JP2014077471A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To supply necessary amount of lubricating oil to a contact part.SOLUTION: A continuously variable transmission includes a shaft 60, first and second rotating members 10, 20, a sun roller 30, a carrier 40, a plurality of planetary balls 50 and tilting force application parts 46 for changing a transmission ratio between input and output by tilting each planetary ball 50. The sun roller 30 includes: a first rotating body 31 having first contact parts P3 with the respective planetary balls 50; a second rotating body 32 enabling circumferential relative rotation to the first rotating body 31 and having second contact parts P4 with the respective planetary balls 50; a clearance S between the first rotating body 31 and the second rotating body 32 to which lubricating oil is supplied; and openings facing contact auxiliary parts of the first and second rotating members 10, 20 with the planetary balls 50 or facing portions near the contact auxiliary portions. Lubrication oil passages 34, 35 for communicating the openings with the clearance S are installed.

Description

  The present invention includes a plurality of power transmission elements having a common rotation center axis and a plurality of rolling members arranged radially with respect to the rotation center axis, and is sandwiched between two of the power transmission elements. Further, the present invention relates to a traction drive type continuously variable transmission that continuously changes the speed ratio between input and output by tilting each rolling member.

  Conventionally, as this type of continuously variable transmission, a transmission shaft serving as a rotation center, a plurality of power transmission elements capable of relative rotation with the central axis of the transmission shaft as a rotation central axis, and the rotation central shaft A ball planetary type is known that includes a plurality of radially arranged rolling members sandwiched between three of the power transmission elements. In this ball planetary continuously variable transmission, each rolling member is sandwiched between a first power transmission element and a second power transmission element arranged to face each other, and each rolling member is a third power transmission element. It is arrange | positioned on the outer peripheral surface. Patent Document 1 below discloses such a ball planetary continuously variable transmission. In the continuously variable transmission of Patent Document 1, an oil passage of a transmission shaft that supplies lubricating oil to an internal space of a sun roller as a third power transmission element, and an axial direction of the internal space and the sun roller (an axial direction of a transmission shaft) ) And an oil passage that communicates with the side surface.

US Patent Application Publication No. 2010/0093480

  By the way, in this type of continuously variable transmission, supply of lubricating oil to each part is required. For example, in the conventional continuously variable transmission, the lubricating oil in the case is scattered by centrifugal force or scraping or dropped by gravity and sent to each part. For this reason, in a conventional continuously variable transmission, a required amount of lubricating oil is not always supplied to a target location. For example, in this type of continuously variable transmission, it is required to supply the lubricating oil to the contact portion between the power transmission element and the rolling member even when generating the traction force, but it is difficult to specify the supply destination of the lubricating oil. Therefore, there is a possibility that an appropriate amount of lubricating oil may not be supplied during that time.

  Accordingly, an object of the present invention is to provide a continuously variable transmission that can improve the disadvantages of the conventional example and can supply a required amount of lubricating oil to the contact portion.

  To achieve the above object, the present invention provides first to fourth powers capable of relative rotation in the circumferential direction between a transmission shaft serving as a rotation center and a first rotation center shaft concentric with the transmission shaft. A first transmission element and a second rotation center axis are arranged on the outer peripheral surface of the third power transmission element in a radial manner around the first rotation center axis and arranged opposite to each other. And a rolling member that is sandwiched between the second power transmission elements and is tiltably held by the fourth power transmission element, and a gear that changes the transmission ratio between the input and output by tilting each of the rolling members. A first rotating body having a first contact portion with each of the rolling members, and the first rotating center axis with respect to the first rotating body. And a second rotation portion having a second contact portion with each of the rolling members. A rolling element, a gap between the first rotating body and the second rotating body to which lubricating oil is supplied, and the rolling member in at least one of the first and second power transmission elements. It has an opening toward the contact spare part or the vicinity of the contact spare part, and includes a lubricating oil passage that communicates the opening with the gap.

  Here, it is desirable that the first rotating body has the opening facing the first power transmission element on an outer peripheral surface.

  In addition, it is desirable that the second rotating body has the opening directed to the second power transmission element on an outer peripheral surface.

  The lubricating oil passage having the opening toward the first power transmission element includes an oil passage of the first rotating body communicating with the gap, and lubricating oil discharged from the oil passage of the first rotating body. An oil passage that guides the opening toward the first power transmission element, and the oil passage having the opening toward the first power transmission element rotates integrally with the first rotating body. It is desirable to form with the groove part of the guide member to do.

  The lubricating oil passage having the opening toward the second power transmission element includes an oil passage of the second rotating body communicating with the gap, and lubricating oil discharged from the oil passage of the second rotating body. An oil passage that guides the opening toward the second power transmission element, and the oil passage having the opening toward the second power transmission element rotates integrally with the second rotating body. It is desirable to form with the groove part of the guide member to do.

  The third power transmission element preferably further includes a lubricating oil passage for supplying lubricating oil in the gap to the first and second contact portions.

  The continuously variable transmission according to the present invention has a third power transmission element with respect to a contact spare portion with the rolling member or in the vicinity of the contact spare portion in at least one of the first and second power transmission elements. Lubricating oil can be directly supplied from the opening of the lubricating oil passage by centrifugal force accompanying rotation. Here, the contact preliminary portion repeats contacting or moving away from the rolling member as the first and second power transmission elements rotate. For this reason, the contact portion between the first power transmission element and the rolling member and the contact portion between the second power transmission element and the rolling member have the lubricating oil adhering to the contact spare portion or the vicinity of the contact spare portion. Sent. Thus, in this continuously variable transmission, the supply destination of the lubricating oil can be specified, so that the required amount of lubricating oil can be supplied to the contact portion.

FIG. 1 is a sectional view showing an example of the configuration of a continuously variable transmission according to the present invention. FIG. 2 is a diagram illustrating one fixed disk portion of the carrier. FIG. 3 is a diagram for explaining the other fixed disk portion and the rotating disk portion of the carrier. FIG. 4 is a diagram illustrating a lubricating oil path of the sun roller in the embodiment. FIG. 5 is a view of the lubricating oil passage of the sun roller in the embodiment as seen from the axial direction. FIG. 6 is a diagram illustrating a guide member that forms a lubricating oil path of the sun roller in the embodiment. FIG. 7 is a diagram illustrating another example of the lubricating oil path of the sun roller in the embodiment. FIG. 8 is a diagram illustrating a lubricating oil path of the sun roller in the first modification. FIG. 9 is a view showing another example of the lubricating oil passage of the sun roller in the first modification. FIG. 10 is a diagram illustrating a lubricating oil path of the sun roller in the second modification. FIG. 11 is a diagram illustrating another example of the lubricating oil path of the sun roller in the second modification. FIG. 12 is a diagram illustrating a lubricating oil path of the sun roller in the third modification. FIG. 13 is a view of the lubricating oil passage of the sun roller in Modification 3 as viewed in the circumferential direction. FIG. 14 is a view of the sun roller in the third modification as viewed from the radial direction.

  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. This continuously variable transmission includes a ball planetary continuously variable transmission mechanism corresponding to a traction planetary mechanism. Reference numeral 1 in FIG. 1 shows an example of a ball planetary continuously variable transmission in the present embodiment.

  The continuously variable transmission mechanism of the present embodiment includes four power transmission elements having a common first rotation center axis R1, a plurality of rolling members arranged radially around the first rotation center axis R1, and 4 And a transmission shaft disposed at the rotation center of the two power transmission elements. The rolling member has a second rotation center axis R2 different from the first rotation center axis R1, and is on a tilt plane including its own second rotation center axis R2 and the first rotation center axis R1. Tilt operation is possible. In the following, unless otherwise specified, the direction along the first rotation center axis R1 is referred to as an axial direction, and the direction around the first rotation center axis R1 is referred to as a circumferential direction. Further, the direction orthogonal to the first rotation center axis R1 is referred to as a radial direction, and among these, the inward side is referred to as a radial inner side, and the outward side is referred to as a radial outer side.

  This continuously variable transmission mechanism clamps each rolling member with three of the four power transmission elements (first to third power transmission elements) and the remaining power transmission elements (fourth power transmission elements). Thus, each rolling member is held to be rotatable and tiltable. Each rolling member is arranged radially about the first rotation center axis R1. And each rolling member is clamped by the 1st and 2nd power transmission element arrange | positioned facing in the axial direction, and is arrange | positioned on the outer peripheral surface of a 3rd power transmission element.

  The continuously variable transmission mechanism can transmit torque via the rolling members between the first to fourth power transmission elements. For example, the continuously variable transmission mechanism generates a traction force (tangential force) between the first to third power transmission elements and each rolling member, so that the first to third power transmission elements Torque (power) can be transmitted through each rolling member. The traction force is generated by pressing at least one of the first and second power transmission elements against each rolling member. Furthermore, in this continuously variable transmission mechanism, torque can be transmitted between the fourth power transmission element and each rolling member by allowing the fourth power transmission element to rotate.

  In this continuously variable transmission mechanism, the second rotation center axis R2 of each rolling member is tilted with respect to the first rotation center axis R1 on the tilt plane, and each rolling member is tilted. The ratio of the rotational speed (number of rotations) between the input and output, that is, the speed ratio γ is changed.

  In this continuously variable transmission mechanism, some of the first to fourth power transmission elements may be used as rotating elements that can rotate relative to the transmission shaft. Some of them are used as fixed elements that cannot rotate relative to the transmission shaft. In the case of the former configuration, any one of the first to fourth power transmission elements serves as a torque input unit, and another one serves as a torque output unit. On the other hand, in the case of the latter configuration, torque is transmitted through the respective rolling members between the three power transmission elements other than the fixed elements, so that any one of the three power transmission elements is A torque input section is provided, and another one is a torque output section. For this reason, in this continuously variable transmission mechanism, the ratio of the rotational speed (number of rotations) between the power transmission element serving as the input unit and the power transmission element serving as the 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 to the power source side such as an engine (engine such as an internal combustion engine) or a rotating machine (electric motor or the like), and the output part is connected to the drive wheel side. Another transmission (for example, a stepped manual transmission or an automatic transmission) may be interposed between the continuously variable transmission 1 and the drive wheel side. In this continuously variable transmission 1, the rotational operation of each power transmission element when torque is input to the power transmission element as an input unit is referred to as positive drive, and when the power transmission element as an output unit is in positive drive. The rotation operation of each power transmission element when reverse direction torque is input is called reverse drive. For example, in the continuously variable transmission 1, according to the example of the preceding vehicle, when torque is input from the power source side to the power transmission element as an input portion and the power transmission element is rotated, such as acceleration. Becomes forward drive, and reverse drive occurs when torque in the direction opposite to that during forward drive is input from the drive wheel side to the rotating power transmission element as the output unit, such as deceleration.

  Here, in the continuously variable transmission 1, the first and second power transmission elements function as a ring gear or the like as in the traction planetary mechanism. The third power transmission element and the fourth power transmission element function as a sun roller and a carrier in the traction planetary mechanism, respectively. The rolling member functions as a ball-type pinion in the traction planetary mechanism. Therefore, the continuously variable transmission 1 includes the first and second rotating members 10 and 20 as the first and second power transmission elements, the sun roller 30 as the third power transmission element, and the fourth power transmission element. A carrier 40, a planetary ball 50 as a rolling member, and a shaft 60 as a transmission shaft. The shaft 60 is fixed to a fixed portion of the continuously variable transmission 1 in a housing or a vehicle body (not shown), and is a columnar or cylindrical fixed shaft configured not to rotate relative to the fixed portion. To do. In the continuously variable transmission 1, the reference position is a state in which the first rotation center axis R1 and the second rotation center axis R2 are parallel to each other on the tilt plane (state in FIG. 1). In addition, although the case where the carrier 40 is used as a fixed element is illustrated here (however, only the rotating disk portion 42 described later is allowed to rotate), the carrier 40 is a rotating element in various oil paths described later. This can also be applied.

  The first and second rotating members 10 and 20 are disk members (disks) or ring members (rings) whose center axes coincide with the first rotation center axis R1, and each planetary ball is opposed in the axial direction. 50 is interposed. In this example, both are circular members.

  The continuously variable transmission 1 has contact portions P1 and P2 in which the first and second rotating members 10 and 20 and the planetary balls 50 are in point contact with each other (strictly, elliptical surface contact). . As will be described in detail later, each planetary ball 50 has an outer peripheral curved surface as a rolling surface, and is sandwiched between the first and second rotating members 10 and 20 on the outer peripheral curved surface. That is, each planetary ball 50 has contact portions P1 and P2 on its outer peripheral curved surface. On the other hand, the first and second rotating members 10 and 20 sandwich the planetary balls 50 from the radially outer side, and have contact portions P1 and P2 on the inner peripheral surfaces 10a and 20a, respectively. In the inner peripheral surfaces 10a and 20a, the contact portions P1 and P2 that are actually in contact with the planetary balls 50 and the contact portions P1 and P2 as the first and second rotating members 10 and 20 rotate. Are connected in the circumferential direction (hereinafter referred to as “contact preliminary portion”). That is, the contact preliminary portion is a portion that repeatedly contacts or leaves the planetary ball 50 as the first and second rotating members 10 and 20 rotate. The shapes of the contact portions P1, P2 and the contact spare portion of the first and second rotating members 10, 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 the curvature of the outer peripheral curved surface thereof. Has a concave arc surface, a convex arc surface, a flat surface or the like having different curvatures. The shapes of the contact portions P1 and P2 and the contact preliminary portion of the first and second rotating members 10 and 20 are axial forces from the first and second rotating members 10 and 20 toward the planetary ball 50. When a (pressing force) is applied, a force (normal force) in a radially inner side and an oblique direction is applied to the planetary ball 50.

  Here, in the state of the reference position, the first and second rotating members 10 and 20 are set such that the distances from the second rotation center axis R2 to the contact portions P1 and P2 and the contact preliminary portions are the same length. The inner peripheral surfaces 10a and 20a and the outer peripheral curved surface of each planetary ball 50 are formed. Further, here, the inner circumferences of the first and second rotating members 10 and 20 are set so that the contact angles θ of the first and second rotating members 10 and 20 and the planetary balls 50 are the same. The outer peripheral curved surfaces of the surfaces 10a and 20a and each planetary ball 50 are formed. The contact angle θ is a line connecting the contact portions P1 and P2 or the contact spare portion with respect to the reference plane and the center of the planetary ball 50 (rotation center and tilt center, which corresponds to the center of gravity in the case of a sphere). It is an angle. The reference plane is a plane extending in the radial direction having the center of each planetary ball 50.

  In this example, the first rotating member 10 is used as a torque input unit during positive driving, and the second rotating member 20 is used as a torque output unit during positive driving. 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 in the axial direction 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 the engaging member on the input shaft 11 side and the engaging portion or the 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, the continuously variable transmission 1 is also provided with an axial force generator 72 between the output shaft 21 and the second rotating member 20. The axial force generating unit 72 generates axial pressing force (axial force) for pressing the second rotating member 20 against each planetary ball 50, and a torque cam similar to the axial force generating unit 71 is used. The axial force generator 72 is connected to the output shaft 21 via the annular member 22.

  The continuously variable transmission 1 has an axial force between the first rotating member 10 and each planetary ball 50, between the second rotating member 20 and each planetary ball 50, and between the sun roller 30 and each planetary ball 50. In the meantime, traction force can be generated during operation.

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

  The sun roller 30 of the present embodiment is such that the contact portions with each planetary ball 50 are dispersed in two locations (first contact portion P3 and second contact portion P4) in the axial direction. The reason is that by reducing the contact pressure by dispersing the contact force between the sun roller 30 and the planetary ball 50, the spin loss can be reduced, the decrease in power transmission efficiency can be suppressed, and the durability can be improved. is there. The first contact portion P3 is provided on one of the axial directions around the reference plane. On the other hand, the 2nd contact part P4 is provided in the other of the axial direction centering on the reference plane. The first and second contact portions P3, P4 have the same distance from the center of each planetary ball 50 (the center of rotation and the tilt, which is equivalent to the center of gravity in the case of a sphere), and The distance from the first rotation center axis R1 is also set at the same position. In the first and second contact portions P3 and P4, the sun roller 30 and each planetary ball 50 are in point contact (strictly surface contact) with each other.

  The sun roller 30 is divided into two rotating bodies (a first rotating body 31 and a second rotating body 32) capable of rotating in the circumferential direction with respect to the shaft 60, and a first contact portion P3 is provided on the first rotating body 31. At the same time, a second contact portion P4 is provided on the second rotating body 32. This is because the loss energy between the sun roller 30 and the planetary ball 50 is reduced by rotating the first and second rotating bodies 31 and 32 relative to each other in the circumferential direction, thereby suppressing reduction in power transmission efficiency. Because it can.

  In the sun roller 30, the first rotating body 31 is disposed on one side in the axial direction centering on the reference plane, and the second rotating body 32 is disposed on the other side in the axial direction centering on the reference plane. The first and second rotating bodies 31 and 32 are attached to the shaft 60 via angular bearings AB and radial bearings RB, respectively, so that relative rotation in the circumferential direction with respect to the shaft 60 can be performed.

  In the first contact portion P <b> 3, an oblique pressing force is applied from the first rotating body 31 to the planetary ball 50 in the axial direction on the second rotating body 32 side and radially outward. On the other hand, in the second contact portion P4, a pressing force in an oblique direction is applied to the planetary ball 50 from the second rotating body 32 in the axial direction on the first rotating body 31 side and radially outward. For this reason, the sun roller 30 has a conical portion in which the outer diameter is uniformly reduced as it approaches the second rotating body 32, and the outer diameter is equalized as it approaches the first rotating body 31. The 2nd rotary body 32 has a cone part which becomes small. The 1st contact part P3 and the 2nd contact part P4 are provided on the outer peripheral surface of each cone part. Moreover, you may substitute the cone part for the 1st rotary body 31 and the 2nd rotary body 32 to an arc-shaped cone part. The arc-shaped cone portion has a shape in which the outer diameter decreases in a parabolic shape as the other rotating body is approached. The 1st contact part P3 and the 2nd contact part P4 are provided on the outer peripheral surface of each arcuate cone part. The cone part and the arcuate cone part are formed on all or part of the outer peripheral surfaces of the first rotating body 31 and the second rotating body 32.

  The planetary ball 50 is a rolling member that rolls on the outer peripheral surface of the sun roller 30 around the support shaft 51. 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 support shaft 51 is penetrated through the center of the planetary ball 50 and supports the planetary ball 50 rotatably. For example, the planetary ball 50 can rotate relative to the support shaft 51 around the second rotation center axis R2 (that is, rotate) by a bearing such as a needle bearing disposed between the outer periphery of the support shaft 51 and the like. Both ends of the support shaft 51 are projected from the planetary ball 50.

  The reference position of the support shaft 51 is the reference position shown in FIG. 1 described above, and is the position where the second rotation center axis R2 is parallel to the first rotation center axis R1. The support shaft 51 can swing (tilt) together with the planetary ball 50 between a reference position and a position tilted therefrom in the tilt plane. The tilt is performed with the center of the planetary ball 50 as a fulcrum in the tilt plane.

  The carrier 40 supports each projecting portion of the support shaft 51 so as not to prevent the tilting motion of each planetary ball 50. The carrier 40 includes, for example, first to third disk portions 41, 42, and 43 that are arranged such that the center axis coincides with the first rotation center axis R1 and is opposed to each other in the axial direction. In the carrier 40, the first disk part 41 and the second disk part 42 are arranged with an interval in the axial direction, and the third disk part 43 is arranged close to one of them. In the carrier 40, the sun roller 30 and the planetary ball 50 are disposed between the two disk parts of the first to third disk parts 41, 42, and 43. In this illustration, the third disk part 43 is arranged between the first disk part 41 and the second disk part 42 and close to the second disk part 42, and the first disk part 41 and the third disk part 42 are arranged. The sun roller 30 and the planetary ball 50 are arranged between In the carrier 40, the third disk portion 43 is not necessarily provided.

  In the carrier 40, one of the first and second disk portions 41, 42 is configured to be capable of relative rotation in the circumferential direction with respect to the shaft 60, and the other of the first and second disk portions 41, 42 is configured in the circumferential direction with respect to the shaft 60. Configure to prevent relative rotation. Further, the third disk portion 43 is configured so as not to be able to rotate relative to the shaft 60 in the circumferential direction. In this example, it is assumed that the first and third disk portions 41 and 43 cannot be rotated relative to the shaft 60, and the second disk portion 42 can be rotated relative to the shaft 60. The first disk portion 41 has an inner diameter side fixed to the outer diameter side of the shaft 60 with, for example, a screw member. The second disk portion 42 is attached on the inner diameter side to the outer diameter side of the shaft 60 via a bearing (not shown). The third disk part 43 is connected to the first disk part 41 by, for example, a plurality of support shafts (not shown). The first disk part 41 and the third disk part 43 have a bowl shape, and a part of the planetary ball 50 protrudes from the gap between the support shafts. The first and second rotating members 10 and 20 are in contact with the protruding portion of the planetary ball 50. Hereinafter, the first disk portion 41 is referred to as a first fixed disk portion 41, the second disk portion 42 is referred to as a rotating disk portion 42, and the third disk portion 43 is referred to as a second fixed disk portion 43.

  Here, in the 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). Rotation speed). 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 center axis of the support shaft 51 (second rotation center axis R2) to the contact portion P1 with the first rotation member 10 changes. At the same time, the distance from the central axis of the support shaft 51 to the contact portion P2 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 carrier 40 is provided with a function as a tilting device (transmission device).

  First, the first and second fixed disk portions 41 and 43 are provided with radial guide portions 44 and 45 for each planetary ball 50. The radial guide portions 44 and 45 are guide portions that guide the end portion in the radial direction when a tilting force is applied to the end portion of the support shaft 51 protruding from the planetary ball 50. . The radial guide portion 44 is, for example, a guide groove or a guide hole whose longitudinal direction is the radial direction (FIG. 2). On the other hand, the radial guide portion 45 is a guide hole whose radial direction is the longitudinal direction (FIG. 3), and penetrates the support shaft 51. That is, in the first and second fixed disk portions 41 and 43, when viewed from the axial direction, the radial guide portions 44 and 45 are radially centered about the first rotation center axis R1. The respective radial guide portions 44 and 45 are formed at positions facing each other in the axial direction, and the second rotation center axis R2 is located on a substantially tilting plane regardless of the speed ratio γ. The support shaft 51 is held. The reason for “substantially” is that a slight gap is provided between the support shaft 51 and the width direction of the radial guide portions 44 and 45 for smooth tilting operation of the support shaft 51. FIG. 2 is a view of the first fixed disk portion 41 viewed in the axial direction from the planetary ball 50 side. FIG. 3 is a view of the rotating disk portion 42 and the second fixed disk portion 43 as viewed in the axial direction from the planetary ball 50 side.

  As described above, the rotating disk portion 42 can rotate relative to the shaft 60 in the circumferential direction. For the relative rotation, an actuator (drive unit) such as an electric motor (not shown) is used. The driving force of this driving portion is transmitted to the outer peripheral portion of the rotating disk portion 42 via the worm gear 81 shown in FIG.

  On the other hand, the rotating disk part 42 is provided with a tilting force applying part 46 for each planetary ball 50. The tilting force applying unit 46 applies a tilting force to one end portion of the support shaft 51 protruding from the planetary ball 50 as the rotating disk unit 42 rotates. For example, the tilting force applying part 46 is a linear groove or hole whose longitudinal direction is inclined at a predetermined inclination angle with respect to the radial direction (FIG. 3). When viewed from the axial direction, a portion of the tilting force applying portion 46 overlaps a portion of the radial guide portion 45. The intersecting portion where the portions overlap each other moves in the radial direction as the rotating disk portion 42 rotates. One end of the support shaft 51 is supported at the intersection. Therefore, when the rotating disk portion 42 is rotated, a tilting force acts on one end portion of the support shaft 51 from the side wall surface of the tilting force applying portion 46, and the end portion is a radial guide. Guided in the radial direction by the portions 44 and 45. In the continuously variable transmission 1, this guiding operation is a tilting operation of the planetary ball 50.

  Specifically, in the carrier 40, the tilting force corresponding to the relative rotation acts on one end portion of the support shaft 51 by relatively rotating the first fixed disk portion 41 and the rotating disk portion 42. . For example, when the rotary disk portion 42 is rotated in the clockwise direction in FIG. 3, the side wall pushes one end portion of the support shaft 51 along the radially outer side wall in the tilting force applying portion 46. To do. At this time, the pushing force becomes a tilting force, and one end portion of the support shaft 51 is moved radially inward by the radial guide portions 44 and 45, so that the speed ratio γ is shifted to the speed increasing side. . On the other hand, when the rotating disk portion 42 is rotated in the counterclockwise direction in FIG. 3, the side wall pushes one end of the support shaft 51 along the radially inner side wall of the tilting force applying portion 46. Move. At this time, the pushing force is a tilting force, and one end portion of the support shaft 51 is moved radially outward by the radial guide portions 44 and 45, so that the gear ratio γ is shifted toward the reduction side. Since the planetary ball 50 is sandwiched between the first rotating member 10, the second rotating member 20, and the sun roller 30, if it is a sphere, the center of gravity is centered when its tilting force is applied. Tilt.

  In the continuously variable transmission 1, lubricating oil (so-called traction oil) is used for cooling each part (cooling object and lubrication object) and generating traction force. For example, the lubricating oil is supplied to the axial center oil passage 61 of the shaft 60 from the oil pump OP shown in FIG. The arrows shown in FIG. 4 represent the lubricating oil supply path. At least one radial oil passage is formed in the shaft 60, and the lubricating oil in the axial center oil passage 61 is supplied to each part of the continuously variable transmission 1 from the radial oil passage. For example, at least one radial oil passage 62 is formed on the shaft 60 on the reference plane (that is, radially inward of the sun roller 30). The radial oil passage 62 supplies the lubricating oil in the axial oil passage 61 to an annular gap S formed between the first rotating body 31 and the second rotating body 32. The gap S is preferably provided with a thickness in the axial direction so that the supplied lubricating oil can be stored.

  Lubricating oil in the gap S is caused by the centrifugal force generated by the rotation of the sun roller 30 or the pressure generated by the pumping of the oil pump OP from the annular gap 33 between the first rotating body 31 and the second rotating body 32 to the sun roller 30 and the planet. It is supplied between the balls 50. That is, the annular gap 33 forms an annular lubricating oil passage for supplying lubricating oil between the sun roller 30 and the planetary ball 50 (particularly, the first and second contact portions P3 and P4). Therefore, the lubricating oil contributes to the cooling and lubrication of the sun roller 30 and the planetary ball 50 and the generation of traction force at the first and second contact portions P3 and P4. Hereinafter, the annular gap 33 is referred to as an annular oil passage 33. The annular oil passage 33 is thinner in the axial direction than the gap S.

  On the other hand, the continuously variable transmission 1 needs to generate a traction force between the first and second rotating members 10 and 20 and the planetary ball 50, that is, at the contact portions P1 and P2. There is a possibility that the lubricating oil supplied from the annular oil passage 33 of the sun roller 30 is also supplied to the contact portions P1, P2 via the planetary balls 50. However, when relying on this lubricating oil, its supply amount is small, and there is a possibility that it will not be supplied depending on the gear ratio γ. Therefore, the sun roller 30 is provided with at least one first and second lubricating oil passages 34 and 35 for supplying lubricating oil between the first and second rotating members 10 and 20 and the planetary ball 50. .

  Here, the lubricating oil is supplied to the contact portions P1, P2 of the first and second rotating members 10, 20 with the planetary ball 50 or in the vicinity of the contact portions P1, P2. However, it is difficult to directly supply the lubricating oil from the sun roller 30 to the contact portions P1, P2 where the first and second rotating members 10, 20 and the planetary ball 50 are actually in contact. On the other hand, lubrication from the outer peripheral surface side of the sun roller 30 is performed on the inner peripheral surfaces 10a and 20a of the first and second rotating members 10 and 20 on the contact spare portion and the vicinity thereof through the space between adjacent planetary balls 50. It is possible to supply oil directly.

  For this reason, the first lubricating oil passage 34 directly supplies the lubricating oil from between the adjacent planetary balls 50 toward or near the contact spare portion on the inner peripheral surface 10a, and through the contact spare portion and the like. It forms so that lubricating oil may be supplied to the contact part P1 at the time of a driving | operation (FIG. 5). Accordingly, the first lubricating oil passage 34 has an opening toward the contact preliminary portion or the vicinity of the contact preliminary portion. The opening communicates with the annular gap S. Lubricating oil is supplied to the first lubricating oil passage 34 from the annular gap S by the centrifugal force accompanying the rotation of the sun roller 30 or the pressure generated by the pumping of the oil pump OP. The lubricating oil in the first lubricating oil passage 34 is discharged from the opening by the centrifugal force or the like, and is supplied to the contact preliminary portion on the inner peripheral surface 10a or the vicinity thereof. The flow amount (for example, the discharge amount per unit time) of the lubricating oil in the first lubricating oil passage 34 may be determined according to the required supply amount of the lubricating oil to the contact portion P1. The required supply amount is the target cooling performance and target lubrication performance of the first rotating member 10 and the planetary ball 50, the power transmission efficiency between the first rotating member 10 and the planetary ball 50, and the like. It is a quantity. FIG. 5 is a conceptual cross-sectional view of the continuously variable transmission 1 cut along a plane including the respective contact portions P1 and the contact preliminary portions. The arrows shown in FIG. 5 represent the lubricating oil supply path.

  Similarly, the second lubricating oil passage 35 supplies lubricating oil directly from between adjacent planetary balls 50 toward or near the contact spare portion on the inner peripheral surface 20a, and the contact spare portion and the like are supplied. Thus, the lubricating oil is formed so as to be supplied to the contact portion P2 during operation (FIG. 5). Accordingly, the second lubricating oil passage 35 has an opening toward the contact preliminary portion or the vicinity of the contact preliminary portion. The opening communicates with the annular gap S. Lubricating oil is supplied to the second lubricating oil passage 35 from the annular gap S by a centrifugal force accompanying the rotation of the sun roller 30 or a pressure by the oil pump OP. The lubricating oil in the second lubricating oil passage 35 is discharged from the opening by the centrifugal force or the like, and is supplied to the contact preliminary portion on the inner peripheral surface 20a or the vicinity thereof. The flow amount (for example, the discharge amount per unit time) of the lubricating oil in the second lubricating oil passage 35 may be determined according to the required supply amount of the lubricating oil to the contact portion P2. The required supply amount is the target cooling performance and target lubrication performance of the second rotating member 20 and the planetary ball 50, the power transmission efficiency between the second rotating member 20 and the planetary ball 50, and the like. It is a quantity. FIG. 5 is also a conceptual cross-sectional view of the continuously variable transmission 1 cut along a plane including the respective contact portions P2 and the contact preliminary portions.

  Specifically, the first lubricating oil passage 34 includes an oil passage 31 a of the first rotating body 31 and an oil passage 36 a formed by a guide member 36 that rotates integrally with the first rotating body 31. . The oil passage 31 a has an opening connected to the annular gap S, and an opening on the side wall surface (side wall surface on the first fixed disk portion 41 side) in the axial direction of the first rotating body 31. The opening on the side wall surface is formed on the radially outer side than the opening connected to the annular gap S. Therefore, the oil passage 31 a can discharge the lubricating oil in the annular gap S from the side wall surface of the first rotating body 31 by a centrifugal force or the like accompanying the rotation of the sun roller 30. The opening on the side wall surface (discharge port of the oil passage 31a) communicates with an oil passage 36a formed by the side wall surface and the guide member 36. The guide member 36 is, for example, a plate-like member having a groove portion, and is fixed to the side wall surface of the first rotating body 31 so that the groove portion communicates with the discharge port of the oil passage 31a. The groove portion serves as an oil passage 36 a when the guide member 36 is fixed to the side wall surface of the first rotating body 31. Therefore, the groove portion has a shape having an opening toward the contact spare portion or the vicinity of the contact spare portion on the inner peripheral surface 10a in a state where the guide member 36 and the side wall surface of the first rotating body 31 are fixed. . In addition, the illustrated groove portion is formed so that the oil passage 36a has a shape for guiding the lubricating oil radially outward. For this reason, the lubricating oil in the oil passage 31a is supplied to the oil passage 36a by a centrifugal force or the like accompanying the rotation of the sun roller 30, and the contact reserve on the inner peripheral surface 10a of the first rotating member 10 from the opening of the oil passage 36a. Or toward the vicinity of the contact preliminary portion. When a plurality of first lubricating oil passages 34 are provided, the guide member 36 may be provided for each first lubricating oil passage 34 as shown in FIG. A plurality of oil passages 36a for each oil passage 34 may be formed.

  The second lubricating oil passage 35 has the same configuration as the first lubricating oil passage 34. Accordingly, the second lubricating oil passage 35 includes an oil passage 32a of the second rotating body 32, a side wall surface in the axial direction of the second rotating body 32 (a side wall surface on the second fixed disk portion 43 side), a guide member 37, and the like. And an oil passage 37a formed by The oil passage 32a has an opening connected to the annular gap S and an opening on the side wall surface in the axial direction of the second rotating body 32 located radially outside of the opening. The opening on the side wall surface (discharge port of the oil passage 32a) communicates with the oil passage 37a. The guide member 37 is, for example, a plate-like member having the same groove as the guide member 36 and can rotate integrally with the second rotating body 32. The guide member 37 is fixed to the side wall surface of the second rotating body 32 so that the groove portion communicates with the discharge port of the oil passage 32a. Therefore, the groove portion becomes a radial oil passage 37a when the guide member 37 is fixed to the side wall surface of the second rotating body 32, and the guide member 37 and the side wall surface of the second rotating body 32 are fixed. In this state, the contact spare portion on the inner peripheral surface 20a or a shape having an opening toward the vicinity of the contact spare portion is formed. Lubricating oil in the annular gap S is supplied to the oil passage 32a by the centrifugal force accompanying the rotation of the sun roller 30 or the pressure by the pumping of the oil pump OP, and is discharged from the side wall surface of the second rotating body 32 to the oil passage 37a. . Then, the lubricating oil in the oil passage 37a is discharged from the opening toward the contact spare part or the vicinity of the contact spare part on the inner peripheral surface 20a of the second rotating member 20 by the centrifugal force or the like.

  The lubricating oil discharged from the first and second lubricating oil passages 34 and 35 is the contact spare portion or the contact spare portion on the inner peripheral surfaces 10a and 20a of the first and second rotating members 10 and 20, respectively. It adheres to the vicinity. The adhering lubricating oil is mixed with the first and second rotating members 10 and 20 and the planets when the contact preliminary portions become the contact portions P1 and P2 as the first and second rotating members 10 and 20 rotate. Reach between the balls 50. In this way, the continuously variable transmission 1 can supply lubricating oil to the respective contact portions P1, P2, so that the cooling performance of the first and second rotating members 10, 20 and the planetary ball 50 can be improved. Lubrication performance can be improved. Therefore, the continuously variable transmission 1 can suppress excessive heat generation of the first and second rotating members 10 and 20 and the planetary ball 50, and therefore generates a traction force at each of the contact portions P1 and P2. Can transmit power. At this time, some of the lubricating oil discharged from the first and second lubricating oil passages 34 and 35 is directly supplied to the planetary ball 50, and this is the contact ratio P1, P2 depending on the gear ratio γ. May be sent to. Further, the supply of the lubricating oil is realized by a simple structure by the first and second lubricating oil passages 34 and 35 using the centrifugal force of the sun roller 30. Therefore, the continuously variable transmission 1 can improve the cooling performance while suppressing an increase in cost.

  By the way, in this embodiment, the first and second lubricating oil passages 34 and 35 are formed by attaching the guide members 36 and 37, which are separate members, to the first and second rotating bodies 31 and 32, respectively. ing. However, the first and second lubricating oil passages 34 and 35 may be configured only by the sun roller 130 without using a separate member, as shown in FIG. The sun roller 130 is the same as the sun roller 30 described above except for the configuration relating to the first and second lubricating oil passages 34 and 35. In FIG. 7, for the sake of convenience, the same components are denoted by the same reference numerals as the sun rollers 30.

  The 1st lubricating oil path 34 is formed in the 1st rotary body 131 which has the 1st contact part P3. The first rotating body 131 corresponds to the first rotating body 31 having an increased thickness in the axial direction. The first lubricating oil passage 34 includes an oil passage 131a corresponding to the oil passage 31a and an oil passage 131b corresponding to the oil passage 36a. The oil passage 131a has an opening through which the lubricating oil in the annular gap S is introduced, and the lubricating oil introduced through the opening is obliquely outward (in the axial direction on the first fixed disk portion 41 side and radially outward). In a diagonal direction). The oil passage 131b supplies the guided lubricating oil toward the contact spare part or the vicinity of the contact spare part on the inner peripheral surface 10a, and has an opening toward the contact spare part or the vicinity thereof. The illustrated oil passage 131b has a shape that guides the lubricating oil outward in the radial direction. The lubricating oil in the annular gap S is supplied to the oil passage 131a and guided to the oil passage 131b by the centrifugal force accompanying the rotation of the sun roller 130 and the pressure by the pressure pumping of the oil pump OP. The lubricating oil in the oil passage 131b is discharged from the opening toward the contact preliminary portion on the inner peripheral surface 10a of the first rotating member 10 or the vicinity thereof by the centrifugal force or the like.

  The second lubricating oil passage 35 has the same configuration as the first lubricating oil passage 34. Accordingly, the second lubricating oil passage 35 is formed in the second rotating body 132 having the second contact portion P4. The second rotator 132 corresponds to an increased thickness of the second rotator 32 in the axial direction. The second lubricating oil passage 35 includes an oil passage 132a corresponding to the oil passage 32a and an oil passage 132b corresponding to the oil passage 37a. The oil passage 132a has an opening through which the lubricating oil in the annular gap S is introduced, and the lubricating oil introduced through the opening is inclined outward (in the axial direction on the second fixed disk portion 43 side and radially outward). In a diagonal direction). The oil passage 132b supplies the guided lubricating oil toward the contact spare part or the vicinity of the contact spare part on the inner peripheral surface 20a, and has an opening toward the contact spare part or the vicinity thereof. The illustrated oil passage 132b has a shape that guides the lubricating oil radially outward. The lubricating oil in the annular gap S is supplied to the oil passage 132a and guided to the oil passage 132b by the centrifugal force accompanying the rotation of the sun roller 130 and the pressure generated by the oil pump OP. The lubricating oil in the oil passage 132b is discharged from the opening toward the contact preliminary portion on the inner peripheral surface 20a of the second rotating member 20 or the vicinity thereof by the centrifugal force or the like.

  Even if the first and second lubricating oil passages 34 and 35 are configured in this way, the same effects as those described above can be obtained. Further, in this case, the cost can be reduced by reducing the number of parts.

  Here, in this example, at least one first and second lubricating oil passages 34 and 35 are provided. However, the supply target of the lubricating oil from the sun roller 30 (130) is the contact portion P1, P2. In the case of only one of these, at least one of the first lubricating oil passage 34 and the second lubricating oil passage 35 may be provided in accordance with the supply target.

[Modification 1]
As in the above-described embodiment, the present modification is an adjacent planet toward the contact spare part or the vicinity of the contact spare part on the inner peripheral surfaces 10a and 20a of the first and second rotating members 10 and 20. Lubricating oil is directly supplied from between the balls 50, and the lubricating oil is supplied to the contact portions P1, P2 during operation through the contact preliminary portion or the vicinity thereof. The continuously variable transmission 1 of this modification is obtained by changing the shape of the oil passage (annular oil passage 33) formed at the center position in the axial direction of the sun roller 30 in the continuously variable transmission 1 of the above-described embodiment. is there.

  The sun roller 230 of this modification is the same as the sun roller 30 described above except for the oil passage 233 to be changed. In FIG. 8, for the sake of convenience, the same components as those of the sun roller 30 are denoted by the same reference numerals, and the first and second lubricating oil passages 34 and 35 are omitted. Further, in FIG. 8, for convenience, only one of the chamfered portion angles θ1 and the contact angle θ2 described later are shown. The oil passage 233 is an annular oil passage composed of an annular gap S. The oil passage 233 expands in the axial direction on the planetary ball side (that is, on the lubricating oil discharge side rather than the lubricating oil introduction side) than the annular clearance S side with respect to the oil passage 33, so that the sun roller 230 rotates. It has been changed so that lubricating oil can be sprayed over a wide area by the accompanying centrifugal force.

  The first rotator 231 is provided with a chamfered portion 231 a at the radially outer end on the wall surface on the second rotator 232 side forming the oil passage 233. The chamfered portion 231a has a shape that moves away from the reference plane as it goes radially outward, and is provided throughout the circumferential direction. The chamfered portion 231a has a chamfered portion angle θ1 (a chamfered portion 231a measured with reference to the axial direction) in which the contact spare portion on the inner peripheral surface 10a or the vicinity of the contact spare portion exists on an extension line extending radially outward. Angle). This is because the lubricating oil discharged along the chamfered portion 231a is supplied to the contact spare portion or the vicinity of the contact spare portion on the inner peripheral surface 10a. Further, the chamfered portion angle θ1 is set to be smaller than the contact angle θ2 of the first contact portion P3 (an angle perpendicular to the normal measured with reference to the axial direction). The chamfered portion 231a is formed such that the axial distance A from the reference plane to the radially outer end is shorter than the axial distance B from the reference plane to the first contact portion P3 (A <B). This is because the first contact portion P3 that is a contact portion with the planetary ball 50 is secured.

  On the other hand, the second rotating body 232 is provided with a chamfered portion 232 a at the radially outer end on the wall surface on the first rotating body 231 side forming the oil passage 233. The chamfered portion 232a has a shape that moves away from the reference plane as it goes radially outward, and is provided throughout the circumferential direction. The chamfered portion 232a has a chamfered portion angle θ1 (a chamfered portion 232a measured with reference to the axial direction) in which the contact spare portion on the inner peripheral surface 20a or the vicinity of the contact spare portion exists on an extension line extending radially outward. Angle). This is because the lubricating oil discharged along the chamfered portion 232a is supplied to the contact spare portion or the vicinity of the contact spare portion on the inner peripheral surface 20a. Here, the angle is the same as that of the chamfered portion 231a. Further, the chamfered portion angle θ1 is made smaller than the contact angle θ2 of the second contact portion P4 (θ1 <θ2). The chamfered portion 232a is formed such that the axial distance A from the reference plane to the radially outer end is shorter than the axial distance B from the reference plane to the second contact portion P4 (A <B). This is to secure the second contact portion P4 that is a contact portion with the planetary ball 50. Here, the distance A is the same as the chamfered portion 231a.

  In this continuously variable transmission 1, the lubricating oil in the annular gap S is introduced into the oil passage 233 by centrifugal force or the like accompanying the rotation of the sun roller 230, and is discharged from the radially outer side enlarged by the chamfered portions 231 a and 232 a. The At that time, some of the discharged lubricating oil is discharged in the radial direction, and some is discharged diagonally outward along the chamfered portions 231a and 232a by surface tension. When the lubricating oil discharged in the radial direction or obliquely outward is supplied directly to the planetary ball 50, it is mainly guided to the first and second contact portions P3 and P4. Further, the lubricating oil discharged obliquely outward is directly supplied from between the adjacent planetary balls 50 to the contact spare part or the vicinity of the contact spare part on the inner peripheral surfaces 10a, 20a, and the contact spare part or the vicinity thereof. Is supplied to the contact portions P1 and P2.

  Therefore, the continuously variable transmission 1 of this modified example includes, for example, the first and second lubricating oil passages 34 and 35 and the oil passage 233 so that the necessary amount of lubricating oil can be secured at the contact portions P1 and P2. When the flow amount of lubricating oil (for example, the discharge amount per unit time) is determined, the same effect as that of the embodiment can be obtained.

  The oil passage 233 is not necessarily provided together with the first and second lubricating oil passages 34 and 35 as long as the necessary supply amount of the lubricating oil to the contact portions P1 and P2 can be secured.

  Here, the annular chamfered portions 231a and 232a of this modification are square chamfered portions in which the cross section cut in the radial direction and the axial direction is a straight line, but as shown in FIG. The cross section cut into two may be replaced with chamfered portions 231b and 232b having an arc shape. The chamfered portions 231b and 232b are bulged toward the opposed rotating bodies, and the shape change is gentle compared to the chamfered portions 231a and 232a, and stress concentration can be reduced. Therefore, the continuously variable transmission 1 can improve the durability of the sun roller 230 in addition to the above-described effects.

[Modification 2]
In this modification, lubricating oil is supplied to only one of the two contact portions P1 and P2 in the oil passage 233 of Modification 1 described above. For example, when the speed ratio γ is on the speed increasing side, the temperature of the first rotating member 10 is likely to be higher than that of the second rotating member 20. On the other hand, when the speed ratio γ is on the deceleration side, the temperature of the second rotating member 20 is likely to be higher than that of the first rotating member 10. For this reason, when it is assumed that the continuously variable transmission 1 uses one speed ratio γ on either the speed increasing side or the speed reducing side more than the other, the first and second rotating members 10 and 20 are There is a possibility that the durability on one side corresponding to the frequently used gear ratio γ is lower than that on the other side.

  Therefore, in the present modification, the lubricating oil can be directly supplied to only one of the first and second rotating members 10 and 20 that is assumed to be deteriorated in durability. The continuously variable transmission 1 according to the present modification has the chamfered portions 231a and 232a (231b and 232b) provided at two locations in the continuously variable transmission 1 according to the above-described modified example 1, and a chamfered portion is provided. By providing an annular projecting portion facing the chamfered portion on the non-rotating body, an oil passage 333 that can supply lubricating oil directly to only one side is formed. The oil passage 333 is an annular oil passage composed of an annular gap S.

  The sun roller 330 of the present modification is illustrated as one in which the speed increasing speed ratio γ is frequently used. That is, in this modification, a configuration in which the lubricating oil is directly supplied to the first rotating member 10 is illustrated. In FIG. 10, for convenience, the same components are denoted by the same reference numerals as the sun roller 230, and the first and second lubricating oil passages 34 and 35 are omitted.

  The sun roller 330 includes the same first rotating body 231 as the sun roller 230 having an annular chamfered portion 231a, and a second rotating body 332 having an annular protruding portion 332a. For example, in the second rotating body 232 of the sun roller 230, the second rotating body 332 is obtained by projecting an annular chamfered portion 232a toward the chamfered portion 231a of the first rotating body 231, and the protruding portion 332a. An annular gap between the chamfered portion 231a and the chamfered portion 231a becomes a contact spare portion on the inner peripheral surface 10a or an oil passage 333 toward the vicinity of the contact spare portion. In this example, the chamfered portion 231a and the protruding portion 332a are substantially parallel to each other. However, the interval is not necessarily parallel.

  In the continuously variable transmission 1, the lubricating oil in the annular gap S is introduced into the oil passage 333 by centrifugal force or the like accompanying the rotation of the sun roller 330, and the contact spare part on the inner peripheral surface 10 a or the vicinity of the contact spare part. It is discharged toward. When the discharged lubricating oil is directly supplied to the planetary ball 50, it is mainly guided to the first contact portion P3. Further, the discharged lubricating oil is directly supplied from between the adjacent planetary balls 50 to the contact spare portion on the inner peripheral surface 10a or in the vicinity of the contact spare portion, and the contact portion P1 with the rotation of the first rotating member 10. Supplied to.

  Thus, the continuously variable transmission 1 of this modification can supply lubricating oil intensively with respect to the 1st rotation member 10 (or 2nd rotation member 20) by which durability fall is assumed. Therefore, the cooling performance and lubrication performance of the first rotating member 10 (or the second rotating member 20) and the planetary ball 50 can be improved. Here, the lubricating oil is supplied from, for example, the second lubricating oil path 35 (or the first lubricating oil path 34) to the second rotating member 20 (or the first rotating member 10) to which no lubricating oil is supplied from the oil path 333. Therefore, the cooling performance and the like can be secured.

  The oil passage 333 is not necessarily provided together with the first and second lubricating oil passages 34 and 35 as long as the necessary supply amount of the lubricating oil to the contact portion P1 (P2) can be secured. Further, the annular chamfered portion 231a and the protruding portion 332a do not necessarily have to be integrally formed with the first rotating body 231 and the second rotating body 332, and the annular separate member having the same is rotated for the first rotation. You may comprise by fixing to the body 231 and the 2nd rotary body 332.

  Here, the annular chamfered portion 231a and the protruding portion 332a of this modified example have a radial cross section cut in the axial direction, but the radial direction and the axial direction as shown in FIG. You may replace with the chamfering part 231b and the protrusion part 332b from which the cross section cut into arc becomes arc shape. The chamfered portion 231b is the same as that illustrated in FIG. 9, and stress concentration can be reduced. Moreover, since the protrusion part 332b is dented according to the shape of the chamfered part 231b, the shape change is gentle compared with the protrusion part 332a, and stress concentration can be reduced. Therefore, the continuously variable transmission 1 can improve the durability of the sun roller 330 in addition to the above-described effects.

[Modification 3]
The continuously variable transmission 1 of this modification is obtained by replacing the oil path 333 of the sun roller 330 with the oil path 433 of the sun roller 430 shown in FIGS. 12 and 13 in the continuously variable transmission 1 of the above-described modification 2. is there. The oil passage 433 is an annular oil passage composed of an annular gap S. In FIG. 12 and FIG. 13, for convenience, the same components are denoted by the same reference numerals as the sun roller 330, and the first and second lubricating oil passages 34 and 35 are omitted.

  The first rotating body 431 has a chamfered portion 431a as shown in FIGS. The chamfered portion 431a has a cross-sectional shape equivalent to that of the chamfered portion 231a of the second modification cut in the radial direction and the axial direction. However, the chamfered portion 431a is not provided in the entire circumferential direction like the chamfered portion 231a of the modified example 2, and is not annular. On the other hand, the 2nd rotary body 432 has the protrusion part 432a in the position which opposes the chamfering part 431a in an axial direction. The protruding portion 432a has a cross-sectional shape equivalent to the protruding portion 332a of Modification 2 cut in the radial direction and in the axial direction. The protruding portion 432a is provided only in a portion facing the chamfered portion 431a in the axial direction, and is not provided in the entire circumferential direction. Further, the protruding portion 432a is closer to the axial direction than the gap C between the first rotating body 431 and the second rotating body 432 at the base of the oil passage 433 (the radially inner portion without the chamfered portion 431a or the protruding portion 432a). The protrusion D is formed so as to be small (D <C).

  Furthermore, as shown in FIGS. 13 and 14, the second rotating body 432 has a chamfered portion 432b at a position shifted from the position of the protruding portion 432a in the circumferential direction. The chamfered portion 432b has a cross-sectional shape equivalent to the chamfered portion 431a cut in the radial direction and in the axial direction. In addition, it can be said that this chamfered part 432b has a cross-sectional shape equivalent to the chamfered part 232a of the modification 1 cut | disconnected in radial direction and the axial direction. The first rotating body 431 has a protruding portion 431b at a position facing the chamfered portion 432b in the axial direction. The protrusion 431b has a cross-sectional shape equivalent to the protrusion 432a cut in the radial direction and in the axial direction. The protruding portion 431b is provided only at a portion facing the chamfered portion 432b in the axial direction. Moreover, this protrusion part 431b has the relationship of the clearance gap C and protrusion amount D which are the same as the protrusion part 432a.

  The sun roller 430 of this modification is provided with a combination of the chamfered portion 431a and the protruding portion 432a and a combination of the chamfered portion 432b and the protruding portion 431b shifted in the circumferential direction at least one set. For example, as shown in FIG. 14, the respective sets may be provided alternately with no interval in the circumferential direction, or may be provided alternately or in an irregular order with an interval in the circumferential direction. Therefore, in the continuously variable transmission 1 of this modification, unlike the modification 2, the oil passage 433 can supply the lubricating oil to both the first rotating member 10 and the second rotating member 20. Therefore, this continuously variable transmission 1 not only can obtain the same effect as the continuously variable transmission 1 of the modification 1, but also directivity of the lubricating oil toward the first rotating member 10 and the second rotating member 20. Therefore, the cooling performance and the like can be improved as compared with the first modification. In the sun roller 430, the combination of the chamfered portion 431a and the protruding portion 432a and the combination of the chamfered portion 432b and the protruding portion 431b have a relationship between the gap C and the protruding amount D. Relative rotation between the second rotating body 432 and the second rotating body 432 is possible.

  The oil passage 433 is not necessarily provided together with the first and second lubricating oil passages 34 and 35 as long as the necessary supply amount of the lubricating oil to the contact portions P1 and P2 can be secured. Further, the chamfered portion 431 a and the protruding portion 431 b of the first rotating body 431 and the protruding portion 432 a and the chamfered portion 432 b of the second rotating body 432 are not necessarily formed integrally with the first rotating body 431 and the second rotating body 432. It is not necessary to be a thing, and you may comprise by fixing the cyclic | annular separate member which has these to the 1st rotary body 431 and the 2nd rotary body 432. FIG.

  By the way, in the continuously variable transmission 1 of the above-described embodiment and the first to third modifications, the input shaft 11 and the output shaft 21 are arranged together on the torque input side where the first rotating member 10 and the like are arranged. . However, the technology relating to the lubricating oil supply path described in this embodiment and the like is a continuously variable transmission in which the input shaft 11 and the output shaft 21 are arranged together on the torque output side where the second rotating member 20 and the like are arranged. The present invention may be applied to a machine, or may be applied to a continuously variable transmission in which the input shaft 11 is disposed on the torque input side and the output shaft 21 is disposed on the torque output side. Even in this case, the continuously variable transmission can obtain the same effects as those of the embodiment.

1 continuously variable transmission 10 first rotating member (first power transmission element)
10a, 20a Inner peripheral surface 20 Second rotating member (second power transmission element)
30, 130, 230, 330, 430 Sun Roller (third power transmission element)
31, 131, 231, 431 First rotating body 31a, 131a, 131b, 132a, 132b Oil passage 32, 132, 232, 332, 432 Second rotating body 32a Oil passage 33, 233, 333, 433 Gap (annular oil passage) )
34 1st lubricating oil path 35 2nd lubricating oil path 36, 37 Guide member 36a, 37a Oil path 40 Carrier (4th power transmission element, fixed element)
50 Planetary ball (rolling member)
60 shaft (transmission shaft)
61 Axial oil passage 62 Radial oil passage 231a, 231b, 232a, 232b, 431a, 432b Chamfered portion 332a, 332b, 431b, 432a Protruding portion OP Oil pump P1, P2 contact portion P3 First contact portion P4 Second contact portion R1 First rotation center axis R2 Second rotation center axis S Clearance

Claims (6)

A transmission shaft as a center of rotation;
First to fourth power transmission elements capable of relative rotation in the circumferential direction between each other having a first rotation center axis concentric with the transmission shaft;
A plurality of first and second rotating shafts having a second rotation center axis and arranged radially on the outer peripheral surface of the third power transmission element, with the first rotation center axis being opposed to each other. A rolling member sandwiched between power transmission elements and tiltably held by the fourth power transmission element;
A transmission that changes the speed ratio between the input and output by tilting each rolling member;
Have
The third power transmission element includes a first rotating body having a first contact portion with each of the rolling members, and relative rotation in the circumferential direction around the first rotation center axis with respect to the first rotating body. And a second rotating body having a second contact portion with each of the rolling members, a gap between the first rotating body and the second rotating body supplied with lubricating oil, Lubricating oil that has an opening toward or near the contact spare part with the rolling member in at least one of the first and second power transmission elements, and communicates the opening with the gap. And a continuously variable transmission.   2. The continuously variable transmission according to claim 1, wherein the first rotating body has an opening on an outer peripheral surface thereof toward the first power transmission element.   The continuously variable transmission according to claim 1 or 2, wherein the second rotating body has the opening toward the second power transmission element on an outer peripheral surface.   The lubricating oil passage having the opening directed to the first power transmission element includes an oil passage of the first rotating body communicating with the gap and lubricating oil discharged from the oil passage of the first rotating body. An oil passage that guides to the opening toward the first power transmission element, and the oil passage having the opening toward the first power transmission element rotates integrally with the first rotating body. 2. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is formed by a groove portion of the member.   The lubricating oil passage having the opening toward the second power transmission element includes an oil passage of the second rotating body communicating with the gap, and a lubricating oil discharged from the oil passage of the second rotating body. An oil passage that guides the opening toward the second power transmission element, and the oil passage having the opening toward the second power transmission element rotates integrally with the second rotating body. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is formed by a groove portion of the member.   The said 3rd power transmission element is further provided with the lubricating oil path which supplies the lubricating oil of the said clearance gap to the said 1st and 2nd contact part, Any one of Claim 1 to 5 characterized by the above-mentioned. The continuously variable transmission described in 1.

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