JP6248609B2 - Toroidal continuously variable transmission - Google Patents

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 single cavity toroidal continuously variable transmission used as an automobile transmission is configured as shown in FIGS. 3 and 4 (see, for example, Patent Document 1). An input shaft 1 is rotatably supported inside a casing (not shown), and an input side disk 2 and an output side disk 3 are attached to the outer periphery of the input shaft 1.

  The output side disk 3 is supported by a needle bearing 5 interposed between the output shaft 1 and the input shaft 1 so as to be rotatable about the axis of the input shaft 1. Further, the input side disk 2 is supported rotatably about the axis of the input shaft 1 by a needle bearing 6 interposed between the input side disc 1 and the input shaft 1. The input side disk 2 is rotationally driven by the input shaft 1 via a loading cam type pressing device 12 provided between the input side disk 2 and the cam plate 7.

  An output gear 4 is rotatably supported on the outer periphery on the back side of the output side disk 3 of the input shaft 1. The output side disk 3 is connected to the output gear 4 so as to rotate integrally. The output gear 4 is provided on the opposite side (right side in FIG. 3) of the output side disk 3 with respect to the output gear 4 and is rotatably supported by the casing via an output side bearing 36 supported by the casing. ing. The output side disk 3 is restricted from moving to the right side of the input shaft 1 via the output gear 4 by the output side bearing 36. As a result, the output side disk 3 and the output gear 4 can rotate around the axis of the input shaft 1 while being prevented from being displaced in the axial direction.

  A power roller 11 is rotatably held between the inner side surface (concave surface) 2a of the input side disc 2 and the inner side surface (concave surface) 3a of the output side disc 3.

  The cam plate 7 of the pressing device 12 located on the left side in FIG. 3 is restricted from moving to the left side with respect to the input shaft 1 by a flange 38 formed on the left side of the input shaft 1 in FIG. Further, the cam plate 7 is spline-coupled to the input shaft 1, for example, so as to be rotatable integrally with the input shaft 1. Further, a cylindrical support member 42 is fixed to the right end portion of the input shaft 1, and this support member 42 is inserted and fixed to an input side bearing 37 supported by the casing. Further, a ring-shaped fixing member 43 is brought into contact with the right side of the flange portion 42 a of the support member 42, and the fixing member 43 is fixed to the input shaft 1.

  As a result, when the input device 2 is pressed toward the right side in the axial direction of the input shaft 1 by the pressing device 12, the cam plate 7 is pressed to the left side in the axial direction of the input shaft 1 by the reaction force. The movement of 1 to the left in the axial direction is restricted. Further, when the output side disk 3 is pressed rightward by the pressing device 12 via the input side disk 2 and the power roller 11, a thrust load is applied to the output side bearing 36 via the output gear 4. In this case, the output side bearing 36 supported by the casing restricts the movement of the output side disk 3 and the output gear 4 to the right in the axial direction of the input shaft 1. For these reasons, the pressing device 12 can apply a pressing force to the contact portions between the concave surfaces 2a and 3a of the disks 2 and 3 and the peripheral surfaces 11a and 11a of the power rollers 11 and 11, respectively.

  In addition, a disc spring 8 is provided between the flange portion 42a of the support member 42 and the fixing member 43, and this disc spring 8 is a concave surface 2a of each of the disks 2 and 3 when the pressing device 12 is not in operation. , 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 around a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing. 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 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, the inclination angle of the displacement shaft 23 supported at the center of each trunnion 15, 15 can be adjusted. Each power roller 11 is rotatably supported via a radial needle bearing 35 around the tip 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input side disk 2 and the output side disk 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 axially displaceable 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 that is long in the direction perpendicular to the axial direction of the input shaft 1 by press working or forging of a metal such as steel. Circular support holes 18 and 18 are provided at both ends of each yoke 23A and 23B, respectively. The pivot shafts 14 provided at both ends of the trunnion 15 are provided with radial needle bearings 30 in the support holes 18 and 18, respectively. It is supported so that it can swing freely. Further, a 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. 4), and posts 64 and 68 are fitted in the locking hole 19. That is, the upper yoke 23A is swingably supported by the post 64 supported by the casing via the fixing member 52, and the lower yoke 23B is formed by the post 68 and the cylinder body 31 that supports the post 68. The upper cylinder body 61 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. In addition, the direction in which the distal end portion 23b of each of the displacement shafts 23 and 23 is eccentric with respect to the base end portion 23a is the same direction (upward and downward direction in FIG. 4) with respect to the rotational direction of both the disks 2 and 3. It has become. 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, drive 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 drive piston ( Hydraulic pistons) 33, 33 are fixed. Each of the drive pistons 33 and 33 is oil-tightly fitted in a cylinder body 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the cylinder body 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 disk 2 via the pressing device 12. Then, the rotation of the input side disk 2 is transmitted to the output side disk 3 via the pair of power rollers 11, 11, and the rotation of the output side disk 3 is taken out from the output gear 4.

  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 direction of the tangential force acting on the contact portions between the peripheral surfaces 11a and 11a of the power rollers 11 and 11 and the inner side surfaces 2a and 3a of the input side disk 2 and the output side disk 3 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.

  5 and 6 show a yoke 23A (23B) of a single cavity toroidal continuously variable transmission. As described above, the yoke 23A is provided with the locking hole 19 that is fitted so as to swingably support the yoke 23A with the post 64 (68) passing through the center thereof. Further, at both ends of the yoke 23A, support holes 18 into which the pivot shafts 14 of the trunnions 15 are swingably fitted are provided.

  The support hole 18 and the locking hole 19 are located in the center of the yoke 23A in a direction (width direction) orthogonal to the longitudinal direction of the yoke 23A and along the direction along the axial direction of the input shaft 1. . For example, the width X, which is the distance between the left side edge along the longitudinal direction of the yoke 23A of the locking hole 19 and the left side edge along the longitudinal direction of the yoke 23A, and the yoke 23A of the locking hole 19 The width Y as the distance between the right side edge along the longitudinal direction and the right side edge along the longitudinal direction of the yoke 23A is equal. That is, the width X and the width Y of each divided portion divided into the left and right by the locking hole 19 along the axial direction of the input shaft 1 in the central portion of the yoke 23A are equal to each other.

A thrust force (F _PR ) of the power roller 11 acts from the pivot 14 of the trunnion 15 on the single-cavity toroidal continuously variable transmission yoke 23A (23B) as shown in FIG. A thrust force acts on the power roller 11 that is pressed by the pressing device 12 while being sandwiched between the input side disk 2 and the output side disk 3, and this thrust force is applied to the trunnion 15 via the thrust ball bearing 24. This thrust force acts on the yoke from the pivot 14 of the trunnion 15.

Here, since the force acting on the yoke from the pair of trunnions 15 is F _PR , the force acting on each support hole 18 is F _PR / 2. Further, in the toroidal type continuously variable transmission, the power roller 11 swings (tilts) around the pivot 14 at the time of shifting. For example, in the neutral position, the axial direction (rotational axis direction) of the power roller 11 is perpendicular to the direction along the axial direction of the input shaft 1, but the power roller 11 and the trunnion 15 have a gear ratio. Tilt to Low or High side. In FIG. 6, when the power roller 11 tilts obliquely to the left of the yoke 23A and the thrust force of the power roller 11 acts diagonally to the right of the yoke 23A (F _PR / 2), the power roller 11 is on the High side.
Conversely, when the power roller 11 tilts obliquely to the right side of the yoke 23A and the thrust force (F _PR / 2) of the power roller 11 acts diagonally to the left of the yoke 23A, the power roller 11 becomes the Low side.

The pair of power rollers 11 and 11 are tilted in the same direction when tilted in the left-right direction while being opposed to each other at the neutral position. Here, the direction of the power rollers 11 and 11 is the direction of the axis of rotation of the power rollers 11 and 11 and the direction from the large diameter side to the small diameter side of the power rollers 11 and 11. The direction (direction) of F _PR / 2, which is the thrust force of the power roller 11 acting on each support hole 18 of the yoke 23A when tilted with respect to the neutral position, is the above-described direction (direction) of the power roller 11. ) In the opposite direction.

In FIG. 6, the direction of F _PR / 2 that is the thrust force of the tilted power roller 11 is represented by an angle φ with respect to the direction along the input shaft 1, and F _PR / 2 is the axial direction of the input shaft 1. And an axial component that is perpendicular to the axial direction perpendicular to the axial direction of the input shaft 1. Axial component of the F _PR / 2 _is, (F PR / 2) _COSφ, and the axis-perpendicular component _becomes (F PR / 2) SINφ. Moreover, High (side) and Low (side) in FIG. 6 are sides on which the arrow of the component perpendicular to the axis faces when the power roller 11 tilts. Therefore, the direction of F _PR / 2 in FIG. 6 is the case where the power roller 11 is tilted to the high side of the gear ratio.

The axial perpendicular components of the thrust force F _PR / 2 of the power roller 11 acting on the two support holes 18 of the yoke 23A from the pivot shaft 14 of the trunnion 15 respectively are substantially equal in the opposite directions. , Offset each other. On the other hand, the axial components of the thrust force F _PR / 2 of the power roller 11 applied to the two support holes 18 are not canceled because their directions are parallel to each other and in the same direction.

Therefore, the yoke 23A receives the force (F _PR / 2) COSφ of the axial component of F _PR / 2 as the thrust force of the power roller 11 from the trunnion 15 at the pair of support holes 18, respectively. The reaction force which becomes F _PR COSφ as the total value of these forces is received from the post 64 (68) at the portion of the locking hole 19. Therefore, the yoke 23A, the stiffness to accommodate these forces required, the yoke 23A, the maximum thrust force F _PR according to the power roller 11 is using those rigid withstand act.

JP 11-294549 A

Meanwhile, the thrust force F _PR acting on the power roller 11 is to change the gear ratio, as shown in the graph of FIG. 7, the thrust force F _PR increases as the Low side from the High side. Therefore, when the power roller 11 is tilted to the Low side, the maximum thrust force _FPR is generated. When the power roller 11 is tilted to the High side, the maximum thrust force (step S) is not generated and the neutral tilt is generated. when divided into low and High at an angle, the thrust force _{F PR} of the High side is lower than the low side.

In contrast, conventional yoke 23A (23B), regardless of the tilting angle of the power rollers 11, the maximum and the thrust force _{F PR} becomes rigid to withstand also act, is _{F PR} acting from the Low side In the state of tilting toward the small High side, the yoke 23A has higher rigidity than necessary and sufficient, and there is a problem in cost.

  Further, the yoke 23A (23B) is provided with a tilt stopper that asymmetrically tilts on the yoke 23A (23B) to restrict the tilt range (rotation range) of the trunnion 15. The left-right direction here is a direction orthogonal to the longitudinal direction of the yoke 23A. When assembling the toroidal continuously variable transmission, if the yoke 23A (23B) is reversed left and right, that is, if the Low side and the High side described above are reversed, the tilt stopper arrangement is reversed left and right ( There is a possibility that the designed speed change cannot be performed.

  Here, when the yoke 23A (23b) is assembled into the toroidal-type continuously variable transmission, the pivot 14 of the trunnion 15 is inserted into the support hole 18 of the yoke 23A (23B), and the post 64 (68) is inserted into the locking hole 19. Will be inserted. Further, the yoke 23A (23B) is reversed left and right by the center line along the longitudinal direction of the yoke 23A (23B) passing through the center of the two support holes 18 and the center of the one locking hole 19. Also, the two pivot shafts 14 and one post 64 (68) can be inserted into the two support holes 18 and the one locking hole 19. That is, the yoke 23A (23B) has such a shape that can be erroneously assembled with the left and right reversed, and it is difficult to completely prevent the erroneous assembly.

  The present invention has been made in view of the above circumstances, and has a structure in which the position of the locking hole in which the yoke post is locked is decentered along the axial direction of the shaft so that the yoke acts on the yoke. It is an object of the present invention to provide a single cavity type toroidal continuously variable transmission that can have an efficient structure with respect to a force based on the thrust force of a power roller.

In order to achieve the above object, a toroidal continuously variable transmission according to the present invention includes an input side disk and an output side disk that are supported concentrically and rotatably with their respective inner surfaces facing each other. A shaft penetrating the center of the input side disc and the center of the output side disc, a power roller sandwiched between the input side disc and the output side disc, and the input side disc and the output side disc. A trunnion that tilts around a pivot that is twisted with respect to the central axis and that rotatably supports the power roller, and that the pivot of the trunnion can be tilted and displaced in the axial direction of the pivot. A single key provided with a pair of yokes that support and swings by the displacement of the trunnion, and posts that support the yokes in a swingable manner. In Activity type toroidal type continuously variable transmission,
The yoke includes a locking hole in which the post is inserted and locked between a pair of pivots supported by the yoke,
And the widths along the axial direction of the shaft of the divided portions of the yoke divided into two by the locking holes along the axial direction of the shaft are different from each other.

  In the present invention, in a single cavity toroidal continuously variable transmission, the width along the axial direction of each divided portion of the yoke divided into two by the locking holes along the axial direction of the shaft Are different from each other. That is, the position of the locking hole for locking the yoke post is eccentric along the axial direction. In this case, the rigidity along the axial direction of the long divided part is higher than the rigidity along the axial direction of the divided part having a short width.

Further, these wedges, when the thrust force F _{PR / 2} of the power roller, respectively the portion for supporting the pair of pivot yoke through a pivot trunnion is input, the these thrust force F _{PR / 2} The reaction force of the axial component (F _PR / 2) COSφ of the shaft is applied from one post 64. At this time, depending on whether the power roller is tilted to the Low side or to the High side, it is determined whether the reaction force acts on either of the two divided portions with the engagement hole of the yoke as a boundary. It has become.

Here, when the power roller rotates to the high side, the reaction force acts on the narrow divided portion, and when the power roller rotates to the low side, the reaction force acts on the wide side, Since the thrust force F _{PR of the} roller tends to increase as it changes from the High side to the Low side, when the thrust force increases on the Low side, the reaction force of the thrust force is applied to the wide divided portion along the axial direction. When the thrust force is lowered on the High side, a reaction force of the thrust force acts on the narrow divided portion along the axial direction.

  In this case, in the state where the position of the locking hole of the yoke is not eccentric as in the prior art, compared to the case where the widths of the parts divided by the yoke are equal to each other, The width of the acting direction of force becomes wider.

  Therefore, the yoke of the present invention can have a structure that can withstand a larger reaction force on the Low side as compared with a yoke that has substantially the same shape and material and the locking hole is not eccentric. This makes it possible to reduce the cost by reducing the width of the yoke or reducing the plate thickness when the maximum reaction force acting on the conventional product is the same. In this case, a structure capable of withstanding a larger reaction force (thrust force of the power roller) can be obtained.

  In the above configuration of the present invention, the yoke receives a thrust force applied to the power roller from the pivot, and applies a reaction force of an axial component along the axial direction of the shaft from the post to the power roller. It is set so that a large reaction force acts on the other divided portion that is received by one of the two divided portions based on the tilt angle of the two and wider than the one divided portion. preferable.

  According to such a configuration, in the single-cavity toroidal-type continuously variable transmission, since the width along the axial direction is wide as described above, a larger reaction force is generated at the divided portion having high rigidity along the axial direction. Compared to the conventional case, it is possible to handle a larger reaction force, and when receiving the same reaction force as before, the width of the yoke is reduced or the plate thickness is reduced. The cost can be reduced.

  According to the present invention, in the single-cavity toroidal-type continuously variable transmission, the locking hole for locking the yoke post can be arranged eccentrically along the axial direction of the yoke. Can be configured to efficiently cope with the force from the post acting on the yoke. In addition, it is possible to reliably prevent erroneous assembly such that the yoke is assembled in the opposite direction.

It is a top view which shows the yoke of the toroidal type continuously variable transmission of the single cavity system in embodiment of this invention. It is a figure for demonstrating the force concerning the yoke of a toroidal type continuously variable transmission. It is sectional drawing which shows an example of the conventional single cavity type toroidal type continuously variable transmission. It is sectional drawing which follows the AA line in FIG. It is a top view which shows the yoke of the conventional single cavity type toroidal type continuously variable transmission. It is a figure for demonstrating the force which the conventional single cavity type toroidal type continuously variable transmission applies. Is a graph showing the relationship between the speed ratio in the toroidal type continuously variable transmission and (iv) a thrust force of the power roller and (F _PR).

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The feature of the toroidal type continuously variable transmission according to the present embodiment is the position of the locking hole in which the yoke post is locked in the single cavity type toroidal continuously variable transmission. Detailed description will be given, and the other parts will be denoted by the same reference numerals as those in the prior art, and the description thereof will be omitted or simplified.

  As shown in FIG. 1, in the single cavity type toroidal continuously variable transmission according to this embodiment, the longitudinal direction of the yoke 23A (23B) (the direction orthogonal to the axial direction of the input shaft (axis) 1) is the same as in the prior art. ) Are provided with support holes 18 into which the pivot shaft 14 of the trunnion 15 is inserted and supported. Further, a locking hole 19 into which the posts 64 and 68 are inserted and locked is provided between the support holes 18 (the pivot shaft 14) at the central portion in the longitudinal direction of the yoke 23A.

  When the yoke 23A is assembled in a toroidal-type continuously variable transmission, the longitudinal direction of the yoke 23A is perpendicular to the direction along the axial direction of the input shaft 1 (the left-right direction in FIGS. 1 and 2). ing.

  Further, the center of the support hole 18 of the yoke 23 </ b> A is disposed at the center of the width along the axial direction of the input shaft 1. The locking hole 19 is arranged at the center between the two support holes 18, but is eccentrically arranged on the left side in the figure from the center of the width of the yoke 23A along the axial direction. Here, in the central portion along the longitudinal direction of the yoke 23 </ b> A, the yoke 23 </ b> A is divided into two left and right by the locking holes 19. Since each of the divided portions is arranged with the locking hole 19 eccentric as described above, from the width X (shown in FIG. 2) along the axial direction of the input shaft 1 of one of the left divided portions, A width Y (shown in FIG. 2) along the axial direction of the input shaft 1 of the other right divided portion is longer in the axial direction of the input shaft 1.

  That is, the width X as the shortest distance from the side edge (left side edge in FIG. 1) along one longitudinal direction of the yoke 23A to the side edge of the locking hole 19 and the other longitudinal direction of the yoke 23A. The width Y as the shortest distance from the side edge (right side edge in FIG. 1) to the side edge of the locking hole 19 is different from each other. Is longer.

In this case, the rigidity of the yoke 23A along the axial direction of the input shaft 1 is higher in the divided portion having the wider width (width Y) than in the divided portion having the smaller width (width X). In such yokes 23A, a thrust force as in the prior art of the power roller 11 _{F PR} acts, the reaction force _F PR cos [phi for _{2 × (F PR / 2)} COSφ an axial component of the _{F PR} Acts from the post 64 (68).

  FIG. 2 shows the force acting on the yoke 23A when the power roller 11 is tilted to the High side. In this case, the reaction force from the post 64 is shown along the axial direction of the input shaft 1 in FIG. It acts on the middle left side and acts on the left divided part having the width X of the two divided parts divided by the locking hole 19 of the yoke 23A.

2, when the power roller 11 tilts to the Low side, the reaction force from the post 64 acts on the right side along the axial direction of the input shaft 1, and the locking hole 19 of the yoke 23A. It acts on the right-side divided portion having the width Y of the two divided portions divided by. Here, when the power roller 11 is tilted from the neutral position to the High side, the axial component (F _PR / 2) COSφ of the thrust force is more than the axis perpendicular to the axis as it tilts to the High side. While towards direction component becomes larger, the thrust force F _PR decreases as shown in the graph of FIG.

Further, when the power roller 11 is tilted from the neutral position to the Low side, the axial component (F _PR / 2) COSφ of the thrust force is axially increased with respect to the axis perpendicular component as it tilts to the Low side. Write components is increased, and the thrust force F _PR increases as shown in the graph of FIG. Therefore, a larger reaction force acts from the post 64 when the gear ratio is set to the Low side than when the gear ratio is set to the High side.

  In the yoke 23A of the present embodiment, when the power roller 11 tilts to the High side, as shown in FIG. 2, a post 64 is provided on the divided portion of the width X shorter than the width Y along the axial direction of the input shaft 1. The reaction force from acts. On the other hand, when the power roller 11 is tilted to the Low side, contrary to the state shown in FIG. 2, the portion from the post 64 is separated from the divided portion having a width Y longer than the width X along the axial direction of the input shaft 1. Force acts.

  Accordingly, when the reaction force is small, the reaction force acts on the divided portion having a narrow width and low rigidity along the axial direction of the input shaft 1, and when the reaction force is large, the reaction force is large and the shaft of the input shaft 1 is wide. Stress acts on the divided portion having high rigidity along the direction. In this case, the yoke 23A has a structure that can withstand even a higher reaction force than in the past. Therefore, if the reaction force acting is the same as the conventional one, it is possible to reduce the cost by reducing the width of the yoke 23A along the axial direction of the input shaft 1 or by reducing the plate thickness.

  Further, in the yoke 23A (23B), the center position of the locking hole 19 is shifted with respect to the line segment connecting the centers of the two support holes 18, so that the shape is asymmetrical. In this case, the position of the post 64 is eccentric with respect to the position of the pivot 14 of the trunnion 15. Therefore, when the pivot 14 of the two trunnions 15 is inserted into the two support holes 18 of the yoke 23A and the post 64 (68) is inserted into the locking hole 19, the yoke 23A is reversed left and right. Both the pivot 14 and the post 64 cannot be inserted into the support hole 18 and the locking hole 19, and it is possible to reliably prevent the wrong assembly (erroneous assembly) in which the yoke 23 </ b> A is assembled to the left and right.

  Note that the values of the width X and the width Y that determine the amount of eccentricity of the locking hole 19 of the yoke 23A may be obtained by, for example, simulation or experiment, and are calculated from the data when there is available data. For example, it is determined based on the largest reaction force acting on each divided portion.

  The present invention can be applied to various single cavity type half-toroidal continuously variable transmissions.

1 Input shaft (axis)
2 Input side disk 3 Output side disk 11 Power roller 14 Pivot 15 Trunnion 18 Support hole 19 Locking hole 23A Yoke 23B Yoke

Claims (1)

An input side disk and an output side disk that are supported concentrically and rotatably with the respective inner side surfaces facing each other, and a shaft that passes through the center of the input side disk and the center of the output side disk. A power roller sandwiched between the input-side disk and the output-side disk, and tilted about a pivot shaft that is twisted with respect to a central axis of the input-side disk and the output-side disk, and A trunnion that rotatably supports a power roller, a pair of yokes that tiltably support the pivot shaft of the trunnion and that can be displaced in the axial direction of the pivot shaft, and swing by the displacement of the trunnion, and the yoke In a single cavity type toroidal continuously variable transmission comprising a post for swingably supporting,
The yoke includes a locking hole in which the post is inserted and locked between a pair of pivots supported by the yoke,
And, unlike width along the axial direction of the shaft of the divided portions of the yoke that is divided into two by the locking hole along the axial direction of the shaft to each other,
The yoke receives a thrust force applied to the power roller from the pivot, and a reaction force of an axial component along the axial direction of the shaft of the thrust force from the post based on the tilt angle of the power roller. A toroidal-type continuously variable step that is set so that a large reaction force acts on the other divided portion that is received by one of the two divided portions and is wider than the one divided portion. transmission.

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