JP2015222083A - Toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal continuously variable transmission capable of achieving size reduction and weight reduction by shortening the axial length between traction surfaces of an integral inner disc that includes two traction surfaces and an outer circumferential gear.SOLUTION: A toroidal continuously variable transmission comprises an integral output-side disc 3B in which a pair of output-side discs 3, 3 is integrated with an output gear 4B. An axial length L1 that is a length of the output gear 4B of the integral output-side disc 3B along an axial direction is larger than an axial length L2 that is a length between outer circumferential portions of a pair of traction surfaces 3a of the integral output-side disc 3B along an axial direction. It is thereby possible to reduce the axial length and weight of the toroidal continuously variable transmission.

Description

  The present invention relates to a toroidal continuously variable transmission that can be used for transmissions of automobiles and various industrial machines.

For example, a double-cavity toroidal continuously variable transmission used as a transmission for an automobile is known.
This double cavity type toroidal continuously variable transmission is configured as shown in FIGS. As shown in FIG. 3, an input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the input shaft 1. 3 is attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

  The input shaft 1 is driven to rotate by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate (loading cam) 7 located on the left side in the drawing. It has become. The output gear 4 is supported in the casing 50 via an intermediate wall 13 formed by coupling two members, whereby the output gear 4 can rotate around the axis O of the input shaft 1 while the axis O Directional displacement is prevented.

  The output side disks 3 and 3 are supported by needle bearings 5 and 5 interposed between the input shaft 1 so as to be rotatable about the axis O of the input shaft 1. Further, the left input side disk 2 in the figure is supported on the input shaft 1 via a ball spline 6, and the right side input disk 2 in the figure is splined to the input shaft 1. Rotates with the input shaft 1. Further, there is power between the inner side surfaces (concave surface; also referred to as a traction surface) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surface; also referred to as a traction surface) 3a and 3a of the output side disks 3 and 3. A roller 11 (see FIG. 4) is rotatably held.

  A step portion 2b is provided on the inner peripheral surface 2c of the input side disk 2 located on the right side in FIG. 3, and the step portion 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step portion 2b. At the same time, the back surface (right surface in FIG. 3) of the input side disk 2 is abutted against a loading nut 9 screwed into a screw portion formed on the outer peripheral surface of the input shaft 1. Thereby, the displacement of the input side disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and a pressing portion (preload) is applied to a contact portion between the peripheral surfaces 11a and 11a of the power rollers 11 and 11.

  4 is a cross-sectional view taken along line AA in FIG. As shown in FIG. 4, a pair of trunnions 15, 15 that swing about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In FIG. 4, the input shaft 1 is not shown. Each trunnion 15, 15 is a pair of bent wall portions 20, 20 formed at both ends in the longitudinal direction (vertical direction in FIG. 4) of the support plate portion 16 so as to be bent toward the inner surface side of the support plate portion 16. have. The bent wall portions 20 and 20 form concave pocket portions P for accommodating the power rollers 11 in the trunnions 15 and 15. Further, the pivot shafts 14 and 14 are concentrically provided on the outer side surfaces of the bent wall portions 20 and 20, respectively.

  A circular hole 21 is formed in the center portion of the support plate portion 16, and a base end portion (first shaft portion) 23 a of the displacement shaft 23 is supported in the circular hole 21. Then, by swinging each trunnion 15, 15 about each pivot 14, 14, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. In addition, each power roller 11 is rotatably supported around the tip end portion (second shaft portion) 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  The pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable and displaceable in the axial direction (vertical direction in FIG. 4) with respect to the pair of yokes 23A and 23B, respectively. The horizontal movement of the trunnions 15 and 15 is restricted by 23B. Each yoke 23A, 23B is formed in a rectangular shape by pressing or forging a metal such as steel. Four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B, and the pivot shafts 14 provided at both ends of the trunnion 15 swing through the radial needle bearings 30. It is supported freely. In addition, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (the left-right direction in FIG. 3), and the inner peripheral surface of the locking hole 19 is a cylindrical surface. 64 and 68 are fitted inside. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical post 68 and the drive for supporting the same. The upper cylinder body 61 of the cylinder (cylinder body) 31 is swingably supported.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying an excessive force to the member.

  Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing (thrust bearing) 24 that is a thrust rolling bearing is sequentially formed from the outer surface side of the power roller 11. A thrust needle bearing 25 is provided. Among these, the thrust ball bearing 24 supports the rotation of each power roller 11 while supporting the load in the thrust direction applied to each power roller 11. Each of such thrust ball bearings 24 includes a plurality of balls (hereinafter referred to as rolling elements) 26, 26, an annular retainer 27 that holds the rolling elements 26, 26 in a freely rolling manner, And an annular outer ring 28. Further, the inner ring raceway of each thrust ball bearing 24 is formed on the outer side surface (large end surface) of each power roller 11, and the outer ring raceway is formed on the inner side surface of each outer ring 28.

  The thrust needle bearing 25 is sandwiched between the inner surface of the support plate portion 16 of the trunnion 15 and the outer surface of the outer ring 28. Such a thrust needle bearing 25 supports the thrust load applied to each outer ring 28 from the power roller 11, while the power roller 11 and the outer ring 28 swing around the base end portion 23 a of each displacement shaft 23. Allow.

  Further, driving rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 4) of the trunnions 15 and 15, respectively, and a driving piston ( Hydraulic pistons) 33, 33 are fixed. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to the input side disks 2 and 2 via the pressing device 12. Then, the rotation of the input side disks 2 and 2 is transmitted to the output side disks 3 and 3 via the pair of power rollers 11 and 11, and the rotation of the output side disks 3 and 3 is further transmitted to the output gear 4. It is taken out more.

  When changing the rotational speed ratio between the input shaft 1 and the output gear 4, the pair of drive pistons 33, 33 are displaced in opposite directions. As the drive pistons 33 and 33 are displaced, the pair of trunnions 15 and 15 are displaced in directions opposite to each other. For example, the power roller 11 on the left side in FIG. 4 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure.

  As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing (tilt) in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the rotational speed ratio between the input shaft 1 and the output gear 4 changes. Further, when the torque transmitted between the input shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each component changes, the power rollers 11 and 11 and the outer rings attached to the power rollers 11 and 11 will be described. 28 and 28 slightly rotate around the base end portions 23a and 23a of the displacement shafts 23 and 23, respectively. Since the thrust needle bearings 25 and 25 exist between the outer side surfaces of the outer rings 28 and 28 and the inner side surfaces of the support plate portions 16 constituting the trunnions 15 and 15, respectively, the rotation is performed smoothly. Is called. Therefore, as described above, the force for changing the inclination angle of each displacement shaft 23, 23 can be small.

  By the way, in the double cavity type toroidal continuously variable transmission, as shown in FIG. 5, the back surfaces of the pair of output side disks 3 and 3 arranged between the pair of input side disks 2 and 2 are joined together. In addition, a pair of output-side disks 3 and 3 are integrated, and an integrated output-side disk 3A which is an output gear 4A provided with outer peripheral teeth on the outer peripheral surface of the integrated output-side disks 3 and 3 is used. (For example, see Patent Documents 1 to 4). In the toroidal type continuously variable transmissions described in Patent Documents 1 to 3, the integrated output side disk 3A is provided on each of the traction surfaces (inner side surfaces) of the pair of input side disks 2 and 2 on both sides of one member. A pair of traction surfaces (inner side surfaces 3a, 3a) opposed to 2a, 2a) are formed, and teeth are formed on the outer peripheral portion of the member to form an output gear 4A. Further, in the toroidal type continuously variable transmission described in Patent Document 4, a pair of output side disks 3 and 3 having outer peripheral teeth serving as output gears on the outer peripheral portion are integrated by welding, and an output gear 4A is provided on the outer peripheral portion. The body output side disk 3A is used.

  In addition, the pair of output side disks 3 and 3 formed separately are joined together, and the output gear 4A provided separately is joined to the outer peripheral portion thereof, so that the pair of output side disks 3 and 3 and A toroidal-type continuously variable transmission that uses the output gear 4A as one member has been proposed (see, for example, Patent Document 5).

  In the toroidal-type continuously variable transmission shown in FIG. 5, instead of the displacement shaft 23 that supports the power roller 11 so as to be rotatable and swingable, the outer ring 28 of the thrust ball bearing 24 that receives the thrust load of the power roller 11 is used. An integrally formed support shaft 23c is used. Therefore, the power roller 11 is swung by the displacement shaft 23 so as not to be displaced along the substantially axial direction of the input shaft 1. Instead, the inner side surface of the support plate portion 16 of the trunnion 15 is a part of a convex cylindrical surface along the axial direction of the pivot 14. Further, on the back side of the outer ring 28 facing the inner side surface of the support plate portion 16, a concave cylindrical surface that abuts against the protruding cylindrical surface of the support plate portion 16 is provided. The power roller 11 can swing along the substantially axial direction of the input shaft 1 by swinging with the power roller 11 so as to swing the head.

Japanese Unexamined Patent Publication No. 2013-177909 JP 2013-167344 A JP 2013-117237 A Japanese Patent Application Laid-Open No. 2005-048880 Japanese Patent No. 4254029

  By the way, in the toroidal type continuously variable transmission described in Patent Document 5, the inner peripheral portion of the output gear 4A provided on the outer peripheral portion is sandwiched between the pair of output side disks 3 and 3 and joined. Since the integrated output side disk 3A is used, fretting wear may occur on the surface of the pair of output side disks 3 and 3 that sandwich the output gear 4A. Further, since the output gear 4A is formed separately from the output side disks 3 and 3, and then joined to the output side disks 3 and 3, the output gear 4A may be increased in size.

  Further, like the toroidal type continuously variable transmission described in Patent Documents 1 to 3, teeth are provided on the outer peripheral portion of the output side disks 3 and 3 formed integrally from the beginning, and the output gear 4A is also integrated. In the body output side disk 3A, for example, as shown in FIG. 6, the axial dimension (thickness along the axial direction) of the outermost periphery of the traction surface is the axial dimension of the output gear 4A provided on the outer periphery thereof. Or the dimensions have been increased. In FIG. 6 and FIG. 1 to be described later, approximately half of the integrated output side discs 3A and 4A is illustrated as a boundary.

  In order to transmit a large torque or to suppress noise by increasing the meshing rate, it is difficult to reduce the axial dimension of the output gear 4A, and accordingly, a pair of traction of the integrated output side disk The axial dimension at the outermost peripheral portion of the surface is also determined. In this case, since the axial dimension of the input shaft 1 of the toroidal-type continuously variable transmission is affected by the axial dimension of the integrated output-side disk 3A, it is difficult to reduce the axial length. . Further, if the integrated output side disk 3A has a solid structure, if the axial dimension of the integrated output side disk 3A increases, the thickness of the integrated output side disk 3A increases and the weight increases. turn into.

  The present invention has been made in view of the above circumstances, and shortens the axial length between traction surfaces in an integrated inner disk having two traction surfaces and an outer peripheral gear, thereby reducing the size and weight. It is an object of the present invention to provide a toroidal continuously variable transmission that can be used.

To achieve the above object, a toroidal continuously variable transmission according to the present invention is provided concentrically and provided concentrically between a pair of outer disks each having a traction surface and the pair of outer disks. An inner disk having a pair of traction surfaces respectively facing the traction surfaces of the pair of outer disks, and a power roller sandwiched between the traction surfaces facing each other,
In the toroidal continuously variable transmission in which the inner disk is provided with the traction surfaces on both side surfaces, and the outer peripheral gears are provided by providing teeth on the outer peripheral side by side in the circumferential direction.
The length along the axial direction of the inner disk between the outermost peripheral portions of the pair of traction surfaces of the inner disk is shorter than the length along the axial direction of the outer peripheral gear.

According to such a configuration, the axial dimension between the outermost peripheral portions of the pair of traction surfaces of the inner disk (the length along the axial direction) is shortened, thereby reducing the thickness of the inner disk. Can be reduced in weight.
Further, if the distance between the pair of traction surfaces of the inner disk is shortened, the distance between the pair of outer disks can be shortened by the shortened length.
For these reasons, it is possible to reduce the axial dimension and to reduce the weight of the toroidal-type continuously variable transmission.

  Further, when the distance between the pair of traction surfaces of the inner disk is narrowed, in the double cavity type toroidal continuously variable transmission, the axial dimension between the two sets of power rollers arranged in each cavity is also reduced. As a result, the axial direction of the input shaft, the upper and lower yokes, the upper and lower cylinder bodies, the upper plate (fixing member) and the like as peripheral components whose axial dimension changes in the same manner as the axial dimension of the interval between the two power rollers changes. Since the size is reduced, the weight can be further reduced.

  ADVANTAGE OF THE INVENTION According to this invention, size reduction and weight reduction of a toroidal type continuously variable transmission can be achieved.

It is principal part sectional drawing which shows the integrated output side disk of the toroidal type continuously variable transmission which concerns on embodiment of this invention. It is an enlarged view of the part shown with the code | symbol A of FIG. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission. It is sectional drawing which follows the AA line in FIG. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission provided with an integrated output side disk. It is principal part sectional drawing which shows the conventional integrated type output side disk.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The toroidal type continuously variable transmission of this embodiment is characterized by the structure of an integrated output side disk (inner disk) 3B, and the other configurations are the same as those of the toroidal type continuously variable transmission shown in FIGS. Since it is substantially the same, the said characteristic is demonstrated in detail below.

  As shown in FIGS. 1 and 2, the integrated output side disk 3B has traction surfaces 3a and 3a on both side surfaces, respectively, and an outer peripheral portion is an output gear (outer gear) 4B. Further, a through hole 3b through which the input shaft 1 passes is formed in the central portion of the integrated output side disk 3B along the axial direction.

The integrated output-side disk 3B has a general shape in which two substantially frustoconical members are arranged in opposite directions so that the large-diameter side ends are opposed to each other and coaxially arranged. The cross-sectional shape of the peripheral surface is a concave arc of a predetermined radius of curvature, and the surface where the cross-section is a concave arc is the traction surface (inner side surface 3a).
Further, in the integrated output side disk 3B, the output gear 4B is integrally provided at a portion outside the outermost peripheral portion (outer peripheral edge) of the traction surface 3a. The traction surface 3a and the output gear 4B are originally provided in one member. For example, the pair of output side disks 3 and 3 and the output gear 4 are manufactured separately and then joined together. It was n’t. The output gear 4B of the present embodiment and the conventional output gear 4A are helical gears.

  In the present embodiment, as shown in FIG. 1, the axial dimension L1 which is the length along the axial direction of the output gear 4B portion of the integrated output side disk 3B is a pair of tractions of the integrated output side disk 3B. It is longer than the axial dimension L2 which is the length along the axial direction in the outermost peripheral part of the surface 3a. In other words, the axial dimension L2 is shorter than the axial dimension L1.

  Here, the conventional integrated output disk 3B shown in FIG. 6 and the integrated output disk 3B of the present embodiment will be compared to describe the integrated output disk 3B of the present embodiment. The conventional integrated output side disk 3A shown in FIG. 6 and the integrated output side disk 3B shown in FIG. 1 have the same outer diameter, and the teeth of the output gears 4A and 4B have the same shape. The axial dimension L3 of the conventional output gear 4A and the axial dimension L1 of the output gear 4B of the present embodiment are the same. Further, the basic shape such as the radius of curvature of the cross section of the traction surfaces 3a and 3a is the same between the conventional integrated output side disk 3A and the integrated output side disk 3B of the present embodiment. On the other hand, from the axial dimension L4 that is the length along the axial direction between the outermost peripheral portions of the pair of traction surfaces 3a, 3a of the conventional integrated output side disk 3A, the integrated output side of the present embodiment. The axial dimension L2 of the pair of traction surfaces 3a, 3a of the disk 3B is shortened.

  However, in the integrated output side disk 3B of the present embodiment, an annular flat surface portion 3d having a radial width is provided at the boundary portion between the side surface 4b of the output gear 4B and the traction surface 3a as described later. ing. Therefore, the diameter of the outermost periphery of the traction surface 3a of the integrated output side disk 3B of the present embodiment is slightly smaller than the diameter of the outermost periphery of the traction surface 3a of the conventional integrated output side disk 3A. . It should be noted that the radial position at which the axial dimensions L2 and L4 of the outermost peripheral portion of the traction surface 3a of the integrated output side disks 3A and 3B are measured is the outer peripheral edge of the traction surface 3a of the integrated output side disk 3B of the present embodiment. A radial position of (a boundary with the plane portion 3d).

  In the conventional integrated output side disk 3A shown in FIG. 6, the traction surfaces 3a, 3a and the side surface 4c of the output gear 4A are continuous at the boundary between the traction surfaces 3a, 3a and the side surface 4c of the output gear 4A. There is no step.

  On the other hand, in the toroidal continuously variable transmission according to the present embodiment shown in FIGS. 1 and 2, the axial direction of the outermost peripheral portions of the pair of traction surfaces 3a is determined from the axial dimension L1 of the output gear 4B as described above. The dimension L2 is shortened, and a step 3e is formed at the boundary between the traction surfaces 3a and 3a and the side surface 4b of the output gear 4B. In this case, with respect to the distance L6 between the center positions C and C of the radius of curvature R of each of the pair of traction surfaces 3a and 3a in the cross section of the conventional integrated output side disk 3A, the integrated output side of the present embodiment. The distance L5 between the center positions C and C of the curvature radii R of the pair of traction surfaces 3a and 3a in the cross section of the disk 3B is shortened. Here, the conventional curvature radius R of the cross section of the traction surface 3a is the same as the curvature radius R of the present embodiment.

  Further, as described above, in the integrated output side disk 3B, between the outermost periphery of the traction surface 3a and the innermost periphery of the side surface 4b of the output gear 4B, that is, between the traction surface 3a and the step 3e. Is provided with the above-described flat surface portion 3d orthogonal to the axial direction of the integrated output side disk 3B.

  Here, in the manufacturing process of the integrated output side disks 3A and 3B, there is a process of polishing the traction surfaces 3a and 3a with a grindstone (not shown). The grindstone has a convex arc shape in which the cross-sectional shape of the outer peripheral surface thereof has a curvature radius substantially the same as the curvature radius of the traction surface 3a. The grindstone has a shape that is circularly symmetric with respect to the central axis. Since the grindstone grinds the entire traction surface 3a, the length of the arc of the cross section of the outer peripheral surface of the grindstone needs to be wider than the length of the arc of the cross section of the traction surface 3a. In FIG. 2, the broken line extending from the solid line indicating the traction surface 3a indicates a part of the end side of the outer peripheral surface of the cross section of the grindstone for polishing the traction surface 3a. This indicates that the arc of the cross section of the outer peripheral surface is longer and that the grindstone is not in contact with the corner 3g of the output gear 4B.

  In the integrated output side disk 3B, if the inner peripheral edge of the side surface 4b of the output gear 4B and the outer peripheral edge of the traction surface 3a coincide with each other, and there is a step in this portion, the outer periphery of the grindstone is placed on the traction surface 3a when polishing with the grindstone. When trying to make the surface contact, the outer peripheral surface of the grindstone hits the corner 3g of the stepped corner in the cross section of the output gear 4B, and the outer peripheral surface of the grindstone cannot be brought into contact with the traction surface 3a. That is, polishing with a grindstone becomes difficult.

  Therefore, as shown in FIG. 2, the outer peripheral edge of the traction surface 3a is between the inner peripheral edge (innermost peripheral part: step 3e) of the side surface 4b of the output gear 4B and the outer peripheral edge (outermost peripheral part) of the traction surface 3a. By providing the flat surface portion 3d as a structure for opening a distance from the inner peripheral edge of the side surface 4b of the output gear 4B, the grindstone comes into contact with the inner peripheral edge (corner portion 3g) of the side surface 4b of the output gear 4B. It is preventing.

  In the present embodiment, not only the flat surface portion 3d is provided, but also the chamfered corner portion 3g of the step 3e portion of the side surface 4b of the output gear 4B makes contact between the grindstone and the output gear 4B. Is preventing.

  In such a toroidal-type continuously variable transmission, a pair of traction surfaces 3a as described above is compared with the conventional integrated output-side disk 3A including the output gear 4A having the same diameter and the same axial dimension L3. 3a, the distance L5 between the center positions C and C of the respective curvature radii R is shortened, so that the distance along the axial direction of the power roller 11 of each cavity is shortened and the axis between the pair of input side disks 2 and 2 is reduced. The distance along the direction is shortened. Thereby, in the toroidal type continuously variable transmission, it is possible to reduce the size in the axial direction.

Further, the integrated output side disk 3B is reduced in weight because the thickness is substantially reduced, and the weight of the toroidal type continuously variable transmission can be reduced.
Further, as described above, even if the axial dimension L1 between the both side surfaces 4b, 4b of the output gear 4B is longer than the axial dimension L2 between the outermost peripheral portions of the pair of traction surfaces 3a, 3a, as described above. By providing a space between the outer peripheral edge of the surfaces 3a and 3a and the inner peripheral edge of the side surfaces 4b and 4b, the grinding stone does not come into contact with the output gear 4B when the traction surfaces 3a and 3a by the grinding stone are polished. can do.

  Further, when the distance between the pair of traction surfaces 3a, 3a of the integrated output side disk 3B becomes narrow, in the double cavity type toroidal continuously variable transmission, the shaft between the two sets of power rollers 11 arranged in each cavity. The directional dimension is also reduced. As a result, when the axial dimension of the distance between the two sets of power rollers 11 is changed, the input shaft 1, the upper and lower yokes 23A and 23B, the upper and lower cylinder bodies 61 and 62, the upper plate ( Since the axial dimensions of the fixing member 52) and the like are reduced, the weight can be further reduced.

  If the distance between the outer peripheral edge of the traction surface 3a and the inner peripheral edge (step 3e) of the side surface 4b is increased when the diameter of the integrated output side disk 3B is not changed, the shaft on the outer peripheral side of the step 3e of the output gear 4B is increased. Since the width along the radial direction of the portion protruding in the direction becomes too thin or the diameter of the outer peripheral edge of the traction surface 3a becomes too small, it is preferable to determine the above-mentioned distance in consideration of these. Further, in consideration of the above-mentioned distance, in order to prevent the grindstone from coming into contact with the output gear 4B, the axial dimension L2 of the outer peripheral edge portion of each of the traction surfaces 3a, 3a and the traction surfaces 3a, 3a It is preferable to determine the distance L5 between the center positions C and C of the radius of curvature R. In addition, the shape between the outer peripheral edge of the traction surface 3a and the inner peripheral edge (step 3e) of the side surface 4b is not necessarily a plane orthogonal to the axial direction as in the flat portion 3d, but when polishing with a grindstone, It is necessary that there is no portion protruding so as to contact the outer peripheral surface of the grindstone, and it is preferable to draw in from the above-described broken line in FIG.

  Further, in the double cavity type toroidal continuously variable transmission, the output side disks 3 and 3 can be configured as outer disks, and the input side disks 2 and 2 can be configured as inner disks. In the toroidal type continuously variable transmission, An integrated input-side disk in which the pair of input-side disks 2 and 2 and the outer peripheral gear are integrated may be used as the inner disk.

  The present invention can be applied to a double cavity type full toroidal continuously variable transmission as well as various double cavity type continuously variable transmissions.

2 Input disc (outer disc)
2a Inner surface (traction surface)
3B Integrated output disk (inner disk)
3a Inner surface (traction surface)
4B Output gear (peripheral gear)
11 Power Roller

Claims (1)

A pair of outer disks provided concentrically and each having a traction surface, and a pair of traction surfaces provided concentrically between the pair of outer disks and opposed to the traction surfaces of the pair of outer disks, respectively. An inner disk, and a power roller sandwiched between the traction surfaces facing each other,
In the toroidal continuously variable transmission in which the inner disk is provided with the traction surfaces on both side surfaces, and the outer peripheral gears are provided by providing teeth on the outer peripheral side by side in the circumferential direction.
The length along the axial direction of the inner disk between the outermost peripheral parts of the pair of traction surfaces of the inner disk is shorter than the length along the axial direction of the outer peripheral gear. Step transmission.

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