JP2013145027A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission that can suppress prying in a socket-and-spigot connection part between both shafts while reducing a load on a bearing for supporting an input shaft or a variator shaft.SOLUTION: In a toroidal type continuously variable transmission, a variator shaft 1 is integrally connected to an input shaft 22 to be rotatably, an axial protruding part 1f of the variator shaft is fitted into an axial recess 22b of the input shaft 22 and supported so that the radial movement is restricted, and the support part is located the inside between two bearings 260, 262 for supporting the input shaft 22.

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 configured as shown in FIGS. 3 and 4 (two cavities 221 and 222 are shown in FIG. 3). As shown in FIG. 3, a variator shaft 1 is rotatably supported inside a casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the variator shaft 1. 3 is attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the variator 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 variator shaft 1 is rotationally driven by an input shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate 7 located on the left side in the drawing. . The output gear 4 is supported in the casing 50 via a partition wall 13 formed by coupling two members, so that the output gear 4 can rotate around the axis O of the variator shaft 1 while the axis O Directional displacement is prevented.

  The output side disks 3 and 3 are rotatably supported around an axis O of the variator shaft 1 by needle bearings 5 and 5 interposed between the output side disks 3 and 3. In addition, the input disk 2 on the left side in the figure is supported on the variator shaft 1 via a ball spline 6, and the input disk 2 on the right side in the figure is splined to the variator shaft 1. Rotates with the variator shaft 1. A power roller 11 (FIG. 4) is provided between the inner side surfaces (concave surfaces) 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. (See below) is rotatably held.

  A step 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 1b provided on the outer peripheral surface 1a of the variator shaft 1 is abutted against the step 2b. At the same time, the back surface (right surface in FIG. 3) of the input side disk 2 is abutted against the loading nut 9. As a result, the displacement of the input side disk 2 in the direction of the axis O relative to the variator shaft 1 is substantially prevented. Also, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the variator shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and the contact surface between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are applied with a pressing force.

  4 is a cross-sectional view taken along line EE 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 variator shaft 1 are provided inside the casing 50. In addition, illustration of the variator shaft 1 is abbreviate | omitted in FIG. Each trunnion 15, 15 is a pair of ends formed in the longitudinal direction (vertical direction in FIG. 4) of the support plate portion 16 that supports the power roller 11 in a state of being bent toward the inner surface side of the support plate portion 16. It has the bent wall parts 20 and 20. 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 central portion of the support plate portion 16, and the base end 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, a displacement shaft (shaft that supports the power roller 11 rotatably) is supported at the center of each trunnion 15, 15. Part) 23 can be adjusted. In addition, each power roller 11 is rotatably supported via a radial needle bearing 99 around the distal end 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 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 each other with respect to the variator 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 arrangement direction of the variator shaft 1. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the variator shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the variator 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 24 that is a thrust rolling bearing, and a thrust needle bearing, in order from the outer surface side of the power roller 11. 25. 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-type continuously variable transmission configured as described above, the rotation of the variator 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 the rotational speed ratio between the variator shaft 1 and the output gear 4 is changed, the pair of drive pistons 33 and 33 are displaced in directions opposite to each other. 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 (traction surfaces) 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a changes, and the gear ratio between the variator shaft 1 and the output gear 4 changes. To do. Further, when the torque transmitted between the variator shaft 1 and the output gear 4 fluctuates and the amount of elastic deformation of each constituent member changes, the power rollers 11 and 11 and the outer ring attached to the power rollers 11 and 11 are attached. 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 toroidal-type continuously variable transmission having the above-described configuration, the input shaft 22 directly connected to the engine (torque converter) and the variator shaft 1 are coupled by dog teeth (claws) 259 so that the variator shaft 1 moves in the axial direction. In the case of a structure that can be used, the support of the variator shaft 1 in the radial direction (support for regulating the movement of the variator shaft 1 in the radial direction) is such that the convex portion 22a on the input shaft 22 side is fitted in the concave portion 1e on the variator shaft 1 side. It is performed by joining (in-lobe coupling) or via a radial bearing (for example, see Patent Document 1).

Japanese Patent No. 4758809

  By the way, in the case of the support by the inlay as described above, the support portion (the inlay connecting portion between the convex portion 22a of the input shaft 22 and the concave portion 1e of the variator shaft 1) is more than between the support bearings 260 and 262 of the input shaft 22. It is located on the outside in the axial direction (rear side in FIG. 3). Therefore, the input shaft 22 has a cantilever structure, and the burden on the bearings 260 and 262 increases. Further, since the pressing device 12 is installed on the outer side of the concave portion 1e on the variator shaft 1, the inner diameter of the concave portion 1e is reduced by the load generated by the pressing device 12, and the convex portion 22a of the input shaft 22 and the variator shaft 1 are reduced. There is a possibility that a twist may occur between the concave portion 1e.

  The present invention has been made in view of the above circumstances, and can reduce the burden on the bearing that supports the input shaft or the variator shaft, and can suppress the twisting at the spigot joint between the shafts. An object is to provide a transmission.

In order to achieve the above object, a first aspect of the present invention includes an input shaft that transmits rotational driving force, and an axially displaceable variator shaft that is coupled to the input shaft and receives rotational force from the input shaft. And a pair of input side disks coupled to the variator shaft and rotating integrally with the variator shaft, and a rotational force of the input side disk at a predetermined speed ratio via a power roller provided between the input side disks. A double-cavity toroidal continuously variable transmission comprising an output-side disk for receiving,
The variator shaft is coupled so as to rotate integrally with the input shaft, and the axial convex portion is fitted and supported in the axial concave portion of the input shaft so that radial movement is restricted. The support portion is located inside the two bearings that support the input shaft.

The second aspect of the present invention includes an input shaft that transmits a rotational driving force, a variator shaft that is coupled to the input shaft and is axially displaceable to receive the rotational force from the input shaft, and the variator shaft. A pair of input-side disks that are coupled and rotate integrally with the variator shaft, and an output-side disk that receives the rotational force of the input-side disk at a predetermined gear ratio via a power roller provided between the input-side disks. A toroidal type continuously variable transmission of a double cavity type comprising:
The variator shaft is coupled so as to rotate integrally with the input shaft, and the axial convex portion of the input shaft is fitted to and supported by the axial concave portion so that the radial movement is restricted. The support portion is located inside the two bearings that support the variator shaft.

  In any of the above aspects, since the axial concavo-convex fitting support portion between the input shaft and the variator shaft is positioned inside the two bearings that support the shaft, the shaft does not have a cantilever structure, and therefore the bearing Can reduce the burden on In addition, since it does not become a cantilever structure, even when a pressing device is installed outside the shaft, it is twisted between the shafts (at the spigot joint between the two shafts) due to the load generated by the pressing device. Can be suppressed.

  According to the toroidal-type continuously variable transmission of the present invention, the axial concavo-convex fitting support portion between the input shaft and the variator shaft is positioned inside the two bearings that support the shaft. The burden on the bearings to be supported can be reduced and the twisting at the spigot joint between both shafts can be suppressed.

It is sectional drawing of the principal part of the toroidal type continuously variable transmission which concerns on the 1st Embodiment of this invention. It is sectional drawing of the principal part of the toroidal type continuously variable transmission which concerns on the 2nd Embodiment of this invention. It is sectional drawing which shows an example of the specific structure of the half toroidal type continuously variable transmission conventionally known. It is sectional drawing which follows the AA line of FIG.

Embodiments of the present invention will be described below with reference to the drawings.
The feature of the present invention lies in the coupling form between the input shaft and the variator shaft, and the other configurations and operations are the same as the conventional configurations and operations described above. Only the above will be referred to, and the other parts will be simply described with the same reference numerals as those in FIGS.

  FIG. 1 shows a first embodiment of the present invention. As shown in the figure, in the toroidal-type continuously variable transmission according to the present embodiment, the input shaft 22 is fastened to an engine or a starting device (torque converter, clutch) and supported by a radial bearing 260 and a deep groove ball bearing 262. ing. The input shaft 22 and the variator shaft 1 are fastened in the direction of rotation by pawls (dog teeth) 400 (the variator shaft 1 is coupled so as to rotate integrally with the input shaft 22), but due to deformation of the variator components Since the variator shaft 1 moves in the axial direction, the axial direction is not restricted.

  The radial direction regulation of the variator shaft 1 is supported by the casing 50 on the rear side via a radial bearing 312, and the front side is provided with a hole (axial recess) in the input shaft 22 and an axis (axial projection) in the variator shaft 22. As an inlay, it is supported via a radial bearing. That is, the variator shaft 1 is supported by fitting its axial convex portion 1 f into the axial concave portion 22 b of the input shaft 22 so that the radial movement is restricted. At this time, the support portion S is located inside the two support bearings 260 and 262 of the input shaft 22.

  Moreover, the toroidal type continuously variable transmission of this embodiment is a double cavity type, the variator shaft 1 is connected with the input side disk 2, and the pressing device 12 is installed in the front side.

  When the support portion S of the variator shaft 1 on the front side is positioned inside the support bearings 260 and 262 of the input shaft 22 with the above-described structure, the load on the bearings 260 and 262 with respect to the radial load is reduced. Is done. Further, since the variator shaft 1 side is supported by the inlay, the inlay portion of the inlay portion with respect to the moment M pressing the variator shaft 1 inward due to the thrust load generated by the pressing device 12 as in the conventional structure described above. There is no risk of the hole side being deformed and causing a twist or the like.

  FIG. 2 shows a second embodiment of the present invention. As shown in the figure, in the toroidal-type continuously variable transmission according to the present embodiment, the input shaft 22 is fastened to an engine or a starting device (torque converter, clutch), and a radial bearing and a deep groove as in the first embodiment. It is supported by a ball bearing.

  Further, the input shaft 22 and the variator shaft 1 are fastened in the direction of rotation by claws (splines) 402 (the variator shaft 1 is coupled so as to rotate integrally with the input shaft 22), but the variator components are deformed. Therefore, since the variator shaft 1 moves in the axial direction, the axial direction is not restricted.

  In the radial direction regulation of the variator shaft 1, the rear side is supported by the casing 50 via the radial bearing 312, and the front side is provided with a hole (axial recess 1e) in the variator shaft 1 and the input shaft 22 as an axis (axial projection). 22a) is an inlay and is supported via a radial bearing (needle bearing) 310 (this allows the variator shaft 1 to move in the axial direction). That is, the variator shaft 1 is supported by fitting the axial convex portion 22a of the input shaft 22 to the axial concave portion 1e so that the radial movement is restricted. At this time, the support portion S is located inside the two support bearings 310 and 312 of the variator shaft 1.

  Moreover, the toroidal type continuously variable transmission of this embodiment is a double cavity type, the variator shaft 1 is connected with the input side disk 2, and the pressing device 12 is installed in the front side.

  Therefore, even in the above configuration, since the support portion S of the input shaft 22 on the front side is inside the support bearings 310 and 312 of the variator shaft 1, the burden on the bearing with respect to the radial load is reduced.

  The present invention can be applied to various types of half-toroidal continuously variable transmissions.

DESCRIPTION OF SYMBOLS 1 Variator shaft 1e Axial recessed part 1f Axial convex part 2 Input side disk 3 Output side disk 11 Power roller 22 Input shaft 22a Axial convex part 22b Axial recessed part 260,262,310,312 Bearing

Claims (2)

An input shaft for transmitting a rotational driving force, a variator shaft coupled to the input shaft and axially displaceable receiving the rotational force from the input shaft, and a pair coupled to the variator shaft and rotating integrally with the variator shaft Double-cavity toroidal continuously variable transmission comprising: an input-side disk; and an output-side disk that receives the rotational force of the input-side disk at a predetermined speed ratio via a power roller provided between the input-side disk Because
The variator shaft is coupled so as to rotate integrally with the input shaft, and the axial convex portion is fitted and supported in the axial concave portion of the input shaft so that radial movement is restricted. The toroidal continuously variable transmission is characterized in that the support portion is positioned inside the two bearings that support the input shaft. An input shaft that transmits rotational driving force, a variator shaft that is coupled to the input shaft and is axially displaceable to receive rotational force from the input shaft, and a pair that is coupled to the variator shaft and rotates integrally with the variator shaft Double-cavity toroidal continuously variable transmission comprising: an input-side disk; and an output-side disk that receives the rotational force of the input-side disk at a predetermined speed ratio via a power roller provided between the input-side disk Because
The variator shaft is coupled so as to rotate integrally with the input shaft, and the axial convex portion of the input shaft is fitted to and supported by the axial concave portion so that the radial movement is restricted. The toroidal-type continuously variable transmission is characterized in that the support portion is located inside the two bearings that support the variator shaft.

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