JP6024186B2 - 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 double-cavity half-toroidal continuously variable transmission used as a transmission for an automobile is configured as shown in FIGS. 15 and 16 (two cavities 221 and 222 are shown in FIG. 15). As shown in FIG. 15, an input shaft (center shaft) 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two outputs are provided on the outer periphery of the input shaft 1. Side disks 3 and 3 are 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 rotationally driven by a drive 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 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, a power roller 11 (FIG. 16) is provided between inner side surfaces (concave surfaces) 2a and 2a of the input side disks 2 and 2 and inner side surfaces (concave surfaces; also referred to as traction surfaces) 3a and 3a of the output side disks 3 and 3. (See below) 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. 15, 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. 15) of the input side disk 2 is abutted against the loading nut 9. 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.

  16 is a cross-sectional view taken along line EE in FIG. As shown in FIG. 16, 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 50. Note that the input shaft 1 is not shown in FIG. Each trunnion 15, 15 is a pair of ends formed in the longitudinal direction (vertical direction in FIG. 16) of the support plate portion 16 that supports the power roller 11 in a state of being bent toward the inner side surface 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, the inclination angle of the displacement shaft (shaft) 23 supported at the center of each trunnion 15, 15 can be adjusted. It has become. 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. 16) 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 23A and 23B, and the pivot shafts 14 provided at both ends of the trunnion 15 are respectively connected to the support holes 18 via radial needle bearings (bearings) 30. And is swingably supported. 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. 15), 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 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 (up and down in FIG. 16). (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 (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. 16) of the trunnions 15 and 15, respectively, and driving pistons ( 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. 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. 16 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 input shaft 1 and the output gear 4 changes. To do. 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 half toroidal type continuously variable transmission as described above, since each trunnion 15 is displaced in the opposite direction to each other and the power roller 11 is tilted, the speed change is performed so as to maximize the torque transmission capacity. It is necessary to equalize the amount of torque transmission of the four power rollers 11 engaged in
For this reason, as schematically shown in FIG. 17, the tangential force 2Ft of the power roller 11 is supported by the drive piston (hydraulic piston) 33 of the drive device 32 that supports the axial force of the pivot 14 of the trunnion 15. The tangential force is equalized. Further, a normal force Fpr for pressing the power roller 11 against the disks 2 and 3 also acts on the trunnion 15, and this force is balanced as an internal force by the link mechanisms (yokes 23A and 23B) that support the four trunnions 15. Designed to be. These yokes 23A and 23B also have a function of relaxing the asynchronization of the offset amount of each trunnion 15 by tilting in a seesaw shape with respect to the trunnion 15 at the time of shifting.

However, when the yokes 23A and 23B have a large inclination and the yokes 23A and 23B and the trunnion 15 come into contact with each other at the interference portion Z and an interference force is applied between them, the torque distribution is deteriorated according to the interference force. There is a problem that the power transmission capability is greatly reduced.
Conventionally, as a method for reducing the interference force between the yokes 23A and 23B and the trunnion 15, for example, it has been proposed to arbitrarily adjust the gaps between the yokes 23A and 23B and the four trunnions 15 ( For example, see Patent Document 1).

JP 2002-213552 A

  However, due to the weight of the yokes 23A and 23B, it is difficult to finely adjust the relative positions of the yokes 23A and 23B incorporated in the variator (transmission unit) and the trunnion 15 by applying pressure.

  The present invention has been made in view of the above circumstances, and maintains the two functions of supporting the normal force acting on the trunnion and linking each trunnion in the seesaw state, while maintaining the pivotal axis of the yoke with respect to the trunnion. It is an object of the present invention to provide a toroidal continuously variable transmission that can regulate the position of the direction and thereby adjust the position between the yoke and trunnion to prevent power transmission loss due to interference between the yoke and trunnion. To do.

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 inner surfaces facing each other, and A plurality of power rollers sandwiched between these two disks, and a pair of pivots that are concentrically provided to each other and are twisted with respect to the center axis of the input side disk and the output side disk. A plurality of trunnions that rotate and rotatably support each of the power rollers, a drive device that displaces the trunnions in the axial direction of the pivot, and the pair of pivots of the trunnion are swingable and axial. A toroidal-type continuously variable transmission that includes a pair of yokes that are supported by a support hole through a bearing so as to be displaceable, and that swing by the displacement of the trunnion. Oite,
The outer peripheral surface of the bearing is formed in an arc-shaped convex surface, and the fitting portion between the inner peripheral surface of the support hole and the outer peripheral surface of the bearing is formed in a V-shaped concave surface or an arc-shaped concave surface, and The yoke is divided into two in the axial direction of the support hole, so that the fitting portion of the support hole is divided into two in the axial direction.

Further, another aspect of the toroidal continuously variable transmission of the present invention includes an input side disk and an output side disk that are supported concentrically and rotatably with their inner surfaces facing each other, and these A plurality of power rollers sandwiched between the two disks, and tilt about a pair of pivots concentrically provided to each other and in a twisted position with respect to the center axis of the input side disk and the output side disk In addition, a plurality of trunnions that rotatably support the power rollers, a driving device that displaces the trunnions in the axial direction of the pivot, and the pair of pivots of the trunnion are swingable and axially displaceable. A toroidal continuously variable transmission that includes a pair of yokes that are supported by a support hole via a bearing and that swings due to the displacement of the trunnion.
The outer peripheral surface of the bearing is formed in an arc-shaped convex surface, and the fitting portion between the inner peripheral surface of the support hole and the outer peripheral surface of the bearing is formed in a V-shaped concave surface or an arc-shaped concave surface, and The support hole is divided into two in the radial direction by dividing the yoke in the radial direction of the support hole.

  According to the present invention, the axial position of the pivot of the yoke relative to the trunnion can be regulated while maintaining the two functions of supporting the normal force acting on the trunnion and linking each trunnion in the seesaw state. Therefore, it is possible to adjust the position between the yoke and the trunnion to prevent interference between the yoke and the trunnion and to prevent power transmission loss. Further, the outer peripheral surface of the bearing is formed in an arc-shaped convex surface, and the fitting portion between the inner peripheral surface of the support hole or the ring and the outer peripheral surface of the bearing is formed in a V-shaped concave surface or an arc-shaped concave surface. These can be assembled and assembled.

It is a figure which shows the toroidal type continuously variable transmission which concerns on the 1st Embodiment of this invention, Comprising: It is sectional drawing which shows the coupling | bond part of a trunnion and a yoke. It is a schematic diagram which shows the coupling | bond part of a yoke and a bearing similarly. It is a figure which shows the toroidal type continuously variable transmission which concerns on the 2nd Embodiment of this invention, Comprising: It is a top view of a yoke. It is a side view which shows the coupling | bond part of a trunnion and a yoke same as the above. It is a schematic diagram which shows the coupling | bond part of a yoke and a bearing similarly. It is a figure which shows the toroidal type continuously variable transmission which concerns on the 3rd Embodiment of this invention, Comprising: It is a top view of a yoke. It is a figure which shows the toroidal type continuously variable transmission which concerns on the 4th Embodiment of this invention, Comprising: It is a top view of a yoke. It is sectional drawing which shows the coupling | bond part of a trunnion and a yoke same as the above. It is a schematic diagram which shows the coupling | bond part of a yoke and a bearing similarly. It is a top view of a ring same as the above. It is sectional drawing for demonstrating the assembly method of a trunnion and a yoke same as the above. It is a figure which shows the toroidal type continuously variable transmission which concerns on the 5th Embodiment of this invention, Comprising: It is a top view which shows the coupling | bond part of a yoke and a bearing. It is a schematic diagram which shows the coupling | bond part of a yoke and a bearing similarly. It is a figure which shows the modification of the toroidal type continuously variable transmission which concerns on the 5th Embodiment of this invention, Comprising: It is a top view which shows the coupling | bond part of a yoke and a bearing. 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 EE line | wire of FIG. It is a schematic diagram for demonstrating the function of a yoke.

Embodiments of the present invention will be described below with reference to the drawings.
The feature of the present invention lies in the structure of the bearing interposed between the pivot shaft of the trunnion and the support hole of the yoke and the support hole of the yoke, and the other configurations and operations are the same as the conventional configurations and operations described above. Accordingly, in the following description, only the characteristic part of the present invention will be referred to, and the other parts will be simply described with the same reference numerals as in FIGS.

1 and 2 show a first embodiment of the present invention.
As shown in FIG. 1, in this first embodiment, as in the conventional case of FIGS. 15 to 17, the radial needle bearing (bearing) 30 has an outer circumferential surface formed in an arcuate convex surface. And an outer ring 30a whose inner peripheral surface is a cylindrical surface and a plurality of needles 30b. The pivot 14 of the trunnion 15 is fitted inside the needle 30b. Further, the support holes 18 of the yoke 23A and the yoke 23B are fitted to the outside of the outer ring 30b. Since the yoke 23B is formed in the same manner as the yoke 23A, only 23A will be described below, and description of the yoke 23B will be omitted or simplified.

And in 1st Embodiment, the cross-sectional shape of the internal peripheral surface (fitting part) of the support hole 18 of the yoke 23A is formed in the V-shaped concave surface. The yoke 23 </ b> A is composed of a pair of yoke pieces 23 </ b> Aa and 23 </ b> Ab that are divided into two with the same thickness in the axial direction of the support hole 18. These yoke pieces 23 </ b> Aa and 23 </ b> Ab are overlapped and joined by a fixture 102 such as a bolt. The inner peripheral surface that forms the support hole 18 of the yoke piece 23Aa and the inner peripheral surface that forms the support hole 18 of the yoke piece 23Ab are connected to each other from the surface side toward the center in the axial direction of the inner peripheral surface. As a result, the taper surface is formed so as to gradually move away from the radial needle bearing 30, whereby the inner peripheral surface (fitting portion) of the support hole 18 of the yoke 23 </ b> A is a V-shaped concave surface. The arcuate convex surface of the radial needle bearing 30 is fitted to the inner peripheral surface of the support hole 18 formed in the V-shaped concave surface of the yoke 23A.
In FIG. 1, reference numeral 103 denotes a spacer that is fitted to the outside of the pivot shaft 14 and interposed between the trunnion 15 and the radial needle bearing 30. The spacer 103 provides a gap in the axial direction of the pivot 14 between the trunnion 15 and the radial needle bearing 30.

  FIG. 2 schematically shows a fitting state between the yoke 23 </ b> A and the radial needle bearing 30. As shown in the figure, the arc-shaped convex surface of the radial needle bearing 30 is in line contact with the inner peripheral surface of the V-shaped concave surface of the support hole 18 of the yoke 23A at two points. Thereby, the trunnion 15 and the yoke 23A operate as follows.

  That is, when the trunnion 15 moves in the axial direction of the pivot 14, the radial needle bearing 30 also moves together. At this time, the arcuate convex surface of the radial needle bearing 30 is within the V-shaped concave surface of the support hole 18 of the yoke 23A. One of the circumferential surfaces of the taper surface (the taper surface of the yoke piece 23Aa or the taper surface of the yoke piece 23Ab) is in line contact, and thereby the relative displacement in the axial direction of the pivot 14 of the yoke 23A with respect to the radial needle bearing 30 is suppressed. 23A moves together with the radial needle bearing 30. That is, the axial position of the pivot 14 of the yoke 23A relative to the trunnion 15 is restricted.

  Further, in the seesaw state of each trunnion 15, the position where the inner peripheral surface of the V-shaped concave surface of the support hole 18 of the yoke 23A is in line contact with the arc-shaped convex surface of the radial needle bearing 30 is changed at two points. In a state where the axial displacement of the pivot 14 of the yoke 23A relative to the needle bearing 30 is suppressed, the yoke 23A swings around the post 64. That is, the yoke 23 </ b> A can function as a link in the seesaw state of each trunnion 15.

  Further, since the arcuate convex surface of the radial needle bearing 30 is in line contact with the inner circumferential surface of the V-shaped concave surface of the support hole 18 of the yoke 23A at two points in the circumferential direction of the support hole 18, it acts on the trunnion 15. A normal force Fpr for pressing the power roller 11 against the disks 2 and 3 can be supported.

Next, an assembling method of the trunnion 15 and the yoke 23A (23B) will be described with reference to FIG.
The tapered through hole of the yoke piece 23Aa and the tapered through hole of the yoke piece 23Ab are inserted from both end face sides of the bearing 30, respectively, and the yoke pieces 23Aa and the yoke pieces 23Ab are overlapped, and then both the yoke pieces 23Aa, The yoke piece 23Ab is fixed with a fixture 102 such as a bolt. Then, the support hole 18 of the yoke 23 </ b> A is fitted to the outside of the bearing 30. Thereafter, each bearing 30 incorporated in the yoke 23 is inserted outside each pivot 14 of each trunnion 15.

  In such a toroidal-type continuously variable transmission, the outer peripheral surface of the radial needle bearing 30 is formed into an arcuate convex surface, and the support hole of the yoke 23A (yoke 23B) fitted to the arcuate convex surface. Since the inner peripheral surface of 18 is formed into a V-shaped concave surface, while maintaining the two functions of supporting the normal force Fpr acting on the trunnion 15 and linking each trunnion 15 in the seesaw state, The axial position of the pivot 14 of the yoke 23A (yoke 23B) can be regulated. Therefore, by adjusting the position between the yoke 23A (yoke 23B) and the trunnion 15, it is possible to prevent interference between the yoke 23A (yoke 23B) and the trunnion 15 and prevent power transmission loss.

  Further, since the yoke 23A (yoke 23B) is divided into two in the axial direction of the support hole 18, the outer peripheral surface of the radial needle bearing 30 is formed into an arcuate convex surface and is fitted to the arcuate convex surface. Even if the inner peripheral surface of the support hole 18 of the yoke 23A (yoke 23B) is formed in a V-shaped concave surface, the yoke 23A (yoke 23B) and the radial needle bearing 30 can be assembled and assembled.

In the first embodiment described above, the fixing member 102 provided on one yoke 23A (yoke 23B) is formed with convex portions respectively protruding on both side surfaces of the yoke 23A (yoke 23B), and the yoke 23A. A fixing member (for example, a wire pulley for synchronizing the trunnion) is provided at a position opposite to the trunnion 15 with respect to the yoke 23B, and the trunnion 15 side of the convex portion of the fixture 102 is provided on the trunnion 15 side. One projecting projecting portion is brought into contact with the end surface of the trunnion 15 facing the yoke 23A (yoke 23B), and the other projecting projecting portion of the projecting portion projecting toward the fixing member is brought into contact with the fixing member. It is preferable to do so.
Thus, when the trunnion 15 is displaced in the axial direction of the pivot 14 in response to the swing of the yoke 23A (yoke 23B), there is almost no play, and each trunnion supported by the yoke 23A (yoke 23B). 15 can be displaced in the axial direction while being synchronized with high accuracy.

3 to 5 show a second embodiment of the present invention.
As shown in FIG. 3, in the second embodiment, the support hole 18 is divided into two in the radial direction by dividing the yoke 23 </ b> A in the radial direction of the support hole 18. Specifically, in this example, the yoke 23A is divided into three yoke pieces 23Ac, 23Ad, and 23Ae in the radial direction of the support hole 18, that is, in plan view. The yoke piece 23Ac forms one end portion of the yoke 23 by dividing the support hole 18, the locking hole 19 and the support hole 18 of one row of the yoke 23 into two parts with a line connecting the centers thereof as a dividing line. The yoke piece 23Ae forms the other end portion of the yoke 23 by dividing the support hole 18, the locking hole 19 and the support hole 18 of the other row into two with a line connecting the centers thereof as a dividing line. The yoke piece 23Ad forms the middle part of the yoke 23 of the remaining part obtained by dividing the support hole 18, the locking hole 19 and the support hole 18 of both rows into two.

  As shown in FIG. 4, the yoke piece 23Ac and the yoke piece 23Ad are divided into the yoke piece 23Ac and the yoke piece 23Ad in more detail by fitting the concave portion and the convex portion in the radial direction of the support hole 18. They are fitted and joined from the direction perpendicular to the line. The yoke piece 23Ad and the yoke piece 23Ae are coupled in the same manner. Note that other means may be used as the coupling method.

As schematically shown in FIG. 5, the cross-sectional shape of the inner peripheral surface (fitting portion) of the support hole 18 of the yoke 23A is a V-shaped concave surface.
The yoke 23B is formed in the same manner as the yoke 23A. Other configurations are the same as those of the first embodiment.

Even in the toroidal type continuously variable transmission according to the second embodiment, the same effects as those of the first embodiment can be obtained.
Further, since the yoke 23A (yoke 23B) is divided into two in the radial direction of the support hole 18, the outer peripheral surface of the radial needle bearing 30 is formed into an arcuate convex surface and is fitted to the arcuate convex surface. Even if the inner peripheral surface of the support hole 18 of the yoke 23A (yoke 23B) is formed in a V-shaped concave surface, the yoke 23A (yoke 23B) and the radial needle bearing 30 can be assembled and assembled.

FIG. 6 shows a third embodiment of the present invention.
As shown in the figure, in the third embodiment, the support hole 18 is divided into two in the radial direction by dividing the yoke 23A in the radial direction of the support hole 18. Specifically, in this example, the yoke 23A is divided into three yoke pieces 23Af, 23Ag, and 23Ah in the radial direction of the support hole 18, that is, in plan view. The yoke piece 23Af divides the two support holes 18 and 18 on one side of the yoke 23 into two parts with a line connecting the centers thereof as a dividing line to form one end portion of the yoke 23. 23Ah is formed by dividing the two support holes 18 and 18 on the other side into two with a line connecting the centers thereof as a dividing line to form the other end portion of the yoke 23. The yoke piece 23Ag The middle portion of the yoke 23 of the remaining portion obtained by dividing the two support holes 18 on the side into two is formed.

As in the second embodiment, the yoke piece 23Af and the yoke piece 23Ag, and the yoke piece 23Ag and the yoke piece 23Ah are respectively fitted in the radial direction of the support hole 18 to be divided in more detail. They are fitted and joined from the direction perpendicular to the line.
Other configurations are the same as those of the second embodiment.

  Even in the toroidal-type continuously variable transmission of the third embodiment, the same effects as those of the second embodiment can be obtained.

7 to 11 show a fourth embodiment of the present invention.
As shown in FIG. 7, in the fourth embodiment, the support hole 18 and the locking hole 19 are formed in the same place as the conventional yoke 23A. As shown in FIG. 8, a ring 105 is fitted inside the support hole 18 of the yoke 23 </ b> A, and a radial needle bearing 30 is fitted inside the ring 105. As schematically shown in FIG. 9, the inner side of the ring 105 functions as a support hole 18A, and the cross-sectional shape of the inner peripheral surface (fitting portion) of the support hole 18A is formed in a V-shaped concave surface. As shown in FIG. 10, the ring 105 includes ring pieces 105a and 105a that are divided into two halves in plan view.

Next, a description will be given.
As shown in FIG. 11, a radial needle bearing 30 is attached to the pivot 14 of the trunnion 15, and then both ring pieces 105 a and 105 a are attached to the outside of the radial needle bearing 30 from the radial direction of the radial needle bearing 30 to form a ring shape. A tapered portion is formed on the outer side of one end portion of both ring pieces 105a and 105a. Corresponding to the taper portion of the ring 105 (the taper portions of both ring pieces 105a and 105a), a taper portion is also formed on the yoke 23A. Thereafter, the ring 105 is inserted into the outside of the ring 105 from the tip end side in the axial direction of the pivot 14 by press fitting or the like, and the ring 105 and the yoke 23A are coupled.
The portion of the yoke 23B is configured similarly to the portion of the yoke 23A. Other configurations are the same as those of the first embodiment.

  Even in the toroidal type continuously variable transmission according to the fourth embodiment, the same effects as those of the first embodiment can be obtained.

12 and 13 show a fifth embodiment of the present invention.
As shown in FIG. 12, in the fifth embodiment, the inner diameter of the support hole 18 </ b> B of the yoke 23 </ b> A is set larger than the outer diameter of the radial needle bearing 30. Further, as schematically shown in FIG. 13, the cross-sectional shape of the inner peripheral surface of the support hole 18B of the yoke 23A is formed in a V-shaped concave surface.
The portion of the yoke 23B is configured similarly to the portion of the yoke 23A. Other configurations are the same as those of the first embodiment.

Even in the toroidal type continuously variable transmission according to the fifth embodiment, the same effects as those of the first embodiment can be obtained.
In the fifth embodiment, it is not necessary to divide the yoke 23A (yoke 23B) for assembly. Further, when the normal force Fpr acts on the trunnion 15, the position of the yoke 23A (yoke 23B) can be regulated.

In the fifth embodiment, the support hole 18B of the yoke 23A (yoke 23B) is not circular as shown in FIG. 12, but may be an elliptical support hole 18C as shown in FIG. The oval shape of the support hole 18 </ b> C is formed so that the major axis direction thereof is parallel to a line connecting the centers of the locking holes 19 and 19.
The shape of the support hole 18B (18C) may be a circle or an ellipse, but a circle is preferable for processing. On the other hand, considering that the normal force Fpr for pressing the power roller 11 acting on the trunnion 15 against the disks 2 and 3 changes due to the swing of the power roller 11, an elliptical shape is preferable. However, even if circular, if processed with high accuracy, even if the normal force Fpr changes as described above, it can be supported without any problem.

In each of the above-described embodiments, the inner peripheral surface of the support hole 18, 18B, 18C or the support hole 18A of the ring 105 is formed into a V-shaped concave surface. You may make it support the radial needle bearing (bearing) 30 so that rocking | fluctuation is possible.
Further, in each of the above-described embodiments, the entire inner peripheral surface of the support hole 18, 18B, 18C or the support hole 18A of the ring 105 is formed into a V-shaped concave surface, and the outer peripheral surface of the radial needle bearing (bearing) 30 is formed. Although a part of the inner peripheral surface of the support hole 18, 18B, 18C or the support hole 18A of the ring 105 is formed into a V-shaped concave surface, the outer peripheral surface of the radial needle bearing (bearing) 30 is fitted. You may make it match.

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

2 input side disk 3 output side disk 11 power roller 14 pivot 15 trunnion 18 support hole 18A support hole 18B support hole 18C support hole 23A yoke 23B yoke 30 radial needle bearing (bearing)
32 Drive 105 Ring

Claims (2)

An input-side disk and an output-side disk that are supported concentrically and rotatably with their inner surfaces facing each other, a plurality of power rollers sandwiched between these two disks, and the input-side disk And a plurality of trunnions that are twisted with respect to the central axis of the output-side disk and tilt around a pair of pivots that are concentrically provided to each other and that rotatably support the power rollers, A drive device for displacing the trunnion in the axial direction of the pivot shaft, and the pair of pivot shafts of the trunnion are supported in a support hole via a bearing so as to be swingable and axially displaceable, and by the displacement of the trunnion In a toroidal continuously variable transmission comprising a pair of swinging yokes,
The outer peripheral surface of the bearing is formed in an arc-shaped convex surface, and the fitting portion between the inner peripheral surface of the support hole and the outer peripheral surface of the bearing is formed in a V-shaped concave surface or an arc-shaped concave surface, and A toroidal continuously variable transmission, wherein the yoke is divided into two in the axial direction of the support hole, and the fitting portion of the support hole is divided into two in the axial direction. An input-side disk and an output-side disk that are supported concentrically and rotatably with their inner surfaces facing each other, a plurality of power rollers sandwiched between these two disks, and the input-side disk And a plurality of trunnions that are twisted with respect to the central axis of the output-side disk and tilt around a pair of pivots that are concentrically provided to each other and that rotatably support the power rollers, A drive device for displacing the trunnion in the axial direction of the pivot shaft, and the pair of pivot shafts of the trunnion are supported in a support hole via a bearing so as to be swingable and axially displaceable, and by the displacement of the trunnion In a toroidal continuously variable transmission comprising a pair of swinging yokes,
The outer peripheral surface of the bearing is formed in an arc-shaped convex surface, and the fitting portion between the inner peripheral surface of the support hole and the outer peripheral surface of the bearing is formed in a V-shaped concave surface or an arc-shaped concave surface, and A toroidal continuously variable transmission characterized in that the support hole is divided into two in the radial direction by dividing the yoke in the radial direction of the support hole.

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