with the support shaft 51 by the relative rotation of the fixed carrier 41 and the movable carrier 42. The movable carrier supply path 82 is provided in the movable carrier 42 so as to extend in a direction intersecting the first rotation center axis R1, and the oil supplied into the transmission shaft 60 is a planet according to the gear ratio between the rotary elements. It can be supplied to the ball 50 side.

  Accordingly, the continuously variable transmission 1 can change the lubrication state by adjusting the amount of oil supplied to the lubrication target portion according to the speed ratio γ (or the magnitude of the spin loss, etc.). It is possible to ensure proper lubrication performance. As a result, the continuously variable transmission 1 can properly lubricate and improve the cooling performance, so that the power transmission efficiency can be improved. Since the continuously variable transmission 1 can be properly lubricated, it is possible to suppress a decrease in the rolling life of the planetary ball 50 or the like.

  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.

  The continuously variable transmission 1 described above may be configured without the support shaft supply path 83. Even in this case, the continuously variable transmission 1 can increase the supply amount to the planetary ball 50 side at a predetermined speed ratio (for example, the minimum speed ratio γmin and the maximum speed ratio γmax). Appropriate lubrication performance according to the gear ratio γ can be ensured.

  The movable carrier supply path 82 (movable element supply path) described above includes either one of the acceleration supply path 82a (first supply path) or the deceleration supply path 82b (second supply path). May be provided, or a supply path corresponding to a plurality of gear ratios may be included.

1 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)
50 Planetary ball (rolling member)
51 Support shaft 60 Transmission shaft 81 Transmission shaft supply path 82 Movable carrier supply path (movable element supply path)
82a Speed increasing supply path (first supply path)
82b Supply path during deceleration (second supply path)
83 Support shaft supply path P1, P2, P3, P4 Contact point R1 First rotation center axis R2 Second rotation center axis

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 the rotation center, and the rotation is relative to the transmission shaft on one end side of the support shaft. A fixed element provided impossible, and a movable element disposed on the other end of the support shaft so as to face the fixed element and provided to be rotatable relative to the transmission shaft, the fixed element and the movable element The both ends of the support shaft are held in a state in which the rolling member can be tilted, and the rolling member is tilted together with the support shaft by relative rotation of the fixed element and the movable element. A supporting rotating element capable of changing a transmission gear ratio that is a rotating speed ratio between the rotating elements;
The movable element is provided to extend in a direction intersecting the first rotation center axis, and the lubricating medium supplied into the transmission shaft is moved to the rolling member side in accordance with a gear ratio between the rotation elements. A movable element supply path that can be supplied,
Continuously variable transmission. The movable element supply path includes a first supply path that supplies the lubricating medium from the transmission shaft side to the rolling member side when the transmission gear ratio between the rotating elements is a predetermined transmission gear ratio. Have
The continuously variable transmission according to claim 1. The movable element supply path includes a second supply path for supplying the lubricating medium from the transmission shaft side to the rolling member side when a speed ratio between the rotating elements is a predetermined speed ratio on the deceleration side. ,
The continuously variable transmission according to claim 1 or 2. A transmission shaft supply path provided in the transmission shaft and supplied with the lubricating medium;
The movable element supply path switches the communication state with the transmission shaft supply path according to the relative rotation of the movable element and the transmission shaft with relative rotation of the movable element and the fixed element.
The continuously variable transmission according to any one of claims 1 to 3. The support shaft is provided along the second rotation center axis, and a support shaft supply path for supplying the lubricating medium supplied to the rolling member side to the fixed element side via the movable element supply path. Have
The continuously variable transmission according to any one of claims 1 to 4. The rolling member is capable of transmitting torque input to the first rotating element to the second rotating element;
The movable element supply path supplies the lubricating medium to the contact point side between the first rotating element and the rolling member when the gear ratio between the rotating elements is a predetermined gear ratio on the speed increasing side. When the amount is larger than the supply amount of the lubricating medium to the contact point side of the second rotating element and the rolling member, and the gear ratio between the rotating elements is a predetermined gear ratio on the deceleration side, The amount of supply of the lubricating medium to the contact point side of the second rotating element and the rolling member is made larger than the amount of supply of the lubricating medium to the contact point side of the first rotating element and the rolling member.
The continuously variable transmission according to any one of claims 1 to 5. The predetermined gear ratio on the speed increasing side is a minimum gear ratio that can be realized,
The predetermined gear ratio on the deceleration side is a maximum gear ratio that can be realized.
The continuously variable transmission according to claim 6.

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