JP2008215547A - Toroidal continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal continuously variable transmission in which the fixing strength of a post is sufficiently secured without being affected by the structure of a hydraulic mechanism having a drive piston and a cylinder. <P>SOLUTION: In this toroidal continuously variable transmission, fixing centers O4, O5 through which the fixing center axes L2, L2' of bolts 310a, 310b pass are offset from a center point O3 between the chamber center points O1, O2 through which two chamber center axes L1, L1' pass in the direction perpendicular to the fixing center axes L2, L2' (axial direction of an input shaft 1) in the vertical plane P2 vertical to the plane P1 including both the chamber center axes L1, L1' of two cylinder chambers 31a, 31a'. <P>COPYRIGHT: (C)2008,JPO&INPIT

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. As shown in FIG. 5, 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 on a partition wall (intermediate wall) 13 formed by coupling two members via an angular ball bearing 107 and is supported in the casing 50 via the partition wall 13. Thus, while being able to rotate around the axis O of the input shaft 1, displacement in the direction of the axis O 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. A power roller is provided 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 disks 3 and 3. 11 (see FIG. 6) 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. 5, and the step 1b provided on the outer peripheral surface 1a of the input shaft 1 is abutted against the step 2b. At the same time, the back surface (right surface in FIG. 5) 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 the contact surface between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are applied with a pressing force.

  As shown in FIG. 6 which is a cross-sectional view taken along the line AA in FIG. 5, both the disks 3 and 3 are sandwiched from both sides inside the casing 50 and at the side positions of the output side disks 3 and 3. The pair of yokes 23A and 23B is supported in the state. The pair of yokes 23A and 23B are formed in a rectangular shape by pressing or forging a metal such as steel. In order to support pivots 14 provided at both ends of the trunnion 15 to be described later in a swingable manner, circular support holes 18 are provided at the four corners of the yokes 23A and 23B, and the width direction of the yokes 23A and 23B. A circular locking hole 19 is provided at the center of the.

  The pair of yokes 23A and 23B is supported by support posts 64 and 68 formed on the inner surface of the casing 50 so as to be able to swing around the support posts 64 and 68 as fulcrums. These support posts 64 and 68 are provided so as to face the first cavity 221 and the second cavity 222, respectively, between the inner side surface 2a of the input side disk 2 and the inner side surface 3a of the output side disk 3. Yes.

  Therefore, the yokes 23 </ b> A and 23 </ b> B are supported by the support posts 64 and 68, and one end thereof faces the outer peripheral portion of the first cavity 221, and the other end faces the outer peripheral portion of the second cavity 222. is doing.

  Since the first and second cavities 221 and 222 have the same structure, only the first cavity 221 will be described below.

  As shown in FIG. 6, inside the casing 50, the first cavity 221 includes a pair of trunnions that swing about a pair of pivots (tilting axes) 14 and 14 that are twisted with respect to the input shaft 1. 15 and 15 are provided. In addition, illustration of the input shaft 1 is abbreviate | omitted in FIG. Each trunnion 15, 15 is a pair of bent portions formed at both ends in the longitudinal direction (vertical direction in FIG. 6) of the support plate portion 16 that is the main body portion so as to be bent toward the inner surface side of the support plate portion 16. Wall portions 20 and 20 are provided. Then, the trunnions 15 and 15 form a pocket portion P that is a concave accommodation space for accommodating the power roller 11 by the bent wall portions 20 and 20. 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 a base end portion (first shaft portion) 23 a of a displacement shaft 23 as a support shaft 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.

  As described above, the pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable with respect to the pair of yokes 23A and 23B and to be displaceable in the axial direction (vertical direction in FIG. 6). The trunnions 15 and 15 are restricted from moving in the horizontal direction by the yokes 23A and 23B. As described above, four circular support holes 18 are provided at the four corners of each of the yokes 23A and 23B, and the pivot shafts 14 provided at both ends of the trunnion 15 are respectively provided in the support holes 18 with radial needle bearings ( A tilting bearing 30 is supported so as to be swingable (tiltable). Further, as described above, the circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (left and right direction in FIG. 5), and the inner peripheral surface of the locking hole 19 is cylindrical. Support posts 64 and 68 are internally fitted as surfaces. 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 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 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 (rolling elements) 26, 26, an annular retainer 27 that holds the balls 26, 26 in a freely rolling manner, and an annular outer ring 28. It consists of and. 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, drive rods (shaft portions extending from the pivot shaft) 29 and 29 are respectively provided at one end portions (lower end portions in FIG. 6) of the trunnions 15 and 15, and outer peripheral surfaces of intermediate portions of the drive rods 29 and 29. The drive pistons (hydraulic pistons) 33, 33 are fixedly provided. Each of the drive pistons 33 and 33 is oil-tightly fitted in a cylinder chamber 31a of 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 drive shaft 22 is transmitted to the input side disks 2 and 2 and the input shaft 1 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 (offset) in opposite directions. For example, the power roller 11 on the left side in FIG. 6 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 positions of the peripheral surfaces (traction surfaces) 11a and 11a of the power rollers 11 and 11 and the inner surfaces 2a and 3a change, and the rotational speed ratio between the input shaft 1 and the output gear 4 is changed. Change. 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 such a toroidal-type continuously variable transmission, whether it is a single cavity or a double cavity, the yoke is independent in the front and rear cavities, or the power transmitted in the front and rear cavities is different. The thrust difference between the input / output side disks 2 and 3 is received by the posts 64 and 68. Therefore, for example, in Patent Documents 1 to 3, the posts 64 and 68 are fixing means such that the center line of the spherical surface of the posts 64 and 68 perpendicular to the variator shaft (input shaft 1) intersects the variator shaft. Thus, the casing 50 or the cylinder body 61 is fixed. That is, the posts 64 and 68 are fixed by bolts whose center lines coincide with the posts 64 and 68.

  On the other hand, for example, in Patent Document 4, the posts 64 and 68 are fixed to the casing 50 or the cylinder body 61 by fixing means having a center line offset from the center line of the spherical portion of the posts 64 and 68 perpendicular to the variator shaft. The lengths of the contact portions between the posts 64 and 68 and the casing 50 or the cylinder body 61 are substantially equal in the direction of the input shaft 1 and the directions of the yokes 23A and 23B.

Japanese Unexamined Patent Publication No. 64-3361 Japanese Patent Publication No.8-19998 Japanese Patent No. 2574849 Japanese Patent Laid-Open No. 10-267097

  In the toroidal type continuously variable transmission, the thrust generated in the input / output side disks 2 and 3 is not equal except in a constant speed state. In the case where the two are independent, the differential force is received by the posts 64 and 68 via the yokes 23A and 23B. This differential force acts in the direction from the output side disk 3 to the input side disk 2 on the deceleration side, and in the direction from the input side disk 2 to the output side disk 3 on the acceleration side. That is, it varies depending on the reduction ratio. Note that this differential force is a large force of about 8 tons at maximum in a single cavity type toroidal continuously variable transmission for a passenger car, for example.

  Further, in the case where the speed ratio or torque transmitted by the front and rear cavities of the double cavity is different (for example, the front and rear cavities are distinguished for front wheels and rear wheels for four-wheel drive; refer to Japanese Patent No. 3666879), for example, the yoke Even if the front and rear cavities 221 and 222 are coupled to each other, the front and rear cavities 221 of the thrust difference between the input and output side disks 2 and 3 are the same unless the transmission torque and the transmission ratio of the front and rear cavities 221 and 222 match. , 222 is received by the posts 64, 68 via the yokes 23A, 23B.

  As disclosed in Patent Documents 1 to 3, when the posts 64 and 68 are fixed by bolts whose center lines coincide with the posts 64 and 68, layout restrictions (interference with the drive piston 33, etc.) ), The bolt thickness is limited. In particular, in small four-wheeled vehicles and two-wheeled vehicles that use a single cavity, the control hydraulic pressure is lowered by increasing the area of the drive piston 33 so that the engine power is not consumed greatly by the pump drive. Since there is a tendency, the restriction becomes significant. In this case, the seating surface pressure between the posts 64 and 68 and the fixed object cannot be sufficiently secured, and there is a concern that the bolt may be loosened due to the above-described large and fluctuating force. When the bolt is loosened, the position of the traction contact point between the disks 2 and 3 and the power roller 11 is deviated from the design value, resulting in a decrease in efficiency.

  Further, as disclosed in Patent Document 4, the posts 64 and 68 are fixed to the casing 50 or the cylinder body 61 by fixing means having a center line offset from the center line of the spherical portion of the posts 64 and 68 perpendicular to the variator shaft. Even if the post is fixed, if the height from the fixed surface of the posts 64 and 68 to the spherical surface portion is high, the moment increases and the effect of the fixing member offset decreases. Therefore, the height from the fixed surface of the posts 64 and 68 to the spherical surface should be as low as possible. Further, in the layout in which the bolt is inserted from the yoke side, it is necessary to sit on the contact surface in order to avoid interference between the head and the yoke when securing the necessary bolt size. When the length of the contact portion between 68 and the casing 50 or the cylinder body 61 is substantially equal in the direction of the input shaft 1 and the direction of the yokes 23A and 23B, interference with the drive piston 33 occurs. We will look for a compromise under three constraints: area, bolt size, and yoke-bolt head interference. On the other hand, in the case of a layout in which the bolt is inserted from the side opposite the yoke, if a sufficient bolt engagement length is ensured, the post spherical surface portion becomes high, and thus a large moment as described above acts. .

  The present invention has been made in view of the above circumstances, and provides a toroidal continuously variable transmission that can sufficiently secure the fixing strength of a post without being affected by the structure of a hydraulic mechanism including a drive piston and a cylinder. The purpose is to do.

  In order to achieve the above object, the present invention provides a casing, an input shaft provided inside the casing, to which rotational torque is input, and the input shaft concentrically with each other with their inner surfaces facing each other. And an input side disk and an output side disk supported rotatably, a power roller sandwiched between these two disks, and a twisted position with respect to the central axis of the input side disk and the output side disk And a trunnion that tilts around a pair of pivots provided concentrically with each other and that rotatably supports the power roller, a drive device that displaces the trunnion in the axial direction of the pivot, and the trunnion The pivot shaft is supported so as to be tiltable and axially displaceable, and the yoke that swings due to the displacement of the trunnion and the yoke can swing. The drive device has a cylinder body having a pair of adjacent cylinder chambers, and a drive piston fitted in each cylinder chamber in an oil-tight manner, and the support member is In a toroidal continuously variable transmission fixed to a portion of the cylinder body located between a pair of cylinder chambers via a fixing means, in a vertical plane perpendicular to a plane including both chamber central axes of the two cylinder chambers The fixed center through which the fixed central axis of the fixing means passes is offset in the direction perpendicular to the fixed central axis from the midpoint between the chamber central points through which the two chamber central axes respectively pass.

  In the above configuration, it is preferable that the fixed center is offset in the axial direction of the input shaft with respect to the midpoint. Moreover, it is preferable that the said support member which contacts the said cylinder body is larger than the length in alignment with the direction along the direction of the said input shaft along the direction orthogonal to it. Also. It is preferable that the fixing means is made of a bolt, and the head of the bolt contacting the yoke is spherical.

  According to the present invention, in the vertical plane perpendicular to the plane including both the chamber central axes of the two cylinder chambers, the fixed center through which the fixed central axis of the fixing means passes is each of the two chamber central axes through Since the center point between the chamber center points is offset in a direction perpendicular to the fixed central axis, the fixing center of the fixing means can be located in a region where the cylinder chambers are largely separated from each other, and therefore the size of the fixing means Can be limited by the cylinder chamber. As a result, the fixing means can be set to a desired size and number to increase the fixing strength. In particular, when the fixing means is a bolt, it is possible to prevent the bolt from loosening. In that case, if the layout is such that the bolt is inserted from the yoke side, the height of the contact portion of the support member with the yoke can be lowered, so that sufficient seating surface pressure can be secured and loosening of the bolt can be reliably prevented. it can.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the post fixing structure, and other configurations and operations are the same as those of the conventional configuration and operations described above. Therefore, only the features of the present invention will be referred to below, and the rest These parts will be simply described with the same reference numerals as those in FIGS.

  As shown in FIGS. 1 to 4, the support member 300 for supporting the yokes 23 </ b> A and 23 </ b> B in a swingable manner has a rectangular plate shape, and a support protrusion 302 projects from the center in the longitudinal direction. Has been. A spherical post 304 that is engaged with the locking hole 19 of the yokes 23A and 23B is press-fitted and fixed to the support protrusion 302.

  The support member 300 is fixed to the cylinder body 61 through a pair of bolts 310a and 310b as fixing means. Specifically, as shown in FIG. 1, bolts 310a and 310b are passed through fixing holes 300a and 300b of the support member 300 positioned substantially symmetrically on both sides of the support protrusion 302, and the passed bolts 310a and 310b are passed through the cylinder body. The support member 300 is fastened and fixed to the cylinder body 61 by being screwed into the corresponding screw holes 61a and 61b. A counterbore 350 is provided at a portion of the cylinder body 61 to which the support member 300 is attached, as shown in FIG. 2B, and the heads of the bolts 310a and 310b and the yoke 23A are provided by the counterbore 350. , 23B is prevented. In addition, on the bottom surface of the support member 300 (the surface that comes into contact with the counterbore surface of the cylinder body 61), an inlay portion 302a that is fitted into the positioning hole 61c of the cylinder body is provided. Thereby, the centering of the supporting member 300 (supporting protrusion 302) with respect to the cylinder body 61 is satisfactorily performed.

  As shown in FIG. 2, the cylinder body 61 has a pair of adjacent cylinder chambers 31a and 31a ′ into which the drive piston 33 (not shown in FIG. 2; see FIG. 6) is fitted in an oil-tight manner. The support member 300 is fixed to a part of the cylinder body 61 (a part of the counterbore surface) located between the pair of cylinder chambers 31a and 31a ′. In that case, the fixed center through which the fixed central axes L2 and L2 ′ of the bolts 310a and 310b pass in the vertical plane P2 perpendicular to the plane P1 including both the chamber central axes L1 and L1 ′ of the two cylinder chambers 31a and 31a ′. O4 and O5 are directions perpendicular to the fixed central axes L2 and L2 ′ from the middle point O3 between the chamber central points O1 and O2 through which the two chamber central axes L1 and L1 ′ respectively pass (the axial direction of the input shaft 1; FIG. 1)). Accordingly, in the support member 300 that contacts the cylinder body 61, the length B along the direction of the input shaft 1 is set to be larger than the length A along the direction orthogonal thereto.

  As shown in FIGS. 3 and 4, the bolts 310a and 310b as fixing means have a spherically shaped bolt head 400 that contacts the yokes 23A and 23B. When the bolt head 400 that contacts the yokes 23A and 23B is made spherical in this way, the head 400 serves as a fulcrum for the seesaw motion of the yokes 23A and 23B, so that, for example, one trunnion 15 (for example, the right trunnion in FIG. 15) The other trunnion 15 (for example, the left trunnion 15 in FIG. 5) is displaced downward in accordance with the upward displacement of 15), and the movement of the pair of trunnions 15 facing each other in the same cavity is like a seesaw. The movement of the yoke to be synchronized with is facilitated.

  As described above, in the present embodiment, the fixed centers of the bolts 310a and 310b in the vertical plane P2 perpendicular to the plane P1 including both the chamber center axes L1 and L1 ′ of the two cylinder chambers 31a and 31a ′. A direction in which the fixed centers O4 and O5 through which the axes L2 and L2 ′ pass are orthogonal to the fixed center axes L2 and L2 ′ from a middle point O3 between the chamber center points O1 and O2 through which the two chamber center axes L1 and L1 ′ pass Since it is offset (in the axial direction of the input shaft 1), the fixing centers O4 and O5 of the bolts 310a and 310b can be positioned in a region S ′ where the cylinder chambers 31a and 31a ′ are largely separated from each other. That is, by fixing the fixing centers O4 and O5 with respect to the middle point O3 located in the narrow central fixing region S where the cylinder chambers 31a and 31a ′ are closest to each other, the fixing region S ′ to which the bolts 310a and 310b are fixed. Can secure a sufficient thickness α (see FIG. 2C). Therefore, the possibility that the size of the bolts 310a and 310b is limited by the cylinder chamber can be minimized. As a result, the fixing means can be set to a desired size and number to increase the fixing strength. In particular, it is possible to prevent loosening of the bolts 310a and 310b. In that case, the layout in which the bolts 310a and 310b are inserted from the side of the yokes 23A and 23B can reduce the height of the contact portion of the support member 300 with the yokes 23A and 23B. The bolts 310a and 310b can be reliably prevented from loosening.

  The present invention can be applied to various half-toroidal continuously variable transmissions such as a single cavity type and a double cavity type.

It is a figure which shows embodiment of this invention, Comprising: It is a perspective view which shows the attachment structure of the support member which has a post, and a cylinder body. 1A is a plan view of the cylinder body of FIG. 1 with a support member fastened, FIG. 1B is a cross-sectional view taken along line AA in FIG. 1A, and FIG. 1C is taken along line BB in FIG. Cross section It is a perspective view which shows the state which attached the yoke with respect to the post (support member) fixed to the cylinder body of FIG. (A) is a top view of the attachment structure of FIG. 3, (b) is a side view, (c) is sectional drawing which follows the CC line of (a). It is sectional drawing which shows an example of the specific structure of the toroidal type continuously variable transmission conventionally known. It is sectional drawing which follows the AA line of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Input shaft 2 Input side disk 3 Output side disk 11 Power roller 14 Pivot 15 Trunnion 23A, 23B Yoke 31a, 31a 'Cylinder chamber 33 Drive piston 50 Casing 61 Cylinder body 300 Support member 304 Spherical post 310a, 310b Bolt (fixing means)

Claims (4)

A casing, an input shaft provided inside the casing to which rotational torque is input, and an input side disk supported concentrically and rotatably on the input shaft in a state where the inner surfaces thereof face each other; An output-side disk, a power roller sandwiched between these two disks, and a pair of pivots provided concentrically with each other at a twisted position with respect to a central axis of the input-side disk and the output-side disk A trunnion that tilts to the center and rotatably supports the power roller, a drive device that displaces the trunnion in the axial direction of the pivot, and the pivot of the trunnion can tilt and displace in the axial direction. And a support member for supporting the yoke so as to be swingable. The apparatus includes: a cylinder body having a pair of adjacent cylinder chambers; and a drive piston fitted oil-tightly in each cylinder chamber, wherein the support member is positioned between the pair of cylinder chambers. In the toroidal-type continuously variable transmission fixed to the part via the fixing means,
In a vertical plane perpendicular to a plane including both chamber central axes of the two cylinder chambers, the fixed center through which the fixed central axis of the fixing means passes is the center between the chamber central points through which the two chamber central axes respectively pass. A toroidal continuously variable transmission that is offset from a point in a direction perpendicular to the fixed central axis.   The toroidal continuously variable transmission according to claim 1, wherein the fixed center is offset in the axial direction of the input shaft with respect to the midpoint.   3. The toroidal continuously variable length according to claim 1, wherein the support member in contact with the cylinder body has a length along the direction of the input shaft larger than a length along a direction orthogonal thereto. transmission.   The toroidal continuously variable transmission according to any one of claims 1 to 3, wherein the fixing means comprises a bolt, and the head of the bolt that contacts the yoke has a spherical shape.

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