JP5626076B2 - Continuously variable transmission and method of assembling continuously variable transmission - Google Patents

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 continuously variable transmission in which a gear ratio between input and output is continuously changed by tilting a member and a method for assembling the continuously variable transmission.

  Conventionally, as this type of continuously variable transmission, a transmission shaft serving as a rotation center, a plurality of rotational elements capable of relative rotation with the central axis of the transmission shaft as a first rotation central axis, and the first rotation central shaft And a plurality of rolling members radially arranged around the first rotation center axis, the first rotation element and the second rotation element disposed opposite to each other. So-called traction planetary gears, in which each rolling member is sandwiched between the outer peripheral surface of the third rotating element and the gear ratio is steplessly changed by tilting the rolling member. One with a mechanism is known. For example, Patent Document 1 below discloses this type of continuously variable transmission.

  The following Patent Document 2 discloses a ball bearing in which resin balls and steel balls having a smaller diameter than the resin balls are alternately arranged.

JP-T-2006-519349 JP 2004-218790 A

  By the way, in this type of continuously variable transmission, spherical members of the same shape are used for all the rolling members in order to perform the speed change operation smoothly and accurately. However, when each of the rolling members is strictly observed, the size of each of the rolling members varies within the range of the design tolerance. For this reason, between the first and second rotating elements and all the rolling members, the first rotating element and the second rotation are selected in order from the largest rolling member among all the rolling members. Will support the elements. Accordingly, in all of the rolling members arranged radially, when the arrangement of the three rolling members is biased, in this continuously variable transmission, the first rotating element and the second rotating element have their own first rotation. There is a possibility that the transmission efficiency of torque is lowered due to inclination with respect to the central axis.

  Therefore, the present invention improves the inconveniences of the conventional example, and according to the continuously variable transmission and the assembly method of the continuously variable transmission 1, a continuously variable transmission capable of improving the torque transmission efficiency. It is an object of the present invention to provide an assembly method for a machine and a continuously variable transmission.

In order to achieve the above-described object, the present invention provides a first and second rotational elements that are rotatable relative to each other and have a transmission shaft serving as a rotation center and a common first rotation center shaft disposed opposite to each other on the transmission shaft. And a second rotation center axis parallel to the first rotation center axis, and a plurality of radial rotations centered on the first rotation center axis and sandwiched between the first and second rotation elements. A moving member, a support shaft of the rolling member that has the second rotation center axis and projecting at both ends from the rolling member, the rolling members are disposed on an outer peripheral surface, and the transmission shaft, The rotation ratio between the third rotation element capable of relative rotation with respect to the first and second rotation elements and the first rotation element and the second rotation element is changed by the tilting operation of each rolling member. And a transmission that is disposed on the transmission shaft, and each end of each support shaft is connected to the transmission shaft. And a fourth rotation element that holds the rolling member in a state in which the rolling member can be tilted. A first reference rolling member in order from the largest of the rolling members. The second reference rolling member and the third reference rolling member, and each of the rolling members has an acute triangle formed by connecting three rotation centers of the first to third reference rolling members. The first to third reference rolling members arranged as described above, and the remaining rolling members among the rolling members arranged in a space formed by the arrangement of the first to third reference rolling members, , in is characterized by being configured.

Here, a radius when the design tolerance of each of the rolling members is ± 0 is set as a reference radius, and an error of an actual radius of the first to third reference rolling members with respect to the reference radius is defined as the first rotation element. It is desirable that the second rotational element be smaller than the radially movable amount with respect to the transmission shaft.

  Further, the fourth rotating element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, and the center of the first reference rolling member is located below the first rotating center shaft in a use state. It is desirable to arrange.

  In addition, it is preferable that the fourth rotating element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, and the first reference rolling member is disposed at the lowermost portion of the rolling members.

  Further, the fourth rotation element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, and the first reference rolling member and the second reference rolling member are in the use state and the first rotation center It is desirable to place it below the shaft.

Furthermore, in order to achieve the above object, the present invention provides first and second relatively rotatable first and second shafts each having a transmission shaft serving as a rotation center and a common first rotation center shaft disposed so as to face each other on the transmission shaft. A rotation element and a second rotation center axis parallel to the first rotation center axis, and a plurality of the rotation elements arranged radially about the first rotation center axis are sandwiched between the first and second rotation elements. A rolling member, a support shaft for the rolling member that has the second rotation center shaft and projecting at both ends from the rolling member, and each rolling member is disposed on an outer peripheral surface, and A tilting operation of each rolling member is performed by setting a rotation ratio between the first rotating element and the second rotating element, and a third rotating element capable of rotating relative to the axis and the first and second rotating elements. And a transmission device that is changed by each of the support shafts and the respective end portions of the support shafts. And a fourth rotating element that holds the rolling members in a state in which the rolling members can be tilted. In the assembling method of the continuously variable transmission, the rolling members are arranged in descending order of shape. Three lines connecting the steps of selecting as one reference rolling member, a second reference rolling member, and a third reference rolling member, and the respective rotation centers of the selected first to third reference rolling members The first to third reference rolling members are arranged so as to form an acute angle triangle, and the remaining of the rolling members in the space formed by the arrangement of the first to third reference rolling members is arranged. And a step of arranging the rolling members to arrange the rolling members .

Here, the radius when the design tolerance of each of the rolling members is ± 0 is set as a reference radius, and an error of an actual radius with respect to the reference radius is determined in the selection process of the first to third reference rolling members. It is desirable to select the first to third reference rolling members that are smaller than the amount of radial movement of the first rotating element and the second rotating element with respect to the transmission shaft.

  In addition, when the fourth rotating element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, the center of the first reference rolling member is in use in the step of arranging the rolling members. It is desirable that the first rotation center axis is disposed below the first rotation center axis.

  Further, in the case where the fourth rotating element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, the first reference rolling member of the rolling member is arranged in the step of arranging the rolling members. Among these, it is desirable to arrange at the bottom.

  Further, when the fourth rotating element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, the first reference rolling member and the second reference rolling are arranged in the step of arranging each rolling member. It is desirable to arrange the member so that the center thereof is located below the first rotation center axis in use.

  According to the continuously variable transmission and the assembly method of the continuously variable transmission according to the present invention, the first to third reference rolling members having a large shape are arranged so as to form an acute triangle. It becomes a thing with little bias with respect to this rolling member. Therefore, in the continuously variable transmission, the amount of inclination of the first rotating element or the second rotating element with respect to the transmission shaft can be suppressed to a small value, so that the unbalanced load applied to the bearing that supports the first rotating element or the second rotating element. Can be reduced. Therefore, in this continuously variable transmission, it is possible to reduce the drive loss when the first rotating element and the second rotating element rotate, so that the torque transmission efficiency can be improved.

FIG. 1 is a partial sectional view showing the configuration of an embodiment of a continuously variable transmission according to the present invention. FIG. 2 is a diagram for explaining the guide groove of the carrier. FIG. 3 is a diagram illustrating the iris plate. FIG. 4 is a diagram illustrating an example of the arrangement of three reference balls. FIG. 5 is a diagram illustrating another example of the arrangement of three reference balls. FIG. 6 is a diagram illustrating another example of the arrangement of three reference balls.

  Hereinafter, embodiments of a continuously variable transmission and a continuously variable transmission assembly method according to the present invention will be described in detail with reference to the drawings. The present invention is not limited to the embodiments.

[Example 1]
A first embodiment of a continuously variable transmission and a continuously variable transmission assembling method according to the present invention will be described with reference to FIGS.

  First, an example of a continuously variable transmission according to the present embodiment will be described with reference to FIG. Reference numeral 1 in FIG. 1 indicates a continuously variable transmission according to this embodiment.

  The continuously variable transmission mechanism that forms the main part of the continuously variable transmission 1 includes first to fourth rotating elements 10, 20, 30, which are capable of relative rotation with each other and have a common first rotation center axis R 1. 40, a plurality of rolling members 50 each having a second rotation center axis R2 parallel to the first rotation center axis R1 and a reference position to be described later, and first to fourth rotation elements 10, 20, 30. , 40 is a so-called traction planetary gear mechanism provided with a shaft 60 as a transmission shaft disposed at the rotation center. The continuously variable transmission 1 changes the gear ratio between input and output by inclining the second rotation center axis R2 with respect to the first rotation center axis R1 and tilting the rolling member 50. In the following, unless otherwise specified, the direction along the first rotation center axis R1 and the second rotation center axis R2 is referred to as the axial direction, and the direction around the first rotation center axis R1 is referred to as the circumferential direction. 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. In this continuously variable transmission 1, one of the first to fourth rotating elements 10, 20, 30, 40 is fixed so as not to rotate in the circumferential direction, and the rest of the elements is circumferentially It can be rotated.

  In the continuously variable transmission 1, torque is transmitted through the rolling members 50 between the first rotating element 10, the second rotating element 20, the third rotating element 30, and the fourth rotating element 40. . For example, in the continuously variable transmission 1, one of the first to fourth rotating elements 10, 20, 30, and 40 serves as a torque (power) input unit, and at least one of the remaining rotating elements is Torque output section. 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.

  In the continuously variable transmission 1, a plurality of rolling members 50 are arranged radially about the central axis (first rotation central axis R <b> 1) of the shaft 60. The respective rolling members 50 are sandwiched between the first rotating element 10 and the second rotating element 20 that are arranged to face each other, and are disposed on the outer peripheral surface of the third rotating element 30. Each rolling member 50 rotates around its own rotation center axis (second rotation center axis R2). Further, when the fourth rotating element 40 rotates about the first rotation center axis R1, the rolling member 50 rotates together with the fourth rotation element 40 and is centered on the first rotation center axis R1. Make a revolution. The continuously variable transmission 1 includes first to fourth rotating elements 10, 20, 30, 40 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 rolling member 50 and torque can be transmitted therebetween. Further, the continuously variable transmission 1 tilts each rolling member 50 on a tilt plane including its own second rotation center axis R2 and first rotation center axis R1, and the first rotation element 10 By changing the ratio of the rotation speed (rotation speed) between the second rotation element 20 and the second rotation element 20, the ratio of the rotation speed (rotation speed) between the input and output is changed.

  Here, in the continuously variable transmission 1, the first and second rotating elements 10 and 20 perform a ring gear function as a planetary gear mechanism. The third rotating element 30 functions as a sun roller of the traction planetary gear mechanism, and the fourth rotating element 40 functions as a carrier. 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 fourth rotating element 40 is referred to as “carrier 40”. The rolling member 50 is referred to as a “planetary ball 50”.

  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. .

  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.

  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 rotation center axis R1 to the contact portion with each planetary ball 50 becomes the same length in the state of a reference position 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 portion 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 11 is connected to the first rotating member 10, and the output shaft 21 is connected to the second rotating member 20. In the continuously variable transmission 1, the input shaft 11 may be used as an output shaft, and the output shaft 21 may be used as an input shaft.

  The output shaft 21 includes a disk portion 21a and a cylindrical portion 21b having a center axis coinciding with the first rotation center axis R1. The cylindrical portion 21b is provided on the inner peripheral side of the disc portion 21a, and the inner peripheral surface is attached to the outer peripheral surface of the shaft 60 via radial bearings RB1 and RB2. Therefore, the output shaft 21 and the second rotating member 20 connected to the output shaft 21 can perform relative rotation in the circumferential direction with respect to the shaft 60.

  The input shaft 11 also includes a disk portion 11a and a cylindrical portion 11b that are the same as the output shaft 21 whose center axis coincides with the first rotation center axis R1. The cylindrical portion 11b has an inner peripheral surface attached to the outer peripheral surface of the cylindrical portion 21b of the output shaft 21 via radial bearings RB3 and RB4. The input shaft 11 can perform relative rotation in the circumferential direction with respect to the output shaft 21 by the radial bearings RB3, RB4 and the thrust bearing TB described below.

  Here, a torque cam 71, an annular member 72, and a thrust bearing TB are disposed between the outer peripheral planes of the disk portion 11a of the input shaft 11 and the disk portion 21a of the output shaft 21. The annular member 72 and the output shaft 21 can rotate relative to each other via the thrust bearing TB. The torque cam 71 generates an axial force between the input shaft 11 and the annular member 72 and transmits rotational torque by engaging the engaging member on the input shaft 11 side and the engaging member on the annular member 72 side. And rotate them together. The axial force is transmitted to the first rotating member 10 and the second rotating member 20, and becomes a pressing force when pressing each planetary ball 50.

  The sun roller 30 has a cylindrical shape whose center axis coincides with the first rotation center axis R1, and can be rotated relative to the shaft 60 in the circumferential direction by the radial bearings RB5 and RB6. 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 carrier 40 holds each protrusion of a support shaft 51 described later so as not to prevent the tilting operation of each planetary ball 50. In this carrier 40, for example, first and second disk members 41, 42 having a center axis coinciding with the first rotation center axis R1 are arranged to face each other, and the first and second disk members 41, 42 are disposed. Are connected by a plurality of connecting shafts (not shown) to form a bowl shape as a whole. As a result, the carrier 40 has an open portion on the outer peripheral surface. Each planetary ball 50 is disposed between the first and second disk members 41 and 42 and is in contact with the first rotating member 10 and the second rotating member 20 through the open portion.

  The carrier 40 can perform relative rotation in the circumferential direction with respect to the shaft 60 by, for example, a bearing (not shown) between the carrier 40 and the shaft 60. In this example, in order to prevent relative movement in the axial direction with respect to the shaft 60, locking members 91 and 92 such as snap rings are disposed on the respective side surfaces of the carrier 40 in the axial direction.

  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 exemplified by a spherical one. In this continuously variable transmission 1, all the planetary balls 50 are formed in the same shape. 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 rotation center axis R2 as a rotation axis (that is, rotation) by a bearing (not shown) disposed between the outer periphery of the support shaft 51. I am doing so. Accordingly, the planetary ball 50 can roll on the outer peripheral surface of the sun roller 30 around the support shaft 51. Both ends of the support shaft 51 are projected from the planetary ball 50.

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

  The continuously variable transmission 1 is provided with a guide portion for guiding the support shaft 51 in the tilting direction when each planetary ball 50 tilts. In this example, the guide portion is provided on the carrier 40. The guide portions are radial guide grooves 43 and 44 for guiding the support shaft 51 projected from the planetary ball 50 in the tilt direction, and the first and second disk members 41 and 42 are opposed to each other. A portion is formed for each planetary ball 50 (FIG. 2). That is, all the guide grooves 43 and all the guide grooves 44 are radially formed when viewed from the axial direction (the direction of arrow A in FIG. 1). FIG. 2 illustrates a case where eight planetary balls 50 are provided.

  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 rotation speed or rotation speed) between the first rotation member 10 and the second rotation member 20 is 1, and the speed ratio γ is 1. On the other hand, when each planetary ball 50 is tilted from the reference position, the distance from the central axis of the support shaft 51 to the contact portion with the first rotating member 10 changes and from the central axis of the support shaft 51. The distance to the contact portion 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 (speed ratio γ) between the first rotating member 10 and the second rotating member 20 can be changed steplessly by changing the tilt angle. it can. 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 a radial bearing RB7 on the radially inner side, and can rotate relative to the shaft 60 about the first rotation center axis R1. An actuator (drive unit) such as a motor (not shown) is used for the relative rotation. The driving force of this driving unit is transmitted to the outer peripheral portion of the iris plate 80 via the worm gear 81.

  The iris plate 80 is arranged on the input side (contact portion side with the first rotating member 10) or output side (contact portion side with the second rotating member 20) of each planetary ball 50 and outside the carrier 40. . In this example, it is arranged on the input side. 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). 3 is a view seen from the direction of arrow A in FIG.

  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 protrusions of the support shaft 51 are inserted into the guide grooves 43 and 44 of the carrier 40, one protrusion 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 protrusion moves outward in the radial direction by the action of the guide grooves 43 and 44. Thus, the support shaft 51 can move in the radial direction by the guide grooves 43 and 44 and the throttle hole 82. Therefore, the planetary ball 50 can be tilted as described above.

  By the way, all the planetary balls 50 are manufactured under a design tolerance set so that each of the planetary balls 50 becomes a spherical body having an equal roundness, but each planetary ball 50 has a size (one by one within the range of the design tolerance). There is variation in diameter). For this reason, at the contact portion between the first and second rotating members 10 and 20 and all the planetary balls 50, the three planetary balls 50 selected from all the planetary balls 50 in descending order of the diameter are the remaining ones. Prior to the planetary ball 50, the first and second rotating members 10 and 20 are brought into contact with each other. That is, the first and second rotating members 10, 20, the input shaft 11 and the output shaft 21 are supported by the three planetary balls 50.

  Here, the axial force of the torque cam 71 is applied to the first and second rotating members 10 and 20. Further, the first rotating member 10 and the second rotating member 20 can move in the radial direction with respect to the shaft 60. The movable amount (maximum moving amount) of the first rotating member 10 in the radial direction with respect to the shaft 60 is determined by the radial gap between the radial bearings RB <b> 1 and RB <b> 2 and the shaft 60. Further, the movable amount of the second rotating member 20 in the radial direction with respect to the shaft 60 (maximum moving amount) is equal to the movable amount of the first rotating member 10 between the radial bearings RB3, RB4 and the output shaft 21. A radial gap is added. The radial clearance between the radial bearings RB1 and RB2 and the shaft 60 refers to the clearance between the inner peripheral surface of the inner ring of the radial bearings RB1 and RB2 and the outer peripheral surface of the shaft 60. This is the difference between the diameter of the inner peripheral surface of the shaft and the diameter of the outer peripheral surface of the shaft 60. This is because, in the illustrated radial bearings RB <b> 1 and RB <b> 2, the outer ring is tightly fitted to the output shaft 21, while the inner ring is gap-fitted to the shaft 60. The radial clearance between the radial bearings RB3 and RB4 and the output shaft 21 is the clearance between the inner peripheral surface of the inner ring of the radial bearings RB3 and RB4 and the outer peripheral surface of the cylindrical portion 21b of the output shaft 21. In other words, this is the difference between the diameter of the inner peripheral surface of the inner ring and the diameter of the outer peripheral surface of the cylindrical portion 21b. This is because, in the illustrated radial bearings RB3 and RB4, the outer ring is tightly fitted to the input shaft 11, while the inner ring is gap-fitted to the output shaft 21.

  When the first rotating member 10 and the second rotating member 20 are biased such that the arrangement of the three planetary balls 50 is concentrated in one place among the arrangements of all the planetary balls 50, the torque cam 71 thereof. Of the first rotation member 10 and the second rotation member 20 may be tilted with respect to the first rotation center axis together with the input shaft 11 and the output shaft 21, depending on the axial force of the first rotation member 10 and the second rotation member 20. . At the time of tilting, the radial bearings RB1 to RB4 and the thrust bearing TB are subjected to an eccentric load. Therefore, when the three planetary balls 50 having a large shape are arranged in a biased manner, the rotational loss of the first rotating member 10 and the second rotating member 20 due to the biased load received by the radial bearings RB1 to RB4 and the thrust bearing TB. This increases the torque transmission efficiency. Further, in this case, the durability of the radial bearings RB1 to RB4 and the thrust bearing TB may be reduced due to the uneven load.

  Therefore, in the continuously variable transmission 1, the three planetary balls 50 are defined as reference balls (reference rolling members), and the three lines connecting the rotation centers of the three reference balls form an acute triangle. In this manner, all the planet balls 50 are arranged.

  For example, the continuously variable transmission 1 includes eight planetary balls 50A to 50H as shown in FIG. In this continuously variable transmission 1, among the eight planetary balls 50A to 50H, the planetary balls 50A to 50C are used as reference balls. Here, the planetary balls 50A to 50C are also referred to as “first to third reference balls 50A to 50C”. Here, it is assumed that the first reference ball 50A is the largest, and the diameter decreases in the order of the first reference ball 50A, the second reference ball 50B, and the third reference ball 50C.

  In the case of this example, as shown in FIG. 4, three lines connecting the centers of the first to third reference balls 50A to 50C are acute triangles (θ1 <90 degrees, θ2 <90 degrees, All the planetary balls 50A to 50H are arranged so as to satisfy θ3 <90 degrees. The first to third reference balls 50A to 50C may be arranged at any location as long as they can form such an acute triangle.

  In this way, three first to third reference balls 50A to 50C are set, and these are arranged at the time of assembling the continuously variable transmission 1 so as to form the acute triangle as described above. The acute triangle inscribed in a circle connecting the centers of the planetary balls 50A to 50H has a shape with less deviation with respect to the circumscribed circle inside the circumscribed circle. That is, the arrangement is less biased with respect to all the planetary balls 50A to 50H. At the contact portion between the first and second rotating members 10 and 20 and all the planetary balls 50A to 50H, the first to third reference balls 50A to 50C are more than the remaining planetary balls 50D to 50H. First, the first and second rotating members 10 and 20 are brought into contact with each other. In that case, the contact portion between the first and second rotating members 10 and 20 and the first to third reference balls 50A to 50C also becomes an acute triangle, and the acute triangle is a circumscribed circle ( The shape is less biased with respect to a circle connecting the contact portions between the first and second rotating members 10 and 20 and all the planetary balls 50A to 50H. Therefore, in the continuously variable transmission 1, the first and second rotating members 10, 20 as well as the input shaft 11 and the output shaft are made without making the design tolerances of the diameters of all the planetary balls 50A to 50H smaller than the conventional design. 21 can be kept small. That is, although the improvement of the processing accuracy of the planetary balls 50A to 50H causes an increase in cost, the continuously variable transmission 1 does not cause such an increase in cost, and the first and second rotating members 10 and 20 do not. In addition, the amount of inclination of the input shaft 11 and the output shaft 21 can be kept small. As a result, in the continuously variable transmission 1, the radial bearings RB1 to RB4 and the thrust bearing TB can be kept small even if the eccentric load is not applied, or the eccentric load is applied. The driving loss when the second rotating member 20 rotates can be reduced, and the torque transmission efficiency can be improved. Further, in the continuously variable transmission 1, the durability of the radial bearings RB1 to RB4 and the thrust bearing TB can be improved.

  When the triangle formed by the three first to third reference balls 50A to 50C is a right triangle or an obtuse angle triangle, the right triangle or the obtuse angle triangle has a large bias with respect to the circumscribed circle, and therefore the first and second rotations. The amount of inclination of the members 10, 20 and the input shaft 11 and the output shaft 21 is increased. FIG. 5 shows a right triangle as an example.

  As described above, according to the continuously variable transmission 1 and the assembling method of the continuously variable transmission 1, the three first to third reference balls 50A are selected from among all the planetary balls 50A to 50H. To 50C, and the three first to third reference balls 50A to 50C are arranged so as to form an acute-angled triangle, so that the first and second rotating members 10 and 20 and the input shaft 11 and The amount of inclination of the output shaft 21 can be kept small at low cost, and the torque transmission efficiency can be improved and the durability of the radial bearings RB1 to RB4 and the thrust bearing TB can be improved.

Here, in the continuously variable transmission 1, even if such first to third reference balls 50A to 50C are arranged, the first and second rotating members 10, 20 and the input shaft 11 and There is a possibility that the output shaft 21 is slightly inclined, and an eccentric load is applied to the radial bearings RB1 to RB4 and the thrust bearing TB. This because, in this continuously variable transmission 1, performs the arrangement of the third reference ball 50A~50C from a first of said first rotary member design tolerance of the radius _{r b} of the planetary ball 50A~50H above 10 or the amount of radial movement of the second rotating member 20 relative to the shaft 60 is made smaller. Radius _{r b1} of the greatest first reference balls 50A which is the maximum within the design tolerances, the first and second rotary members 10 and 20 and the input shaft 11 and the output shaft 21 by the first reference ball 50A Is inclined, the amount of movement of the first and second rotating members 10, 20, etc. in the radial direction corresponding to the amount of inclination relative to the shaft 60 of the first rotating member 10 or the second rotating member 20 is relative to the shaft 60. This is because it is smaller than the radial movable amount. Therefore, in this continuously variable transmission 1, since the uneven load is not applied to the radial bearings RB1 to RB4 and the thrust bearing TB, the torque of the continuously variable transmission 1 is larger than that corresponding only by the arrangement of the first to third reference balls 50A to 50C. The transmission efficiency and the durability of the radial bearings RB1 to RB4 and the thrust bearing TB can be improved. Incidentally, the radius _{r b,} the design tolerance indicates a reference radius of the planetary ball 50A~50H when the ± 0. Hereinafter, the radius r _{b is referred} to as “reference radius r _b ”.

Since this illustrative contains movable amount in the radial direction of the first rotating member 10 to the movable amount of the radial direction of the second rotating member 20, the design tolerance of the reference radius r _b of the planetary ball 50A~50H is What is necessary is just to make it smaller than the movable amount of the radial direction with respect to the shaft 60 of the 1st rotation member 10.

The reason that the design tolerance of the reference radius r _b of the planetary ball 50A~50H in this manner in comparison subjects, even when the design tolerance is maximized (when the design tolerance is zero in the case of minus tolerance) This is to prevent an unbalanced load from being applied to the radial bearings RB1 to RB4 and the thrust bearing TB. However, the planetary balls 50A to 50H are not always the maximum within the range of the design tolerance. In the continuously variable transmission 1, when the design tolerance of the reference radius rb of the planetary balls 50 </ _b > A to 50 </ _b > H is larger than the radially movable amount of the first rotating member 10 or the second rotating member 20 with respect to the shaft 60. The design tolerance has to be set small, and the cost increases as the processing accuracy of the planetary balls 50A to 50H improves.

Therefore, the measured values of the radii r _b1 , r _b2 , r _b3 of the first to third reference balls 50A, 50B, 50C at the time of assembly are used. Thus, in this continuously variable transmission 1, performs the arrangement of the third reference ball 50A~50C from the first of the above, the error from the first with respect to a reference radius _{r b} of the third reference ball 50A~50C The amount of movement in the radial direction relative to the shaft 60 of the first rotating member 10 or the second rotating member 20 is set to be smaller. That is, when the continuously variable transmission 1 is assembled, when the first to third reference balls 50A to 50C are arranged as described above, the shaft 60 of the first rotating member 10 or the second rotating member 20 is used. First to third reference balls 50A to 50C having the above errors smaller than the movable amount in the radial direction with respect to are selected. Since the movable amount can be estimated in advance based on the design value, the estimated value may be used.

As a result, even if the first and second rotating members 10 and 20 and the input shaft 11 and the output shaft 21 are inclined by the first reference ball 50A, the first and second rotating members 10 corresponding to the inclination amounts. , 20 or the like in the radial direction with respect to the shaft 60 is smaller than the radial movable amount of the first rotating member 10 or the second rotating member 20 with respect to the shaft 60. At that time, than the largest error _(r b1 -r _b) a movable amount of the radial direction with respect to the shaft 60 of the first rotary member 10 and the second rotary member 20 with respect to a reference radius _{r b} of the first reference ball 50A Just make it smaller. Therefore, in this continuously variable transmission 1, since the uneven load is not applied to the radial bearings RB1 to RB4 and the thrust bearing TB, the torque of the continuously variable transmission 1 is larger than that corresponding only by the arrangement of the first to third reference balls 50A to 50C. The transmission efficiency and the durability of the radial bearings RB1 to RB4 and the thrust bearing TB can be improved. Further, in the continuously variable transmission 1, since it is not necessary to increase the processing accuracy of the planetary balls 50A to 50H, an increase in cost can be suppressed.

As described above, in the illustrated continuously variable transmission 1, the radially movable amount of the second rotating member 20 includes the radially movable amount of the first rotating member 10. This because, the error with respect to a reference radius r _b of the largest first reference ball 50A, may be smaller than the movable amount of the radial direction with respect to the shaft 60 of the first rotary member 10.

  In the illustrated continuously variable transmission 1, the outer rings of the radial bearings RB <b> 1 and RB <b> 2 are directly fitted on the output shaft 21, and the outer rings of the radial bearings RB <b> 3 and RB <b> 4 are directly fitted on the input shaft 11. However, depending on the continuously variable transmission, an annular member (not shown) is interposed between the outer ring of the radial bearings RB1 and RB2 and the output shaft 21, and the output shaft 21 is spline-fitted to the annular member by a spline. There are also things. Therefore, in the continuously variable transmission having such a spline fitting structure, the radial gap between the radial bearings RB1 and RB2 and the shaft 60 described above and the radially movable amount (maximum movement) of the spline. Amount), that is, the amount of radial movement of the output shaft 21 relative to the annular member is the amount of radial movement of the first rotating member 10 relative to the shaft 60. Further, there is no structure in which a second annular member (not shown) is interposed between the outer ring of the radial bearings RB3, RB4 and the input shaft 11, and the input shaft 11 is spline-fitted to the second annular member by the second spline. A step transmission is also conceivable. Therefore, in the continuously variable transmission having such a spline fitting structure, the movable amount of the first rotating member 10 includes the radial clearance between the radial bearings RB3, RB4 and the output shaft 21, and the spline. Is the sum of the radially movable amount (maximum movable amount) of the input shaft 11, that is, the radially movable amount of the input shaft 11 relative to the annular member, and the radially movable amount of the second rotating member 20 relative to the shaft 60. become.

Thus, according to the continuously variable transmission 1 and the assembly method of the continuously variable transmission 1, in addition to the arrangement of the acute triangles of the three first to third reference balls 50A to 50C, the first is made smaller than the movable amount of the radial direction with respect to the shaft 60 of the error first rotating member 10 and the second rotary member 20 with respect to a reference radius r _b of the third reference ball 50A~50C from the by its placement The amount of movement of the first and second rotating members 10 and 20 and the input shaft 11 and the output shaft 21 in the radial direction with respect to the shaft 60 of the first and second rotating members 10 and 20 and the like accompanying the inclination is suppressed. Can be made smaller than the radially movable amount of the first rotating member 10 and the second rotating member 20 with respect to the shaft 60. Therefore, according to the continuously variable transmission 1 and the assembly method of the continuously variable transmission 1, the radial bearings RB1 to RB4 and the thrust bearing TB are not subjected to an uneven load. In addition, the durability of the thrust bearing TB can be improved.

[Example 2]
Next, a second embodiment of the continuously variable transmission and the method for assembling the continuously variable transmission according to the present invention will be described with reference to FIGS.

  The present embodiment is a continuously variable transmission and a continuously variable transmission assembling method capable of improving the lubrication performance and cooling performance of the planetary ball 50 (50A to 50H). In this embodiment, the continuously variable transmission 1 having the same structure as that of the first embodiment will be described as an example.

  The lubricating performance and cooling performance are improved by supplying lubricating oil to the planetary balls 50 (50A to 50H). As a form of supplying the lubricating oil, for example, supply by scooping up the lubricating oil stored in the storage section on the lower side of the first and second rotating members 10 and 20, an oil pump such as a dry sump system (not shown) And the like, and supply by spraying the lubricating oil that has been sucked up or dripping from above the sprayed lubricating oil or the like.

  However, as described in the first embodiment, the planetary balls 50 </ b> A to 50 </ b> H vary in diameter one by one within the design tolerance. Accordingly, in each of the planetary balls 50A to 50H, even if lubricating oil is evenly supplied to all of the planetary balls 50A to 50H, the larger the diameter, the greater the distance from the first and second rotating members 10 and 20 and the sun roller 30. Since the pressing force is large, the lubrication performance and cooling performance are lowered. Thereby, the planetary ball (for example, the first to third reference balls 50A to 50C described above, and particularly the first reference ball 50A having the largest diameter) whose drive performance is reduced is reduced. And the durability of the first and second rotating members 10 and 20 and the sun roller 30 may be reduced. Therefore, in the continuously variable transmission 1, there is a possibility that an increase in driving loss and a decrease in durability may be caused as the lubrication performance and cooling performance of the planetary balls 50A to 50H are lowered.

  Therefore, in the continuously variable transmission 1 of the present embodiment, the first reference ball 50A having the largest diameter is located below the first rotation center axis R1, more preferably the lowermost of all the planetary balls 50A to 50H. To place. Here, the term “lower” refers to the lower side in the usage mode of the continuously variable transmission 1 (that is, when the vehicle is mounted). The first reference ball 50A may be arranged so that the center thereof is below the first rotation center axis R1, and a part above the center is located above the first rotation center axis R1. You may do it.

  As a result, the first reference ball 50A is supplied with lubricating oil dropped from above, such as the lubricating oil supplied to the case and the other planetary balls 50B to 50H, and the supply amount thereof increases. In particular, when the first reference ball 50A is disposed at the lowermost part, the supply amount of the lubricating oil is the largest as compared with the other planetary balls 50B to 50H. For this reason, the first reference ball 50A has improved lubrication performance and cooling performance. Accordingly, the continuously variable transmission 1 can suppress an increase in driving loss at the first reference ball 50A, and thus can improve the torque transmission efficiency. Further, the continuously variable transmission 1 can improve the durability of the first reference ball 50A.

  By the way, the carrier 40 of the first embodiment described above is illustrated as a rotating element capable of rotating relative to the shaft 60. For this reason, since all the planetary balls 50A to 50H revolve with the rotation of the carrier 40, the arrangement location of the first reference ball 50A changes. Therefore, in this embodiment, the carrier 40 is a fixed element that cannot rotate relative to the shaft 60 in the circumferential direction. For example, the carrier 40 of the present embodiment is such that relative rotation in the circumferential direction is achieved by spline fitting the inner peripheral surfaces of the first and second disk members 41 and 42 with the outer peripheral surface of the shaft 60. Is prohibited. Further, the carrier 40 may be regulated to relative rotation and relative movement by being press-fitted into the shaft 60.

  FIG. 5 is an example of the case where the first reference ball 50A is disposed at the lowermost part. In FIG. 5, the first reference ball 50A having the largest diameter is arranged at the lowermost part, and the second reference ball 50B having the next largest diameter is located below the first rotation center axis R1. Is arranged. Thereby, in this continuously variable transmission 1, not only the first reference ball 50A but also the second largest second reference ball 50B can be supplied with a larger amount of lubricating oil. Therefore, since the continuously variable transmission 1 can suppress an increase in driving loss at the second reference ball 50B, the torque transmission efficiency can be further improved. The continuously variable transmission 1 can also improve the durability of the second reference ball 50B.

  In the illustration of FIG. 5, the third reference ball 50C is arranged at the top, but if the main purpose is to improve the lubrication performance and cooling performance of the planetary balls 50A to 50H, the third reference ball 50C is The first and second reference balls 50A and 50B may be arranged at any location other than the arrangement location. Here, three first to third reference balls 50A to 50C satisfying the relationship of the following expression 1 are selected at the time of assembly, and the first to third reference balls 50A to 50C are expressed by the following expression 2 It may be arranged so as to satisfy the relationship.

r _b3 ≦ r _b2 ≦ r _b1 (1)
L1 ≦ L2 ≦ L3 (2)

  “L1” represents the distance between the traveling road surface of the vehicle and the center of the first reference ball 50A. “L2” represents the distance between the traveling road surface of the vehicle and the center of the second reference ball 50B. “L3” represents the distance between the traveling road surface of the vehicle and the center of the third reference ball 50C. “LC” represents the distance between the traveling road surface of the vehicle and the first rotation center axis R1.

  Due to the arrangement of the first to third reference balls 50A to 50C satisfying the relationship of the formulas 1 and 2, in the continuously variable transmission 1, the larger one of the first to third reference balls 50A to 50C decreases. Since it is arranged on the side, a larger amount of lubricating oil is supplied to the lower side. On the other hand, among the first to third reference balls 50A to 50C, the one having a smaller diameter (radius) is arranged on the upper side, so that the upper reference ball is lubricated more than the one arranged on the lower side. Although the amount of oil supplied is small, it is possible to suppress a decrease in lubrication performance and cooling performance. Therefore, according to the continuously variable transmission 1 and the assembly method of the continuously variable transmission 1, it is possible to suppress a decrease in drive loss and a decrease in durability. And according to this continuously variable transmission 1 and the assembly method of the said continuously variable transmission 1, torque transmission efficiency can be improved with the suppression of a drive loss fall.

In the illustration of FIG. 5, three first to third reference balls 50A to 50C form a right triangle. Therefore, in the continuously variable transmission 1, the inclination of the first and second rotating members 10, 20 and the like as in the first embodiment is generated. Therefore, the continuously variable transmission 1 of the present embodiment is the first reference ball having the largest diameter in the form of the first embodiment in which the three first to third reference balls 50A to 50C are arranged so as to form an acute triangle. It is preferable to arrange 50A so that the center thereof is located below the first rotation center axis R1, and more preferably, the first reference ball 50A is at the bottom of all the planetary balls 50A to 50H. . Further, the continuously variable transmission 1 of the present embodiment includes the reference of the first to third reference balls 50A to 50C in addition to the arrangement of the acute triangles of the three first to third reference balls 50A to 50C. in the embodiment example 1 is smaller than the movable amount of the radial direction with respect to the shaft 60 of the error with respect to the radius r _b first rotating member 10 and the second rotary member 20, the center of the first reference balls 50A having the largest diameter Is preferably arranged such that the first reference ball 50A is at the lowermost of all the planetary balls 50A to 50H so that the first reference ball 50A is located below the first rotation center axis R1. For example, the three first to third reference balls 50 </ b> A to 50 </ b> C may be arranged in the acute angle triangle of FIG. 4 described above.

  Here, in order to improve the torque transmission efficiency of the continuously variable transmission 1, the other second and third reference balls 50B and 50C are also disposed below the first rotation center axis R1, It is preferable to improve the lubrication performance and cooling performance. On the other hand, in order to improve the torque transmission efficiency of the continuously variable transmission 1 by suppressing the inclination of the first and second rotating members 10, 20 and the like, It is preferable to arrange one of the three first to third reference balls 50A to 50C on any one of the two and the other two on the other.

  Therefore, in the continuously variable transmission 1, the first and second first and second reference balls 50A and 50B are arranged in the descending order of the first rotation center axis R1 in order from the larger diameter. The third reference ball 50C is arranged so that the center thereof is located above the first rotation center axis R1, and the three first to third reference balls 50A to 50C form an acute angle triangle. To place. Therefore, in the continuously variable transmission 1, three first to third reference balls 50A to 50C that satisfy the relationship of the following expression 3 are selected during assembly. In the continuously variable transmission 1, the first to third reference balls 50 </ b> A to 50 </ b> C are arranged so as to form an acute triangle at a place satisfying the relationship of the following Expression 4. FIG. 6 illustrates an arrangement of the planetary balls 50A to 50H that satisfy the relations of the expressions 3 and 4 and in which the first to third reference balls 50A to 50C form an acute triangle.

r _b3 <r _b2 ≦ r _b1 (3)
L1 ≦ L2 <LC <L3 (4)

  In the continuously variable transmission 1, the first to third reference balls 50 </ b> A to 50 </ b> C are arranged with respect to the first reference ball 50 </ b> A that is likely to cause a reduction in driving loss and a decrease in durability. The largest amount of lubricating oil is supplied from the first to third reference balls 50A to 50C. In the continuously variable transmission 1, when the sizes of the first reference ball 50A and the second reference ball 50B are the same, they are arranged at the same height (L1 = L2), and the same amount of each is obtained. The lubricating oil can be supplied. In the continuously variable transmission 1, the center of the smallest third reference ball 50C among the three first to third reference balls 50A to 50C comes above the first rotation center axis R1. Therefore, the deterioration of the lubrication performance and cooling performance can be minimized. Further, in the continuously variable transmission 1, since the three first to third reference balls 50A to 50C are arranged to form an acute triangle, the first and second rotating members 10, 20 and the like are arranged. Uneven loads on the radial bearings RB1 to RB4 and the thrust bearing TB accompanying the inclination can be reduced. Therefore, according to the continuously variable transmission 1 and the assembling method of the continuously variable transmission 1, it is compared with the illustration of the arrangement of the first to third reference balls 50A to 50C that satisfy the relationship of the above formulas 1 and 2. Thus, the drive loss can be reduced by reducing the eccentric load of the radial bearings RB1 to RB4, etc., so that the drive loss can be further reduced, and the torque transmission efficiency is further improved.

Here, in the continuously variable transmission 1, the first to third reference balls 50A to 50C are arranged so as to satisfy the relationship of the above formulas 3 and 4 and form an acute triangle. as discussed, smaller than the movable amount of the from the first error with respect to a reference radius r _b of the third reference ball 50A~50C first rotating member 10 and the second radial direction with respect to the shaft 60 of the rotary member 20 It is preferable. As a result, no eccentric load is applied to the radial bearings RB1 to RB4 and the thrust bearing TB. Therefore, according to the continuously variable transmission 1 and the assembling method of the continuously variable transmission 1, the drive loss is further greatly reduced. As a result, torque transmission efficiency can be further improved.

  In the continuously variable transmission 1, when the storage portion is provided on the lower side of the first and second rotating members 10, 20, the center is located below the first rotation center axis R <b> 1. A part of the arranged reference balls may be immersed in the lubricating oil in the reservoir. In other words, during assembly, the lubricating oil may be accumulated up to the oil level at which the lower reference ball is immersed. Thereby, in this continuously variable transmission 1, the lubrication performance and cooling performance of the planetary balls 50A to 50H can be improved with a smaller amount of lubricating oil.

  By the way, in the above example, the carrier 40 in which the first disk member 41 and the second disk member 42 are connected and integrated by the connecting shaft is used, but the carrier is the first disk member 41 and the second disk member 42. May be arranged on the shaft 50 with a space equivalent to that of the carrier 40 without being connected by a connecting shaft. Further, in the carrier without the connecting shaft, one of the first or second disk members 41 and 42 is fixed so as not to rotate relative to the shaft 50, and the other is attached so as to be rotatable relative to the shaft 50. May be.

1 continuously variable transmission 10 first rotating member (first rotating element)
11 Input shaft 20 Second rotating member (second rotating element)
21 output shaft 30 sun roller (third rotating element)
40 Carrier (4th rotating element)
50 (50A-50H) Planetary ball (rolling member)
50A First reference ball 50B Second reference ball 50C Third reference ball 51 Support shaft 60 Shaft R1 First rotation center axis R2 Second rotation center axis RB1, RB2, RB3, RB4 Radial bearing TB Thrust bearing

Claims (10)

A transmission shaft as a center of rotation;
First and second rotational elements capable of relative rotation having a common first rotational center axis disposed opposite to each other on the transmission shaft;
A rolling member having a second rotation center axis parallel to the first rotation center axis, and a plurality of radial members arranged radially about the first rotation center axis and sandwiched between the first and second rotation elements When,
A support shaft of the rolling member having the second rotation center axis and projecting both ends from the rolling member;
A third rotating element that is arranged on an outer peripheral surface and capable of rotating relative to the transmission shaft and the first and second rotating elements;
A transmission that changes a rotation ratio between the first rotating element and the second rotating element by a tilting operation of each rolling member;
A fourth rotating element that is disposed on the transmission shaft and holds the end portions of the support shafts in a state in which the rolling members can be tilted;
In a continuously variable transmission equipped with
Among the rolling members, the first reference rolling member, the second reference rolling member, and the third reference rolling member are arranged in descending order of the shape, and the rolling members are the first to the third. The first to third reference rolling members arranged so that three lines connecting the respective rotation centers of the reference rolling members form an acute triangle, and the first to third reference rolling members A continuously variable transmission comprising: the remaining rolling members among the rolling members arranged in a space formed by arrangement . The radius when the design tolerance of each of the rolling members is ± 0 is set as a reference radius, and an error of the actual radius of the first to third reference rolling members with respect to the reference radius is defined as the first rotation element or the first rotation element. The continuously variable transmission according to claim 1, wherein the continuously variable transmission is smaller than a radially movable amount of the two-rotating element with respect to the transmission shaft.   The fourth rotation element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, and the first reference rolling member is arranged such that its center is located below the first rotation center axis in use. The continuously variable transmission according to claim 1 or 2, wherein the continuously variable transmission is provided.   The fourth rotation element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, and the first reference rolling member is disposed at the lowermost of the rolling members. 2. The continuously variable transmission according to 2.   The fourth rotation element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, and the first reference rolling member and the second reference rolling member are used in the center from the first rotation center shaft. The continuously variable transmission according to claim 1 or 2, wherein the continuously variable transmission is arranged so as to come to a lower side. A transmission shaft as a center of rotation;
First and second rotational elements capable of relative rotation having a common first rotational center axis disposed opposite to each other on the transmission shaft;
A rolling member having a second rotation center axis parallel to the first rotation center axis, and a plurality of radial members arranged radially about the first rotation center axis and sandwiched between the first and second rotation elements When,
A support shaft of the rolling member having the second rotation center axis and projecting both ends from the rolling member;
A third rotating element that is arranged on an outer peripheral surface and capable of rotating relative to the transmission shaft and the first and second rotating elements;
A transmission that changes a rotation ratio between the first rotating element and the second rotating element by a tilting operation of each rolling member;
A fourth rotating element that is disposed on the transmission shaft and holds the end portions of the support shafts in a state in which the rolling members can be tilted;
In the assembly method of the continuously variable transmission comprising:
A step of selecting each of the rolling members as a first reference rolling member, a second reference rolling member, and a third reference rolling member in descending order of shape,
The first to third reference rolling members are arranged so that three lines connecting the respective rotation centers of the selected first to third reference rolling members form an acute triangle, and An arrangement step of each rolling member for arranging the remaining rolling members among the rolling members in a space formed by the arrangement of the first to third reference rolling members ;
A method for assembling a continuously variable transmission. The radius as a reference radius when the design tolerance ± 0 in each rolling member, at selection step of the third reference rolling member from said first, actual radius of errors the first relative to the reference radius 7. The continuously variable transmission according to claim 6, wherein the first to third reference rolling members that are smaller than a radial movable amount of the rotating element or the second rotating element with respect to the transmission shaft are selected. Assembly method.   When the fourth rotation element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, the first reference rolling member is used in the center in the use state in the step of arranging each rolling member. 8. The continuously variable transmission assembling method according to claim 6, wherein the continuously variable transmission is disposed so as to be lower than the center axis of one rotation.   When the fourth rotating element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, the first reference rolling member is the highest among the rolling members in the step of arranging the rolling members. 8. The continuously variable transmission assembling method according to claim 6, wherein the continuously variable transmission is disposed at a lower portion.   In the case where the fourth rotating element is a fixed element that cannot rotate in the circumferential direction with respect to the transmission shaft, the first reference rolling member and the second reference rolling member are arranged in the step of arranging each rolling member. The method for assembling the continuously variable transmission according to claim 6 or 7, wherein the center of the continuously variable transmission is arranged so as to be located below the first rotation center axis in use.

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