JP2013151967A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure an oil quantity of lubricating oil between a rolling member and a support shaft.SOLUTION: A continuously variable transmission includes a shaft 60 having on the inside oil passages 61 and 62 that can supply lubricating oil toward an outer peripheral surface, first and second rotary members 10 and 20, a sun roller 30 and a carrier 40, planetary balls 50 arranged on an outer peripheral surface of the sun roller 30 in a radial shape and sandwiched by the first and second rotary parts 10 and 20, support shafts 51 having on both ends a projection part for tiltably holding the planetary ball 50 by the carrier 40 and relatively rotating the planetary ball 50 by being inserted into the planetary ball 50, an iris plate 80 for changing the gear ratio between the first and second rotary members 10 and 20 by tilting of the respective planetary balls 50, and an oil guiding part for guiding the lubricating oil discharged from the oil passage 62 of the shaft 60 to the projection part of the support shaft 51. The oil guiding part has oil guiding walls 45 and 46 in the carrier 40 for guiding the lubricating oil discharged from the oil passage 62 to the projection part of the support shaft 51.

Description

  The present invention includes a plurality of rotating elements having a common rotating shaft, and a plurality of rolling members arranged radially with respect to the rotating shaft, and each rolling element sandwiched between two of the rotating elements. The present invention relates to a traction drive type continuously variable transmission that continuously changes a gear ratio between input and output by tilting a member.

  Conventionally, as this type of continuously variable transmission, a transmission shaft serving as a rotation center, three rotational elements that can rotate relative to the central axis of the transmission shaft, and a radial shape with respect to the rotation central shaft A ball planetary comprising: a plurality of rolling members disposed between the three rotating elements; and a fixing element that is disposed coaxially with the rotation center axis and holds each rolling member in a tiltable manner. The formula is known. In this ball planetary continuously variable transmission, each rolling member is sandwiched between the first rotating element and the second rotating element that are arranged to face each other, and each rolling member is an outer peripheral surface of the third rotating element. Is placed on top. Further, in this ball planetary continuously variable transmission, a supporting shaft for rotating and supporting the rolling member is prepared for each rolling member, and the rolling member is provided via protruding portions at both ends of the supporting shaft. Is held by the fixed element. Patent Documents 1-3 below disclose a ball planetary continuously variable transmission.

  In the continuously variable transmission of Patent Document 1, the transmission shaft has an axial oil passage and a radial oil passage, and the lubricating oil sent to the axial oil passage is in the radial direction. The oil is supplied to a bearing of the sun roller (third rotating element) through an oil passage. Further, in the continuously variable transmission of this Patent Document 1, an oil passage that is inclined so that the lubricating oil is discharged toward the carrier by centrifugal force is provided in the sun roller. In the continuously variable transmission of Patent Document 2, a spiral groove is provided on the outer peripheral surface of the support shaft, and lubricating oil is supplied between the support shaft and the planetary ball (rolling member) via the spiral groove. ing. Further, this Patent Document 2 also discloses a continuously variable transmission in which an internal oil passage is formed in a leg portion (one component forming a tilting mechanism of a planetary ball) that supports the support shaft.

  In the continuously variable transmission of Patent Document 3, an oil passage for supplying lubricating oil to the planetary ball is provided on the transmission shaft side of the output side rotating member (rotating element).

US Patent Application Publication No. 2010/0093480 JP 2010-101696 A JP 2011-196528 A

  By the way, in the ball planetary continuously variable transmission described above, the lubricating oil supplied to the gap between the rolling member and the support shaft is transmitted through a protruding portion from the rolling member on the support shaft. For example, since the lubricating oil adheres to the outer peripheral surface of the protruding portion due to dripping from other members or the like, the adhering lubricating oil propagates on the outer peripheral surface of the support shaft to the gap between the rolling member and the support shaft. Supplied by For this reason, in order to supply lubricating oil between the rolling member and the support shaft, the lubricating oil must adhere to the outer peripheral surface of the support shaft. Therefore, in this continuously variable transmission, there is a possibility that the lubricating oil supplied between the rolling member and the support shaft will be insufficient.

  SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a continuously variable transmission capable of improving the disadvantages of the conventional example and ensuring the amount of lubricating oil between the rolling member and the support shaft. And

  In order to achieve the above object, the present invention provides a transmission shaft having an oil passage capable of supplying lubricating oil toward an outer peripheral surface, and a first central shaft common to the central shaft of the transmission shaft. To the fourth power transmission element and a plurality of the first and second powers arranged radially on the outer surface of the third power transmission element and opposed to each other with the first central axis as a center. A rolling member sandwiched between transmission elements, and projecting portions from the rolling member for holding the rolling member in a tiltable manner by the fourth power transmission element at both ends; A support shaft that is inserted to relatively rotate the rolling member about the second central axis, and between each of the first power transmission element and the second power transmission element by tilting each of the rolling members. A transmission for changing a transmission ratio, and lubricating oil discharged from an oil passage of the transmission shaft; An oil guide portion that guides to an exit portion, wherein the oil guide portion has an oil guide wall through which the lubricating oil discharged from the oil passage of the transmission shaft is guided to the protruding portion of the support shaft. It is characterized by having a power transmission element.

  Here, the oil guiding portion is supplied with lubricating oil discharged from the oil passage of the transmission shaft, and the third power transmission through the oil guiding path for discharging the introduced lubricating oil toward the oil guiding wall. It is desirable to prepare for the element.

  The oil guide wall is preferably provided in a guide portion of the fourth power transmission element that guides the protruding portion of the support shaft when the rolling member is tilted.

  In the continuously variable transmission according to the present invention, since the lubricating oil discharged from the oil passage of the transmission shaft is guided to the protruding portion of the support shaft, lubrication between the rolling member passing through the protruding portion and the support shaft is performed. The amount of oil can be secured.

FIG. 1 is a sectional view showing a configuration of an embodiment of a continuously variable transmission including a ball planetary continuously variable transmission mechanism according to the present invention. FIG. 2 is a diagram illustrating the guide portion of the support shaft and the oil guide wall in the carrier. FIG. 3 is a diagram illustrating the iris plate and the through hole. FIG. 4 is a diagram illustrating the oil guiding unit according to the embodiment. FIG. 5 is a diagram for explaining the oil guiding portion of the first modification. FIG. 6 is a diagram for explaining the oil guiding portion of the second modification. FIG. 7 is a diagram for explaining the oil guiding portion of the third modification. FIG. 8 is a diagram illustrating the oil guide wall of the carrier in the fourth modification.

  Embodiments of a continuously variable transmission according to the present invention will be described below in detail with reference to the drawings. The present invention is not limited to the embodiments.

[Example]
An embodiment of a continuously variable transmission according to the present invention will be described with reference to FIGS.

  First, an example of a traction drive type continuously variable transmission according to the present embodiment will be described with reference to FIG. In this embodiment, a continuously variable transmission provided with a ball planetary continuously variable transmission mechanism corresponding to a traction planetary gear mechanism will be described as an example. Reference numeral 1 in FIG. 1 denotes a ball planetary continuously variable transmission in the present embodiment.

  A ball planetary continuously variable transmission mechanism that forms the main part of the continuously variable transmission 1 includes first to fourth power transmission elements (components for transmitting power) 10 having a common first central axis R1. , 20, 30, 40, and a first power transmission element and a second power transmission element that are arranged radially on the outer peripheral surface of the third power transmission element 30 and opposed to each other with the first central axis R1 as a center. As a transmission shaft disposed at the center of the first to fourth power transmission elements 10, 20, 30, 40, the rolling member 50 sandwiched between 10, 20 and the central axis coincide with the first central axis R 1. A shaft 60. The continuously variable transmission 1 changes the speed ratio γ between input and output by inclining the second central axis R2 with respect to the first central axis R1 and inclining the rolling member 50. In the following, unless otherwise specified, the direction along the first central axis R1 is referred to as the axial direction, and the direction around the first central axis R1 is referred to as the circumferential direction. Further, the direction orthogonal to the first central axis R1 is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side.

  More specifically, in the continuously variable transmission mechanism, the first to fourth power transmission elements 10, 20, 30, and 40 are all between each other about the first central axis R1 and the shaft 60. Some of the first to fourth power transmission elements 10, 20, 30, 40 are fixed elements for the shaft 60, and the remaining three are rotational elements. There are also. Hereinafter, the latter continuously variable transmission mechanism will be described as an example.

  The latter continuously variable transmission mechanism has first to third rotating elements 10, 20, and 30 that can rotate relative to each other and have a common first central axis R1, and the first central axis R1. A plurality of fixing elements 40 having the same axis and a plurality of radial elements centered on the first central axis R1 and a second central axis R2 parallel to the first central axis R1 and a reference position to be described later are provided. And a shaft 60 disposed at the center of rotation of the first to third rotating elements 10, 20, 30 and the center of the fixed element 40.

  In the continuously variable transmission 1, each rolling member 50 is tiltably held by the fixed element 40. The continuously variable transmission 1 is configured to roll with the first to third rotating elements 10, 20, 30 by pressing at least one of the first and second rotating elements 10, 20 against the rolling member 50. An appropriate tangential force (traction force) is generated between the member 50 and the member 50. Further, the continuously variable transmission 1 tilts each rolling member 50 on a tilt plane including its second central axis R2 and first central axis R1, thereby rotating the rotational speed between input and output. Change the ratio of (rotation speed).

  In the continuously variable transmission 1, torque is transmitted between the first to third rotating elements 10, 20, 30 via the rolling members 50. Therefore, any one of the first to third rotating elements 10, 20, and 30 serves as a torque (power) input unit, and another one serves as a torque output unit. For this reason, in this continuously variable transmission 1, the ratio of the rotational speed (the number of rotations) between any rotation element serving as an input unit and any rotation element serving as an output unit is the gear ratio γ. For example, the continuously variable transmission 1 is disposed on the power transmission path of the vehicle. In that case, the input part is connected with the power source side, such as an engine and a motor, and the output part is connected with the drive wheel side. In this continuously variable transmission 1, the rotation operation of each rotation element when torque is input to the rotation element as the input unit is referred to as normal drive, and the rotation element as the output unit is in the direction opposite to that during normal drive. The rotating operation of each rotating element when torque is input is called reverse driving. For example, in the continuously variable transmission 1, according to the example of the preceding vehicle, when the torque is input from the power source side to the rotating element as the input unit and the rotating element is rotated as in acceleration or the like, Driving is performed, and reverse driving is performed when torque in the opposite direction to that during forward driving is input to the rotating rotating element serving as the output unit from the driving wheel side, such as deceleration.

  Here, in the continuously variable transmission 1, the first and second rotating elements 10 and 20 function as a ring gear, which is a traction planetary gear mechanism. The third rotating element 30 and the fixed element 40 function as a sun roller and a carrier in the traction planetary gear mechanism, respectively. Moreover, the rolling member 50 functions as a ball-type pinion in the traction planetary gear mechanism. Hereinafter, the first and second rotating elements 10 and 20 are referred to as “first and second rotating members 10 and 20”, respectively. The third rotating element 30 is referred to as “sun roller 30”, and the fixed element 40 is referred to as “carrier 40”. The rolling member 50 is referred to as a “planetary ball 50”.

  The first and second rotating members 10 and 20 are disk members (disks) or ring members (rings) whose center axes coincide with the first center axis R1, and each planetary ball 50 is opposed in the axial direction. It arrange | positions so that it may be inserted | pinched. In this example, both are circular members.

  Each of the first and second rotating members 10 and 20 has a contact surface that comes into contact with a radially outer peripheral curved surface of each planetary ball 50 described in detail later. Each of the contact surfaces has, for example, a concave arc surface having a curvature equal to the curvature of the outer peripheral curved surface of the planetary ball 50, a concave arc surface having a curvature different from the curvature of the outer peripheral curved surface, a convex arc surface, or a flat surface. doing. Here, the first and second contact surfaces are formed so that the distance from the first central axis R1 to the contact point with each planetary ball 50 is the same length in a reference position state to be described later. The contact angles θ of the rotating members 10 and 20 with respect to the planetary balls 50 are set to the same angle. The contact angle θ is an angle from the reference to the contact point with each planetary ball 50. Here, the radial direction is used as a reference. The respective contact surfaces are in point contact or surface contact with the outer peripheral curved surface of the planetary ball 50. Each contact surface is radially inward with respect to the planetary ball 50 when an axial force (pressing force) is applied from the first and second rotating members 10, 20 toward the planetary ball 50. And an oblique force (normal force) is applied.

  In this example, the first rotating member 10 acts as a torque input portion when the continuously variable transmission 1 is positively driven, and the second rotating member 20 acts as a torque output portion when the continuously variable transmission 1 is positively driven. . Accordingly, the input shaft (first rotation shaft) 11 is connected to the first rotation member 10, and the output shaft (second rotation shaft) 21 is connected to the second rotation member 20. The input shaft 11 and the output shaft 21 can rotate relative to the shaft 60 in the circumferential direction. Further, the input shaft 11 and the output shaft 21 can perform relative rotation in the circumferential direction between the input shaft 11 and the output shaft 21 via the bearing B1 and the thrust bearing TB.

  Between the input shaft 11 and the first rotating member 10, an axial force generator 71 that generates an axial force is provided. The axial force is a pressing force for pressing the first rotating member 10 against each planetary ball 50. Here, a torque cam is used as the axial force generator 71. Accordingly, the axial force generating portion 71 is configured such that the input shaft 11 and the first engaging member are engaged with the engaging portion or engaging member on the input shaft 11 side and the engaging portion or engaging member on the first rotating member 10 side. An axial force is generated between the rotating member 10 and a rotational torque is transmitted, and these are rotated together. On the other hand, between the output shaft 21 and the second rotating member 20, an axial force generator 72 that generates a pressing force (axial force) for pressing the second rotating member 20 against each planetary ball 50 is disposed. Yes. A torque cam similar to the axial force generator 71 is used for the axial force generator 72. The axial force generator 72 is connected to the output shaft 21 via the annular member 22.

  In the continuously variable transmission 1, the lubricating oil in the lower oil pan can be scooped up by the rotation of the first rotating member 10 and the second rotating member 20. Accordingly, a part of the scraped lubricating oil is supplied directly to each part in the casing or directly or dripped from the first and second rotating members 10 and 20 and the inner wall of the casing.

  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. When the sun roller 30 is used as a torque input unit or a torque output unit, an input shaft and an output shaft that are separately configured are connected to the sun roller 30.

  The sun roller 30 is disposed concentrically with the shaft 60. The sun roller 30 is attached to the shaft 60 via the radial bearings RB1 and RB2, and can rotate relative to the shaft 60 in the circumferential direction. A plurality of planetary balls 50 are radially arranged at substantially equal intervals on the outer peripheral surface of the sun roller 30. Accordingly, the outer peripheral surface of the sun roller 30 is a rolling surface when the planetary ball 50 rotates. The sun roller 30 can roll (rotate) each planetary ball 50 by its own rotation, or it can rotate along with the rolling operation (spinning) of each planetary ball 50.

  The planetary ball 50 is a rolling member that rolls on the outer peripheral surface of the sun roller 30. The planetary ball 50 is preferably a perfect spherical body, but it may have a spherical shape at least in the rolling direction, for example, a rugby ball having an elliptical cross section. The planetary ball 50 is rotatably supported by a support shaft 51 that passes through the center of the planetary ball 50. For example, the planetary ball 50 can be rotated relative to the support shaft 51 with the second central axis R2 as a rotation axis (that is, rotation) by the needle bearings NB1 and NB2 disposed between the planetary ball 50 and the outer peripheral surface of the support shaft 51. I have to. The planetary ball 50 can roll on the outer peripheral surface of the sun roller 30 around the support shaft 51. Both ends of the support shaft 51 are projected from the planetary ball 50.

  The reference position of the support shaft 51 is a position where the second central axis R2 is parallel to the first central axis R1, as shown in FIG. The support shaft 51 has a reference position and a position inclined from the reference position in a tilt plane including the center axis (second center axis R2) and the first center axis R1 formed at the reference position. It can swing (tilt) with the planetary ball 50 between them. The tilt is performed with the center of the planetary ball 50 as a fulcrum in the tilt plane.

  The carrier 40 holds each protrusion of the support shaft 51 so as not to prevent the tilting operation of each planetary ball 50. The carrier 40 has, for example, first and second disk portions 41 and 42 having a central axis coinciding with the first central axis R1. The first and second disk portions 41 and 42 are opposed to each other, and are disposed with a space therebetween so that the sun roller 30 and the planetary ball 50 can be disposed therebetween. The carrier 40 has an inner diameter side of at least one of the first and second disk portions 41 and 42 fixed to the outer diameter side of the shaft 60, and relative rotation in the circumferential direction with respect to the shaft 60 and axial direction. Relative movement is disabled. Here, the first disk part 41 is fixed to the shaft 60, and the first disk part 41 and the second disk part 42 are connected by a plurality of support shafts (not shown) to form the carrier 40 in a bowl shape. .

  The continuously variable transmission 1 is provided with guide portions 43 and 44 for guiding the support shaft 51 in the tilt direction when each planetary ball 50 tilts. In this example, the guide portions 43 and 44 are provided on the carrier 40. The guide portions 43 and 44 are radial guide grooves that guide the support shaft 51 protruding from the planetary ball 50 in the tilt direction, and the first and second disk portions 41 and 42 face each other. A portion is formed for each planetary ball 50 (FIG. 2). That is, all the guide portions 43 and 44 are radially formed when viewed in the axial direction from the planetary ball 50 side. FIG. 2 is a view of the first and second disk portions 41 and 42 as viewed in the axial direction from the planetary ball 50 side.

  In this continuously variable transmission 1, when the tilt angle of each 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 the rotation speed or the number of rotations) of the first rotation member 10 with respect to the second rotation member 20 is 1, and the speed ratio γ is 1. On the other hand, when each planetary ball 50 is tilted from the reference position, the distance from the central axis (second central axis R2) of the support shaft 51 to the contact point with the first rotating member 10 changes, The distance from the central axis of the support shaft 51 to the contact point with the second rotating member 20 changes. Therefore, one of the first rotating member 10 and the second rotating member 20 rotates at a higher speed than when it is at the reference position, and the other rotates at a lower speed. 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 the continuously variable transmission 1, the rotation ratio (gear ratio γ) of the first rotating member 10 with respect to the second rotating member 20 can be changed steplessly by changing the tilt angle. When the speed is increased (γ <1), the upper planetary ball 50 in FIG. 1 is tilted counterclockwise on the paper and the lower planetary ball 50 is tilted clockwise on the paper. . 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 is provided with a transmission that changes its speed ratio γ. Since the gear ratio γ changes as the tilt angle of the planetary ball 50 changes, a tilting device that tilts each planetary ball 50 is used as the speed change device. Here, the transmission is provided with a disk-shaped iris plate (tilting element) 80.

  The iris plate 80 is attached to the shaft 60 via, for example, a radially inner bearing, and can rotate relative to the shaft 60 about the first central axis R1. An actuator (drive unit) such as a motor (not shown) is used for the relative rotation. The driving force of this driving portion is transmitted to the outer peripheral portion of the iris plate 80 via the worm gear 81 shown in FIG.

  The iris plate 80 is on the input side (contact portion side with the first rotating member 10) or the output side (contact portion side with the second rotating member 20) of each planetary ball 50 and on the outside or inside of the carrier 40. Deploy. In this example, it is arranged on the output side and inside the carrier 40, that is, between the sun roller 30 and each planetary ball 50 and the second disk portion 42. The iris plate 80 is formed with a throttle hole (iris hole) 82 into which one protrusion of the support shaft 51 is inserted. If the radial direction of the starting point is assumed to be the reference line L, the throttle hole 82 has an arc shape that moves away from the reference line L in the circumferential direction from the radially inner side to the radially outer side. (Fig. 3). FIG. 3 shows the iris plate 80 viewed from the planetary ball 50 side in the axial direction.

  One protrusion of the support shaft 51 moves to the center side of the iris plate 80 along the aperture 82 as the iris plate 80 rotates in the clockwise direction in FIG. At this time, since the respective protruding portions of the support shaft 51 are inserted into the guide portions 43 and 44 of the carrier 40, one of the protruding portions inserted into the throttle hole 82 moves radially inward. Further, one of the protrusions moves to the outer peripheral side of the iris plate 80 along the aperture hole 82 when the iris plate 80 rotates counterclockwise in FIG. At this time, the one projecting portion moves outward in the radial direction by the action of the guide portions 43 and 44. As described above, the support shaft 51 can be moved in the radial direction by the guide portions 43 and 44 and the throttle hole 82. Therefore, the planetary ball 50 can be tilted as described above.

  The continuously variable transmission 1 configured as described above transmits torque between the first and second rotating members 10 and 20 and the sun roller 30 and each planetary ball 50 via an oil film of lubricating oil. The lubricating oil is supplied by, for example, scooping up the first and second rotating members 10 and 20 described above. In the continuously variable transmission 1, the continuously variable transmission 1 is also supplied through an oil passage formed inside the shaft 60.

  Here, the shaft 60 is formed with an axial oil passage 61 formed in the axial direction. Lubricating oil pumped from the oil pump 91 is supplied to the axial oil passage 61. The shaft 60 is formed with at least one radial oil passage 62 that supplies the lubricating oil in the axial oil passage 61 to the inside in the radial direction of the sun roller 30. The radial oil passage 62 is an oil passage formed in the radial direction that allows the axial oil passage 61 and the outer peripheral surface side of the shaft 60 to communicate with each other. The outer peripheral surface, the inner peripheral surface of the sun roller 30, and the radial bearings RB1, It opens to the annular space S formed by the side surface of RB2. Lubricating oil in the space S is supplied between the inner and outer rings of the radial bearings RB1 and RB2, and is supplied to the outside of the space S through the inner and outer rings. Then, the lubricating oil discharged to the outside of the space S is sent to the planetary ball 50 and the like.

  By the way, the planetary ball 50 rotates relative to the support shaft 51 via the needle bearings NB1 and NB2. Therefore, if the amount of lubricating oil supplied between the planetary ball 50 and the support shaft 51 is small, the durability of the needle bearings NB1 and NB2 may be reduced. As described above, the lubricating oil adhering to the outer peripheral surface of the protruding portion of the support shaft 51 is supplied between the planetary ball 50 and the support shaft 51. Further, an axial oil passage 51a and a radial oil passage 51b for discharging the lubricating oil in the oil passage 51a to the space between the needle bearings NB1 and NB2 are formed inside the support shaft 51. Yes. The oil passage 51 a is opened at one end face of the support shaft 51. In this example, the support shaft 51 is opened at the end surface on the second disk portion 42 side. Therefore, when the lubricating oil is introduced into the oil passage 51a from the opening, the lubricating oil passes between the planetary ball 50 and the support shaft 51 via the radial oil passage 51b and the needle bearings NB1, NB2. Is supplied to the annular space between. The support shaft 51 may be provided with a plurality of combinations of the oil passage 51a and the oil passage 51b. At that time, one of the oil passages 51 a may be opened on the end surface of the support shaft 51 on the first disc portion 41 side, and the other may be opened on the end surface of the support shaft 51 on the second disc portion 42 side.

  As described above, in the continuously variable transmission 1, for example, the lubricating oil discharged to the outside of the space S via the radial bearings RB1 and RB2, the lubricating oil dropped from other members such as the housing, and the like are supported on the support shaft. When adhering to the protruding portion of 51, the lubricating oil is supplied between the planetary ball 50 and the support shaft 51 via the oil passages 51 a and 51 b and / or along the outer peripheral surface of the protruding portion. Therefore, in this continuously variable transmission 1, it is difficult to always supply the lubricating oil to the protruding portion of the support shaft 51, so that it is not always stable between the planetary ball 50 and the support shaft 51 during operation. There is a possibility that the amount of lubricating oil supplied is not always supplied, and the amount of lubricating oil supplied during that time may be insufficient.

  Therefore, the continuously variable transmission 1 is provided with an oil guiding portion that can supply the lubricating oil to the protruding portion of the support shaft 51 from the planetary ball 50. Since there are two protruding portions in one support shaft 51, the oil guiding portion is provided for at least one protruding portion. Further, it is desirable that the oil guiding portion is capable of supplying lubricating oil to the protruding portion regardless of the tilt angle of the planetary ball 50. For this reason, the oil guiding portion is within the tilting range of the planetary ball 50 (between the speed reduction ratio of maximum deceleration and the speed ratio of maximum speed increase). The lubricating oil existing radially inside is guided toward the radially outer side than the protruding portion, and the lubricating oil guided to the radially outer side is further guided toward the protruding portion. .

  Here, as the lubricating oil present radially inward from the protruding portion of the support shaft 51, when the protruding portion is located at the most radially inner side, the lubricating oil is present further radially inward than this. The lubricating oil in the space S is used. For this reason, at least one oil guide path 31 that guides the lubricating oil in the space S to the outside in the radial direction from the space S is formed inside the sun roller 30. The oil guide path 31 has an oil introduction path 31a that is open to the space S (FIG. 4). The oil introduction path 31 a is an oil path formed in the radial direction at the central portion in the axial direction of the sun roller 30, for example. The oil guide path 31 includes first and second oil guide paths 31b and 31c that allow the oil introduction path 31a and the side wall surface of the sun roller 30 to communicate with each other. The first oil guide path 31 b is an oil path that is inclined radially outward and toward the first disk portion 41 of the carrier 40. On the other hand, the second oil guide path 31 c is an oil path that is inclined radially outward and toward the second disk portion 42 of the carrier 40. Accordingly, the lubricating oil in the space S is introduced into the oil introduction path 31a, and is discharged out of the sun roller 30 via the first oil guide path 31b and the second oil guide path 31c by the centrifugal force accompanying the rotation of the sun roller 30. The

  The oil guide part has oil guide walls 45 and 46 provided in the carrier 40 in addition to the oil guide path 31. The oil guide wall 45 and the oil guide wall 46 are formed in the first disk part 41 and the second disk part 42 of the carrier 40, respectively.

  The oil guide wall 45 has an inclined wall surface 45a to which the lubricating oil discharged from the first oil guide path 31b is sprayed, and a radially outer portion of the inclined wall surface 45a is directed radially outward from a protruding portion of the support shaft 51. And an arcuate wall surface 45b extending (FIGS. 2 and 4). The inclined wall surface 45a is formed such that the inclination angle with respect to the axial direction is equal to or greater than the inclination angle with respect to the axial direction of the first oil guide path 31b, and the lubricating oil discharged from the first oil guide path 31b I am trying to be sprayed. When setting the inclination angle, the inclination angle of the inclined wall surface 45a may be determined based on the inclination angle of the first oil guide path 31b, or vice versa. Here, they are formed at the same inclination angle φ1. The inclined wall surface 45a guides the lubricating oil to the arcuate wall surface 45b. The arcuate wall surface 45 b is a wall surface that guides the lubricating oil sent from the inclined wall surface 45 a toward the radially outer side from the protruding portion of the support shaft 51 regardless of the tilt angle of the planetary ball 50. In this oil guide wall 45, the inclination angle of the inclined wall surface 45a is made to coincide with the tangent of the arc in the radially inner portion of the arc-shaped wall surface 45b in order to facilitate the flow of lubricating oil from the inclined wall surface 45a to the arc-shaped wall surface 45b. Is desirable.

  The oil guide wall 45 further has a rebound wall surface 45c. The rebound wall surface 45c is a wall surface for preventing the lubricating oil guided radially outward from the protruding portion of the support shaft 51 along the arc-shaped wall 45b from being sent further outward in the radial direction. It extends toward the planetary ball 50 side from the radially outer portion of the wall surface 45b. The rebound wall surface 45c is formed such that the angle ψ1 of the wall surface with respect to the radial direction is 90 degrees or less. At this time, the rebound wall surface 45c is formed so as not to interfere with the support shaft 51 when the speed ratio γ is the maximum speed increasing ratio. Here, the rebound wall surface 45c is made to correspond to the axial direction. In addition, the rebound wall surface 45c is set to have an end in the extending direction so that the protruding portion of the support shaft 51 exists on the radially inner side of the wall surface in order to adhere the rebounded lubricating oil to the projecting portion of the support shaft 51.

  The oil guide wall 46 is equivalent to the oil guide wall 45, and includes an inclined wall surface 46a to which the lubricating oil discharged from the second oil guide path 31c is sprayed, and a support shaft 51 from a radially outer portion of the inclined wall surface 46a. And an arcuate wall surface 46b extending outward in the radial direction from the protruding portion (FIGS. 2 and 4). The inclined wall surface 46a is formed such that the inclination angle with respect to the axial direction is equal to or greater than the inclination angle with respect to the axial direction of the second oil guiding path 31c, and the lubricating oil discharged from the second oil guiding path 31c is I am trying to be sprayed. When setting the inclination angle, the inclination angle of the inclined wall surface 46a may be determined based on the inclination angle of the second oil guide path 31c, or vice versa. Here, they are formed at the same inclination angle φ2. The inclined wall surface 46a guides the lubricating oil to the arcuate wall surface 46b. The arc-shaped wall surface 46 b is a wall surface that guides the lubricating oil sent from the inclined wall surface 46 a toward the radially outer side from the protruding portion of the support shaft 51 regardless of the tilt angle of the planetary ball 50. In this oil guide wall 46, the inclination angle of the inclined wall surface 46a is made to coincide with the tangent of the arc in the radially inner portion of the arc-shaped wall surface 46b in order to smoothly flow the lubricating oil from the inclined wall surface 46a to the arc-shaped wall surface 46b. Is desirable.

  As with the oil guide wall 45, the oil guide wall 46 also has a rebound wall surface 46c. The rebound wall surface 46c is a wall surface for preventing the lubricating oil guided radially outward from the protruding portion of the support shaft 51 along the arc-shaped wall 46b from being sent further outward in the radial direction. The wall 46b extends from the radially outer portion toward the planetary ball 50. The rebound wall surface 46c is formed such that the angle ψ2 of the wall surface with respect to the radial direction is 90 degrees or less. At this time, the rebound wall surface 46c is formed so as not to interfere with the support shaft 51 when the speed ratio γ is the maximum reduction ratio. Here, the rebound wall surface 46c is made to correspond to the axial direction. Further, the rebound wall surface 46c is set to have an end in the extending direction so that the protruding portion of the support shaft 51 exists on the radially inner side of the wall surface in order to adhere the rebounded lubricating oil to the projecting portion of the support shaft 51.

  When the oil guide walls 45 and 46 have the same function as the guide parts 43 and 44 in members other than the first and second disk parts 41 and 42, the oil guide walls 45 and 46 are exclusively used for guiding the lubricating oil. You may form in the 1st and 2nd disk parts 41 and 42. FIG. However, in this example, oil guide walls 45 and 46 are provided in the guide portions 43 and 44, respectively. Here, the groove bottoms of the guide portions 43, 44 along which the end surface of the protruding portion of the support shaft 51 moves during tilting are used as arcuate wall surfaces 45b, 46b, and inclined wall surfaces 45a, 46a and bounce wall surfaces 45c and 46c are arranged. In other words, in this example, the inclined wall surfaces 45a and 46a and the arcuate wall surfaces 45b and 46b are formed as the groove bottoms of the guide portions 43 and 44, and the rebound wall surfaces 45c and 46c are the groove bottoms of the guide portions 43 and 44, respectively. It is formed as a groove wall surface erected from. Therefore, the oil guide path 31 is formed radially according to the number of the guide portions 43 and 44.

  Here, the illustrated carrier 40 is a rotating element that cannot rotate relative to the shaft 60 in the circumferential direction. For this reason, in the oil guide walls 45 and 46 disposed on the vehicle upper side with respect to the first central axis R1, the momentum of the lubricating oil when discharged from the first and second oil guide paths 31b and 31c ( Lubricating oil is guided from the inclined wall surfaces 45a and 46a to the arcuate wall surfaces 45b and 46b by the action of the flow velocity). Therefore, it is desirable to set the inclination angles of the first and second oil guide paths 31b and 31c and the inclined wall surfaces 45a and 46a so that the lubricating oil rebounds and is guided to the wall surfaces 45c and 46c. The lubricating oil that has reached the rebound wall surfaces 45c and 46c on the vehicle upper side drops onto the protruding portion of the support shaft 51 and is supplied between the planetary ball 50 and the support shaft 51 through the outer peripheral surface of the protruding portion. . Further, when the speed ratio γ is on the deceleration side (especially at the maximum speed reduction ratio), as shown in FIG. 4, the lubricating oil dripped from the rebound wall surface 46c enters the oil path 51a. Lubricating oil is also supplied between the planetary ball 50 and the support shaft 51.

  On the other hand, in the oil guide walls 45 and 46 arranged on the vehicle lower side than the first central axis R1, the momentum (flow velocity) of the lubricating oil when discharged from the first and second oil guide paths 31b and 31c. ) And gravity, the lubricating oil is guided from the inclined wall surfaces 45a and 46a to the arcuate wall surfaces 45b and 46b. At the time of the induction, a part of the lubricating oil drops on the protruding portion of the support shaft 51 by gravity before reaching the rebounding wall surfaces 45c and 46c. If the gear ratio γ is on the speed increasing side, the lubricating oil in the protruding portion is supplied between the planetary ball 50 and the support shaft 51 along the outer peripheral surface of the protruding portion, and the gear ratio γ is on the speed reducing side. For example, when a shift to the speed increasing side is performed, the gear is supplied between the planetary ball 50 and the support shaft 51 along the outer peripheral surface of the protruding portion. Further, when the gear ratio γ is on the speed increasing side (particularly at the maximum speed increasing ratio), a part of the lubricating oil may enter the oil path 51a, so that the planetary ball 50 via the oil path 51b and Lubricating oil is also supplied to and from the support shaft 51.

  Incidentally, an iris plate 80 is interposed between the second oil guide path 31 c and the oil guide wall 46. Therefore, there is a possibility that the lubricating oil discharged from the second oil guide path 31c cannot reach the oil guide wall 46 by the iris plate 80. Therefore, the iris plate 80 has an extension line on the oil guide wall 46 side in the second oil guide path 31c (that is, on the lubricating oil movement path between the second oil guide path 31c and the oil guide wall 46). A through hole 83 is formed. The through-hole 83 is desirably formed larger than the opening shape (here, circular) of the second oil guide path 31c in order to reduce the amount of lubricating oil adhering from the second oil guide path 31c to the iris plate 80 ( FIG. 3). Further, it is desirable that the through hole 83 is inclined at an inclination angle φ2 equivalent to that of the second oil guiding path 31c and the oil guiding wall 46 (FIG. 4).

  Here, the through hole 83 is preferably extended in the circumferential direction in order to supply the lubricating oil discharged from the second oil guide path 31c to the oil guide wall 46 regardless of the speed ratio γ. However, in order to enable supply at all speed ratios γ, the circumferential length of the through hole 83 is required to be at least a length corresponding to the tilting range of the planetary ball 50, and in the circumferential direction. Since there is a possibility that the interval between the adjacent through holes 83 is narrowed, the strength of the second disk portion 42 may be reduced. For this reason, for example, the through holes 83 adjacent in the circumferential direction may be shifted in the radial direction as shown in FIG. In this case, the second oil guide path 31c and the inclined wall surface 46a are also arranged so as to be shifted from each other in the circumferential direction in the radial direction. Thus, the lubricating oil discharged from the second oil guide path 31c at any speed ratio γ can be supplied to the oil guide wall 46 while suppressing the strength reduction of the second disk portion 42. FIG. 2 shows an inclined wall surface 46a that is not shifted in the radial direction.

  As described above, in the continuously variable transmission 1 of the present embodiment, the oil guide path 31 that discharges the lubricating oil in the sun roller 30 by the centrifugal force associated with the rotation of the sun roller 30 and the discharged lubricating oil. An oil guide portion including oil guide walls 45 and 46 that lead to the protruding portion of the support shaft 51 is provided. That is, the oil guiding portion can supply the lubricating oil to the protruding portion of the support shaft 51 in the continuously variable transmission 1 during operation regardless of the operation state such as the gear ratio γ. For this reason, in this continuously variable transmission 1, since a stable amount of lubricating oil is supplied between the planetary ball 50 and the support shaft 51 during operation, a shortage of the amount of lubricating oil supplied between them is avoided. can do. Therefore, in this continuously variable transmission 1, the durability of the bearings (the needle bearings NB1, NB2 in this example) between the planetary ball 50 and the support shaft 51 can be improved.

  In this example, the carrier 40 is a fixed element with respect to the shaft 60. However, the carrier 40 may be a rotating element that performs relative rotation with respect to the shaft 60 about the first central axis R1. In this case, since the planetary ball 50 and the support shaft 51 revolve around the first central axis R1, the supply form of the lubricating oil by the oil guide portion depends on the position of the support shaft 51 and the oil guide portion when mounted on the vehicle. Change. That is, when the support shaft 51 and the oil guiding portion are present on the vehicle upper side with respect to the first central axis R1, the oil guiding walls 45 and 46 described above are disposed on the vehicle upper side with respect to the first central axis R1. It becomes a supply form in a state. On the other hand, when the support shaft 51 and the oil guiding portion are present on the vehicle lower side with respect to the first central axis R1, the oil guiding walls 45 and 46 described above are disposed on the vehicle lower side with respect to the first central axis R1. It becomes a supply form in a state. Also in this case, the continuously variable transmission 1 avoids an insufficient supply amount of lubricating oil between the planetary ball 50 and the support shaft 51 during operation, as in the case where the carrier 40 is a fixed element. Can do.

  Here, when the carrier 40 is a rotating element, relative rotation also occurs between the carrier 40 and the iris plate 80. For this reason, the lubricating oil discharged from the second oil guide path 31c has a through hole even though the circumferential length of the through hole 83 of the iris plate 80 is shorter than the length corresponding to the tilting range of the planetary ball 50. 83, and can reach the oil guide wall 46. Therefore, in the case where the carrier 40 is a rotating element, it is not necessary to provide a radial shift such as the through holes 83 adjacent in the circumferential direction described above. In this case, since it is difficult to determine which oil guide wall 46 the lubricating oil discharged from a certain second oil guide path 31c is sent to, it is not provided with such a radial deviation. Thus, the supply of the lubricating oil from the second oil guide path 31c to the oil guide wall 46 can be ensured.

[Modification 1]
In the above-described continuously variable transmission 1 according to the first embodiment, the rebound wall surfaces 45c and 46c are parallel to the axial direction. In this modification, in the continuously variable transmission 1 according to the first embodiment, the dropping position of the lubricating oil from the rebound wall surface is predetermined.

  In the continuously variable transmission 1, the lubricant oil is supplied between the planetary ball 50 and the support shaft 51 along the outer peripheral surface of the protruding portion of the support shaft 51 and the oil passages 51 a and 51 b. It is roughly divided into things. In this continuously variable transmission 1, the movement path of the lubricating oil on the outer peripheral surface of the protruding portion varies depending on the tilt angle of the planetary ball 50, so that the planetary ball 50 and the planetary ball 50 are supplied by supplying the lubricating oil via the oil passages 51 a and 51 b. It is desirable to stabilize the supply of lubricating oil to and from the support shaft 51.

  Therefore, in this modified example, in the continuously variable transmission 1 according to the first embodiment, when the opening of the oil passage 51a is closest, the oil is guided so as to be dripped into the opening or the vicinity of the opening in the support shaft 51. Parts. Specifically, as shown in FIG. 5, the carrier 40 in which a part of the oil guiding portion is formed is replaced with a carrier 140.

  The carrier 140 has first and second disk parts 141 and 142 similar to the carrier 40, and the first and second disk parts 141 and 142 have guide parts 143 equivalent to the guide parts 43 and 44, respectively. , 144 are formed. The carrier 140 is formed with oil guiding walls 145 and 146 of the oil guiding portion. In this modification as well, the oil guide walls 145 and 146 are formed on the first and second disk portions 141 and 142 as a part of the guide portions 143 and 144, but the guide portions 143 and 144 are different from each other. You may form as another thing.

  The oil guide walls 145 and 146 of this modification have inclined wall surfaces 145a and 146a and arcuate wall surfaces 145b and 146b similar to the oil guide walls 45 and 46, respectively. Therefore, the lubricating oil discharged from the first oil guiding path 31b and the second oil guiding path 31c is blown onto the inclined wall surfaces 145a and 146a, and then is sent radially outward along the arcuate wall surfaces 145b and 146b.

  On the other hand, the oil guide walls 145, 146 of this modified example have rebound wall surfaces 145c, 146c parallel to the axial direction similar to the oil guide walls 45, 46, but the extended lengths L1, L2 are dripping of the lubricating oil. It is defined according to the position. The exemplary extension length L1 is set so as to define the dripping position of the lubricating oil on the outer peripheral surface of the protruding portion of the support shaft 51. On the other hand, since the extension length L2 is on the side where the oil guide wall 146 has the opening of the oil passage 51a, when the opening rebounds and comes closest to the wall surface 146c, the lubricating oil can be opened. It sets so that it may be dripped at the vicinity of the said opening in the support shaft 51. FIG. For example, as shown in FIG. 5, the extended lengths L1 and L2 are based on the end surface of the support shaft 51 when the gear ratio γ = 1 (the tilt angle of the planetary ball 50 is 0 degree), and the end surfaces rebound. The distance in the axial direction to the target dropping position on the support shaft 51 when the wall surfaces 145c and 146c are closest.

  Further, return wall surfaces 145d and 146d are formed on the oil guide walls 145 and 146 to guide the lubricating oil on the rebound wall surfaces 145c and 146c to the target dropping position. The return wall surfaces 145d and 146d are wall surfaces extending radially inward from the ends of the extended lengths L1 and L2 of the rebound wall surfaces 145c and 146c. Therefore, the lubricating oil that has reached the rebound wall surfaces 145c, 146c is present on the vehicle upper side when the support shaft 51 and the oil guide walls 145, 146 are present on the vehicle upper side with respect to the first central axis R1. , And supplied to the target dropping position on the support shaft 51 along the return wall surfaces 145d and 146d. In addition, with respect to the support shaft 51 which exists in another position, lubricating oil is sent to a protrusion part with the supply form similar to the continuously variable transmission 1 of Example 1. FIG.

  Thus, in the continuously variable transmission 1 of this modification, in addition to the lubricating oil supply form similar to that of the first embodiment, if the support shaft 51 and the like are present on the vehicle upper side, the return wall surface 145d, Lubricating oil can also be supplied to the target dropping position via 146d. Therefore, the continuously variable transmission 1 of this modification can secure a supply amount of lubricating oil equal to or greater than that of the first embodiment between the planetary ball 50 and the support shaft 51. Further, when the carrier 140 is a rotating element, the lubricating oil can be supplied to the target dropping position with respect to the protruding portions of all the support shafts 51 that have reached the upper side of the vehicle. Oil can be supplied between the planetary ball 50 and the support shaft 51.

[Modification 2]
This modified example is a continuously variable transmission 1 of the above modified example 1 in which the return wall surfaces 145d and 146d are formed of separate members from the first and second disk portions 141 and 142, as shown in FIG. In addition, the carrier 140 is replaced with the carrier 240, and annular members 247 and 248 having return wall surfaces 247a and 248a are newly provided.

  The carrier 240 has first and second disk parts 241 and 242 similar to the carrier 140, and the first and second disk parts 241 and 242 have guide parts 243 equivalent to the guide parts 143 and 144, respectively. , 244 are formed. The carrier 240 is formed with oil guiding walls 245 and 246 of the oil guiding portion. In this modified example, the oil guide walls 245 and 246 are formed on the first and second disk parts 241 and 242 as a part of the guide parts 243 and 244. You may form as another thing.

  The oil guide walls 245 and 246 of this modification have inclined wall surfaces 245a and 246a and arcuate wall surfaces 245b and 246b similar to the oil guide walls 145 and 146, respectively. Therefore, the lubricating oil discharged from the first oil guiding path 31b and the second oil guiding path 31c is blown to the inclined wall surfaces 245a and 246a and then sent radially outward along the arcuate wall surfaces 245b and 246b. Further, the oil guide walls 245 and 246 have rebound wall surfaces 245c and 246c having extended lengths L1 and L2 set in the same manner as in the first modification.

  The annular members 247 and 248 are annular members whose central axes coincide with the first central axis R1, and are fixed to the end surfaces of the extended lengths L1 and L2 of the rebound wall surfaces 245c and 246c by welding or the like, for example. The return wall surfaces 247a and 248a are the same as the return wall surfaces 145d and 146d of Modification 1, and are annular surfaces that are present on the radially inner side of the rebound wall surfaces 245c and 246c in the annular members 247 and 248 after being fixed. Consisting of a part of.

  The continuously variable transmission 1 of this modified example is configured by separate members as described above, so that not only the same effect as that of the modified example 1 is obtained, but also the return wall surfaces 247a and 248a are easier to form than the modified example 1. . Therefore, the continuously variable transmission 1 of this modification can construct the same effect as that of the modification 1 with a structure with good manufacturability, compared to the modification 1.

[Modification 3]
In this modified example, in the continuously variable transmission 1 of the first embodiment, the angles ψ1, ψ2 with respect to the radial direction of the rebound wall surfaces 45c, 46c are made smaller than 90 degrees. Here, such a rebound wall surface having a narrow angle with respect to the radial direction is less manufacturable than that formed at 90 degrees with respect to the radial direction. For this reason, in this modification, in the continuously variable transmission 1 of the first embodiment, the rebound wall surface is configured by a member different from the first and second disk portions 41 and 42. Specifically, as shown in FIG. 7, the carrier 40 in which a part of the oil guiding portion is formed is replaced with the carrier 340, and cylindrical members 347 and 348 having rebound wall surfaces 347a and 348a are newly provided.

  The carrier 340 includes first and second disk parts 341 and 342 similar to the carrier 40, and guide parts 343 equivalent to the guide parts 43 and 44 are provided in the first and second disk parts 341 and 342, respectively. , 344 are formed. The carrier 340 is formed with oil guide walls 345 and 346 of the oil guide portion. In this modification as well, the oil guide walls 345 and 346 are formed on the first and second disk parts 341 and 342 as a part of the guide parts 343 and 344, but the guide parts 343 and 344 are different from each other. You may form as another thing.

  The oil guide walls 345 and 346 of this modification have inclined wall surfaces 345a and 346a similar to the oil guide walls 45 and 46, and arc-shaped wall surfaces 345b and 346b. Accordingly, the lubricating oil discharged from the first oil guiding path 31b and the second oil guiding path 31c is blown onto the inclined wall surfaces 345a and 346a, and then sent radially outward along the arcuate wall surfaces 345b and 346b.

  As described above, in this modification, the rebound wall surfaces 347a and 348a which are part of the oil guide walls 345 and 346 are cylindrical members 347 and 348 different from the first and second disk portions 341 and 342, respectively. It is constituted by. The cylindrical members 347 and 348 have the center axis aligned with the first center axis R1, and the inner peripheral surfaces are fixed to the outer peripheral surfaces of the first and second disk portions 341 and 342. As the fixing method, welding, caulking, press fitting, or the like can be considered. On the inner peripheral surface after the cylindrical members 347 and 348 are fixed, there is a portion extending to the planetary ball 50 side from the most radially outer portion of the arc-shaped wall surfaces 345b and 346b. In these cylindrical members 347 and 348, the extended part of the inner peripheral surface rebounds to become wall surfaces 347a and 348a. Therefore, the lubricating oil that has bounced back from the arc-shaped wall surfaces 345b and 346b and reached the wall surfaces 347a and 348a is located above the vehicle when the support shaft 51 and the oil guide walls 345 and 346 are present above the first central axis R1. As it is present on the side, it drops from the rebound wall surfaces 347a and 348a onto the protruding portion of the support shaft 51. In addition, with respect to the support shaft 51 which exists in another position, lubricating oil is sent to a protrusion part with the supply form similar to the continuously variable transmission 1 of Example 1. FIG.

  Thus, in the continuously variable transmission 1 of this modification, the rebound wall surfaces 347a and 348a are formed simply by inserting and fixing the first and second disk portions 341 and 342 to the cylindrical members 347 and 348. can do. Therefore, the continuously variable transmission 1 of this modification can not only obtain the same effect as that of the first embodiment, but also can construct the effect with a structure with good manufacturability.

  In the continuously variable transmission 1 of this modified example, the extended lengths of the rebound wall surfaces 347a and 348a are set as in the modified example 2, and the lubricating oil can be supplied to the target dropping position on the support shaft 51. You may comprise as follows.

[Modification 4]
In the continuously variable transmission 1 of the first embodiment described above, since the oil guide walls 45 and 46 are provided in the guide portions 43 and 44, in order to guide the support shaft 51 along the guide portions 43 and 44, The width in the circumferential direction of the oil guide walls 45 and 46 is matched to the groove width in the circumferential direction of the guide portions 43 and 44. For this reason, the width in the circumferential direction of the inclined wall surfaces 45a, 46a is also equal to the groove width of the guide portions 43, 44.

  Therefore, in this modification, the circumferential width of the inclined wall surfaces 45a and 46a is expanded in the continuously variable transmission 1 of the first embodiment, and the lubricating oil discharged from the first and second oil guiding paths 31b and 31c is used. The oil guide walls 45 and 46 are easily introduced. Specifically, as shown in FIG. 8, the carrier 40 in which a part of the oil guiding portion is formed is replaced with a carrier 440.

  The carrier 440 includes first and second disk portions 441 and 442 similar to those of the carrier 40, and guide portions 443 equivalent to the guide portions 43 and 44 are provided on the first and second disk portions 441 and 442, respectively. , 444 are formed. The carrier 440 is formed with oil guiding walls 445 and 446 of the oil guiding portion. In this modified example, the oil guide walls 445 and 446 are formed on the first and second disk parts 441 and 442 as a part of the guide parts 443 and 444. You may form as another thing.

  The oil guide walls 445 and 446 of this modification have inclined wall surfaces 445a and 446a that are wider in the circumferential direction than the inclined wall surfaces 45a and 46a of the first embodiment. The inclination angle is set in the same manner as the inclined wall surfaces 45a and 46a. On the other hand, the oil guide walls 445 and 446 of this modified example have arcuate wall surfaces 445b and 446b and rebound wall surfaces 445c and 446c similar to the oil guide walls 45 and 46 of the first embodiment. The arc-shaped wall surfaces 445b and 446b have the circumferential width matched to the groove width of the guide portions 443 and 444. Therefore, the illustrated inclined wall surfaces 445a and 446a have the circumferential width of the inlet portion (the portion closest to the opening of the first and second oil guide paths 31b and 31c) of the lubricating oil as the inclined wall surface 45a of the first embodiment. 46a, and the width in the circumferential direction may be narrowed gradually as it approaches the arcuate wall surfaces 445b and 446b.

  In the continuously variable transmission 1 of this modification, the lubricating oil discharged from the first and second oil guiding paths 31b and 31c is more easily introduced into the oil guiding walls 445 and 446 than in the first embodiment. Therefore, the continuously variable transmission 1 of this modification can secure a supply amount of lubricating oil equal to or greater than that of the first embodiment between the planetary ball 50 and the support shaft 51.

  The shapes of the inclined wall surfaces 445a and 446a of this modification are applied to the inclined wall surfaces 145a, 146a, 245a, 246a, 345a, and 346a of the above-described modifications 1 to 3 in order to obtain the same effect as this modification. May be.

1 continuously variable transmission 10 first rotation member (first power transmission element, first rotation element)
20 Second rotating member (second power transmission element, second rotating element)
30 Sunroller (third power transmission element, third rotation element)
31 Oil guiding path 31a Oil introducing path 31b First oil guiding path 31c Second oil guiding path 40, 140, 240, 340, 440 Carrier (fourth power transmission element, fixed element)
41,141,241,341,441 First disc part 42,142,242,342,442 Second disc part 43,44,143,144,243,244,343,344,443,444 Guide part 45,46 , 145, 146, 245, 246, 345, 346, 445, 446 Oil guide walls 45a, 46a, 145a, 146a, 245a, 246a, 345a, 346a, 445a, 446a Inclined wall surfaces 45b, 46b, 145b, 146b, 245b, 246b, 345b, 346b, 445b, 446b Arc-shaped wall surface 45c, 46c, 145c, 146c, 245c, 246c, 347a, 348a, 445c, 446c Rebound wall surface 50 Planetary ball (rolling member)
51 Support shaft 51a, 51b Oil passage 60 Shaft (transmission shaft)
61 Axial oil passage 62 Radial oil passage 80 Iris plate 83 Through hole 91 Oil pump 247, 248 Annular member 145d, 146d, 247a, 248a Return wall surface 347, 348 Tubular member NB1, NB2 Needle bearing R1 First central axis R2 Second central axis S space

Claims (3)

A transmission shaft provided with an oil passage inside which lubricating oil can be supplied toward the outer peripheral surface;
First to fourth power transmission elements having a first central axis common to the central axis of the transmission shaft;
A plurality of rolling members arranged radially on the first central axis and disposed on the outer peripheral surface of the third power transmission element and sandwiched between the first and second power transmission elements arranged to face each other When,
Projection portions from the rolling member for holding the rolling member in a tiltable manner by the fourth power transmission element are provided at both ends, inserted into the rolling member, and centered on the second central axis. A support shaft that relatively rotates the rolling member;
A transmission that changes a gear ratio between the first power transmission element and the second power transmission element by tilting each of the rolling members;
An oil guiding portion for guiding the lubricating oil discharged from the oil passage of the transmission shaft to the protruding portion of the support shaft;
Have
The continuously variable transmission is characterized in that the oil guide section includes an oil guide wall in the fourth power transmission element through which lubricating oil discharged from an oil passage of the transmission shaft is guided to a protruding portion of the support shaft. .   The oil guide portion is provided with an oil guide path into which the lubricating oil discharged from the oil path of the transmission shaft is introduced and discharges the introduced lubricating oil toward the oil guide wall in the third power transmission element. The continuously variable transmission according to claim 1.   3. The continuously variable transmission according to claim 1, wherein the oil guide wall is provided in a guide portion of the fourth power transmission element that guides a protruding portion of the support shaft when the rolling member is tilted. 4. Machine.

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