JP4797410B2 - 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.

  In some cases, a toroidal continuously variable transmission as schematically shown in FIGS. 10 and 11 is used as an automobile transmission. This toroidal continuously variable transmission supports an input side disk 2 concentrically with an input shaft 1, and an output side disk 4 is fixed to an end of an output shaft 3 disposed concentrically with the input shaft 1. On the inner side of the casing containing the toroidal type continuously variable transmission, trunnions 6 and 6 are provided that swing around pivots (tilting shafts) 5 and 5 that are twisted with respect to the input shaft 1 and the output shaft 3. It has been. A power roller 11 is rotatably supported on each trunnion 6, 6, and each power roller 11, 11 is sandwiched (rolled) between both the input side and output side disks 2, 4. .

  The cross sections of the inner side surfaces 2a and 4a facing each other of the input and output side disks 2 and 4 each form a concave surface obtained by rotating an arc centering on the pivot 5 or a curve close to such an arc. ing. And the peripheral surface 11a, 11a of each power roller 11, 11 formed in the spherical convex surface is contact | abutted to each inner surface 2a, 4a.

  Between the input shaft 1 and the input side disk 2, a loading cam type pressing device 12 is provided. The pressing device 12 elastically presses the input side disk 2 toward the output side disk 4. The pressing device 12 includes a cam plate 13 that rotates together with the input shaft 1 and a plurality of (for example, four) rollers 15 held by a cage 14. In addition, a cam surface 16 that is a concavo-convex surface is formed on one side surface (the left side surface in FIGS. 10 and 11) of the cam plate 13, and the outer surface (see FIGS. 10 and 10) of the input side disk 2. A similar cam surface 17 is formed on the right side surface of FIG. The plurality of rollers 15 are supported so as to be rotatable about an axis extending in the radial direction with respect to the input shaft 1.

  In the toroidal type continuously variable transmission having such a configuration, when the input shaft 1 is rotated, the cam plate 13 is rotated along with the rotation of the input shaft 1, and the plurality of rollers 15, 15 are connected to the input side disk by the cam surface 16. 2 is pressed by the cam surface 17 provided on the outer side surface of the head. As a result, the input side disk 2 is pressed against the plurality of power rollers 11, 11, and at the same time, based on the pressing between the pair of cam surfaces 16, 17 and the rolling surfaces of the plurality of rollers 15, 15. The input side disk 2 rotates. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the power rollers 11 and 11, and the output shaft 3 fixed to the output side disk 4 rotates.

  When the rotational speeds of the input shaft 1 and the output shaft 3 are changed, and when deceleration is performed between the input shaft 1 and the output shaft 3, the trunnions 6 and 6 are swung around the pivot shafts 5 and 5. As shown in FIG. 10, the peripheral surfaces 11 a and 11 a of the power rollers 11 and 11 are arranged near the center of the inner surface 2 a of the input side disk 2 and the outer periphery of the inner side surface 4 a of the output side disk 4. The displacement shafts 9 and 9 are inclined so as to abut each other.

  On the other hand, when increasing the speed, the trunnions 6 and 6 are swung so that the peripheral surfaces 11a and 11a of the power rollers 11 and 11 are formed on the inner surface 2a of the input side disk 2 as shown in FIG. Each of the displacement shafts 9 and 9 is inclined so as to come into contact with the outer peripheral portion and the central portion of the inner side surface 4 a of the output side disk 4. If the inclination angle of each of the displacement shafts 9 and 9 is intermediate between those shown in FIGS. 10 and 11, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

12 and 13 show an example of a more specific double cavity type toroidal continuously variable transmission. In addition, about the structural member which is common in FIG. 10 and FIG. 11, hereafter, the same code | symbol is attached | subjected and the detailed description or illustration is abbreviate | omitted.
As shown in FIG. 12, the input shaft 1 is rotatably supported inside the casing 101. A circular transmission shaft 103 is supported on the outer periphery of the input shaft 1. In this case, the transmission shaft 103 is disposed concentrically with the input shaft 1 and can rotate with respect to the input shaft 1.

  The first and second input side disks 2 and 2 are respectively supported by ball splines 96 at both ends of the transmission shaft 103. In this case, the first and second input side disks 2 and 2 are concentrically arranged with their inner side surfaces 2a and 2a facing each other, and can rotate in synchronization with each other inside the casing 101. .

  Around the intermediate portion of the transmission shaft 103, first and second output side disks 4, 4 are supported via a sleeve 109. An output gear 110 is integrally provided on the outer peripheral surface of the intermediate portion of the sleeve 109. The output gear 110 is disposed concentrically with the transmission shaft 103 and has an inner diameter larger than the outer diameter of the transmission shaft 103. The output gear 110 is rotatably supported by a support wall 111 provided in the casing 101 via a pair of rolling bearings 112.

  The first and second output side disks 4 and 4 are splined to both ends of the sleeve 109. In this case, the output side disks 4 and 4 are arranged with their inner side surfaces 4a and 4a facing in opposite directions. Accordingly, the input side disk 2 and the output side disk 4 have their inner side surfaces 2a, 4a facing each other.

  As shown in FIG. 13, a pair of yokes 113a and 113b are supported inside the casing 101 and laterally of the output side disks 4 and 4 with both the disks 4 and 4 sandwiched from both sides. . The pair of yokes 113a and 113b are formed in a rectangular shape by pressing or forging a metal such as steel. In order to support the pivots 5 provided at both ends of the trunnion 6 to be described later in a swingable manner, circular support holes 118 are provided at the four corners of the yokes 113a and 113b, and the width direction of the yokes 113a and 113b. A circular locking hole 119 is provided at the center of the.

  The pair of yokes 113a and 113b are supported so as to be slightly displaceable by support posts 20a and 20b formed on portions of the inner surface of the casing 101 facing each other. These support posts 20a and 20b are respectively provided so as to face the first cavity 21 and the second cavity 22 between the inner side surface 2a of the input side disk 2 and the inner side surface 4a of the output side disk 4, respectively. Yes. The post 20 a is provided with a tilt stopper 150 that regulates the tilt amount of the trunnion 6.

  Accordingly, the yokes 113 a and 113 b are supported by the support posts 20 a and 20 b, and one end thereof faces the outer peripheral portion of the first cavity 21 and the other end faces the outer peripheral portion of the second cavity 22. is doing.

  Since the first and second cavities 21 and 22 have the same structure, only the first cavity 21 will be described below.

  The first cavity 21 is provided with a pair of trunnions 6. Concentric shafts 5 are provided concentrically at both ends of the trunnion 6, and these pivots 5 are supported by one end portions of a pair of yokes 113a and 113b so as to be swingable and axially displaceable. That is, the pivot 5 is supported by the radial needle bearing 26 inside the support hole 118 formed at one end of the yokes 113a and 113b. The radial needle bearing 26 includes an outer ring 27 whose outer peripheral surface is a spherical convex surface and whose inner peripheral surface is a cylindrical surface, and a plurality of needles 28.

  A circular hole 30 is provided in each intermediate portion of the trunnion 6. A displacement shaft 31 is supported in each circular hole 30. Each of the displacement shafts 31 includes a support shaft portion 33 and a pivot shaft portion 34 that are parallel to each other and eccentric. Among these, the support shaft portion 33 is supported inside the circular hole 30 via a radial needle bearing 35. The power roller 11 is supported around the pivot shaft 34 via another radial needle bearing 38.

  A pair of displacement shafts 31 provided for each of the first and second cavities 21 and 22 are 180 degrees opposite to the input shaft 1 and the transmission shaft 103 for each of the first and second cavities 21 and 22. Is located. In addition, the direction in which each pivot shaft 34 of the displacement shaft 31 is eccentric with respect to each support shaft 33 is the same as the rotational direction of the input disks 2, 2 and the output disks 4, 4. The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Therefore, the power roller 11 is supported so that it can be slightly displaced along the longitudinal direction of the input shaft 1 and the transmission shaft 103. As a result, the power roller 11 tends to be displaced in the axial direction of the input shaft 1 and the transmission shaft 103 due to a variation in the amount of elastic deformation of the constituent members based on a variation in the torque transmitted by the toroidal continuously variable transmission. Even in this case, an excessive force is not applied to the component member, and the displacement can be absorbed.

  A thrust ball bearing 39 and a thrust bearing 40 such as a slide bearing or a needle bearing are provided between the outer peripheral surface of the power roller 11 and the inner peripheral surface of the trunnion 6 in order from the outer surface of the power roller 11. It has been. Among these, the thrust ball bearing 39 allows rotation of the power roller 11 while supporting a load in the thrust direction applied to the power roller 11. The thrust bearing 40 allows the pivot shaft 34 and the outer ring 41 to swing around the support shaft 33 while supporting a thrust load applied to the outer ring 41 of the thrust ball bearing 39 from the power roller 11. .

  A drive rod 42 is coupled to one end of the trunnion 6. A drive piston 43 is fixed to the outer peripheral surface of the intermediate portion of these drive rods 42. The drive piston 43 is oil-tightly fitted in the drive cylinder 44. The drive piston 43 constitutes an actuator for displacing the trunnion 5 in the axial direction.

  As shown in FIG. 12, a loading cam type pressing device 45 is provided between the input shaft 1 and one input side disk 2. The pressing device 45 includes a cam plate 46 and a plurality of rollers 48, and rotates one input-side disk 2 while pressing it toward the other input-side disk 2 based on the rotation of the input shaft 1. In this case, the cam plate 46 is spline-engaged with the intermediate portion of the input shaft 1, supported in a state where displacement in the axial direction is prevented, and rotates together with the input shaft 1. The plurality of rollers 48 are held by a holder 47 so as to be freely rollable.

  During operation of the toroidal continuously variable transmission configured as described above, the rotation of the input shaft 1 is transmitted to one input side disk 2 via the pressing device 45, and the input side disk 2 and the other input side disk are transmitted. The disk 2 rotates in synchronization with each other. The rotation of the input side disks 2 and 2 is transmitted to the output side disks 4 and 4 via the power roller 11. The rotation of the output side disks 4 and 4 is taken out by the output gear 110.

  When the rotational speed ratio between the input shaft 1 and the output gear 110 is changed, a pair is provided corresponding to the first and second cavities 21 and 22 based on switching of control valves (not shown). The drive piston 43 thus moved is displaced by the same distance in the opposite directions for each of the cavities 21 and 22. Along with the displacement of these drive pistons 43, a total of four trunnions 6 are displaced in the opposite direction, and one power roller 11 is displaced downward and the other power roller 11 is displaced upward. As a result, the tangential force acting on the contact portion between the peripheral surface of each power roller 11 and the inner side surfaces 2a and 2a of the input side disks 2 and 2 and the inner side surfaces 4a and 4a of the output side disks 4 and 4 The direction of changes. As the direction of the force changes, the trunnion 6 swings in the reverse direction around the pivot shaft 5 pivotally supported by the yokes 113a and 113b. As a result, the contact position between the peripheral surface of the power roller 11 and the input side disks 2 and 2 and the output side disks 4 and 4 changes, and the rotational speed ratio between the input shaft 1 and the output gear 110 changes. .

  By the way, in such a toroidal-type continuously variable transmission, power transmission between the power roller 11 and the input / output side disks 2 and 4 is non-contact by a traction force through an oil film in order to prevent damage to the surface of these members. (The interface between the power roller 11 formed by the oil film and the input / output side disks 2 and 4 is called a traction surface). Therefore, a sufficient amount of lubricating oil (traction oil) that can form an oil film for transmitting torque in a non-contact manner is supplied to the traction surface formed between the power roller 11 and the input / output side disks 2 and 4. There is a need to.

  Further, in such a toroidal-type continuously variable transmission, there is a problem that machining of the displacement shaft 31 is difficult, the cost of parts is increased, and the trunnion 6 is increased in size and weight in order to ensure support rigidity. Therefore, for example, in Patent Document 1, the position of the power roller 11 with respect to both the disks 2 and 4 is adjusted by supporting the power roller 11 so that it can move in parallel with the trunnion 6 in the direction orthogonal to the swing axis O. A linear motion support mechanism is disclosed.

  As shown in FIG. 14, a pair of slopes 215a and 215a whose slopes are opposite to each other in the longitudinal direction of the trunnion 6 are formed on the surface on the pocket P side in which the power roller 11 of the trunnion 6 is accommodated. A pair of slopes 215b and 215b parallel to these slopes 215a and 215a are also formed on the back surface of the outer ring 41 that rotatably supports the power roller 11, and a rolling element (roller) 217 is provided between these opposing slopes. A pair of linear motion bearings 218 are arranged. As a result, the power roller 11 can move in the width direction of the trunnion 6 (direction perpendicular to the paper surface), and the power roller 11 and both discs 2 accompanying the relative displacement of the components and the elastic deformation of the components as the trunnion 6 tilts. , 4 is adjusted. Further, the pair of linear motion bearings 218 inclined in opposite directions from each other causes a thrust direction (left-right direction in the figure) applied to the power roller 11 from the input-side and output-side disks 2, 4 and a longitudinal direction of the trunnion 6 (in the figure). Both forces acting in the vertical direction) can be received.

JP 2001-12574 A

  The linear motion bearing 218 holds not only the thrust force generated in the power roller 11 but also the traction force. This traction force acts to shift the power roller 11 in the direction of the tilt axis (pivot axis 5). Due to this shift, the power roller 11 is shifted from the central axis, side slip occurs, and the set gear ratio is shifted. (This is generally called torque shift). This not only makes shifting control difficult, but also adversely affects maneuverability.

  Accordingly, the one provided with the linear motion bearing 218 is advantageous for torque shift because there is no gap between the bearings that support the conventional pivot shaft type. However, as shown in FIG. 14, the intersection R of the normal lines L from the centers of the two bearings 218 of the pair of inclined surfaces 215a and 215b on the back surface of the outer ring 41 is an action point Q at which the power roller 11 receives the traction force. (In the figure, the height of the intersection R is far below the surface X), as shown in FIG. 15, a moment M is generated by the traction force. Rotation direction deviation is likely to occur, and torque shift occurs.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a toroidal continuously variable transmission that can reduce a torque shift by reducing a deviation in a rotation direction of a power roller.

In order to achieve the above object, the toroidal continuously variable transmission according to claim 1 includes an input side disk and an output side disk arranged coaxially with the first axis and facing the first axis direction. A plurality of power rollers sandwiched between the two disks, and a second axis that is twisted with respect to the first axis between the disks. A toroidal continuously variable transmission comprising: a trunnion; and an outer ring that is housed in a pocket provided in the second axially central portion of the trunnion and rotatably supports the power roller. A linear motion bearing is provided between the trunnion and the outer ring or an integral member integrally formed with the outer ring to support the outer ring so as to be movable in a direction perpendicular to the second axis. Said It provided respectively opposite on both sides of the central axis of the second axis and parallel to the outer ring, characterized in that is.

In the toroidal continuously variable transmission according to the present invention, a linear motion bearing is provided between the trunnion and the outer ring or an integral member integrally formed with the outer ring so as to support the outer ring in a direction perpendicular to the second axis. In addition to being provided, the linear motion bearings are provided opposite to each other on both sides of the central axis of the outer ring parallel to the second axis, so that the number of shaft support points is increased compared to the conventional one, Deviations that rotate on the linear bearing can be suppressed. Accordingly, it is possible to reduce the deviation in the rotation direction of the power roller and reduce the torque shift caused by the deviation.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. The feature of the present invention lies in the arrangement of the linear motion bearings, and the other configurations and operations are the same as the conventional configurations and operations described above. Therefore, in the following, only the features of the present invention will be referred to. Other parts will be described briefly with the same reference numerals as in FIGS.

  1 to 3 show a first embodiment of the present invention. As shown in the drawing, on the extension line on the right side of the rotation axis of the power roller 11, the input shaft 1 is provided so as to extend in a direction perpendicular to the paper surface, as in the prior art. The disk 2 and the output side disk 4 are provided so as to be rotatable around the axis (first axis) O1 of the input shaft 1 (see FIGS. 10 and 11). A power roller 11 is sandwiched between the toroidal inner surfaces of the input side disk 2 and the output side disk 4 facing each other.

  The trunnion 6 includes a bent plate-shaped main body portion 224, bent wall portions 226 provided at both ends (vertical end portions in FIG. 1), and a pivot shaft 5 extending outward from the bent wall portions 226. I have. In this case, each of the pivot shafts 5 and 5 has an axial direction between the discs 2 and 4 in the middle of the discs 2 and 4 with respect to the axial direction of the input and output discs 2 and 4, respectively. Are arranged at a twisted position in a direction perpendicular to the center axis of the discs 2 and 4 (see FIGS. 10 and 11), and are provided on the outer surfaces of both ends of each trunnion 6. Further, the main body portion 224 and the bent wall portion 226 form a pocket portion P that is a recess for housing the power roller 11 and the outer ring 41 that rotatably supports the power roller 11. The trunnion 6 has a closing portion 229 that extends to close the pocket portion P on the power roller 11 side. That is, the trunnion 6 forms a closed space that closes the pocket portion P by the main body portion 224, the bent wall portion 226, and the closing portion 229. In the present embodiment, the outer ring 41 and the displacement shaft 31 are integrally formed.

  The outer ring 41 is provided with an integral member (race) 240 that is integrated therewith. The integral member 240 has a main portion 240c extending along the main body portion 224 of the trunnion 6 (along the axis O (second axis) of the pivot shaft 5), and the axis O of the pivot shaft 5 from both sides of the main portion 240c. Leg portions 240b and 240b extending in a direction orthogonal to each other and a surrounding extending portion 240d extending along the closing portion 229 of the trunnion 6 so as to surround the power roller 11 are included.

  A pair of inclined surfaces (first inclined surfaces) 215a and 215a that are inclined inwardly (on the power roller 11 side) toward the end (on the pivot shaft 5 side) are formed on the end side of the inner surface of the main body 224 of the trunnion 6. ing. On the other hand, a pair of inclined surfaces (second inclined surfaces) 215b and 215b are formed at positions corresponding to the first inclined surfaces 215a and 215a on the outer surface of the main portion 240c of the integral member 240, respectively. A plurality of cylindrical rollers 217 (especially see FIG. 3) are arranged between the first inclined surfaces 215a and 215a and the second inclined surfaces 215b and 215b so that the axis thereof is along the maximum inclination angle direction of the inclined surfaces (see FIG. 1 is arranged in parallel (parallel to the paper surface) to constitute a linear motion bearing 218. As a result, the outer ring 41 and the integral member portion 240 can be translated in the width direction of the trunnion 6 (the direction orthogonal to the paper surface in FIG. 1) and are restricted in movement in the longitudinal direction of the trunnion 6. 6 is supported.

  A pair of inclined surfaces (first inclined surfaces) 215a and 215a that are inclined inwardly (on the power roller 11 side) toward the end (on the pivot 5 side) are also formed on the end side of the inner surface of the closed portion 229 of the trunnion 6. ing. On the other hand, a pair of inclined surfaces (second inclined surfaces) 215b and 215b are formed at positions corresponding to the first inclined surfaces 215a and 215a, respectively, on the outer surface of the surrounding extension portion 240d of the integrated member 240. A plurality of cylindrical rollers 217 are arranged between the first inclined surfaces 215a and 215a and the second inclined surfaces 215b and 215b so that the axis thereof is along the maximum inclination angle direction of the inclined surfaces (in FIG. 1, parallel to the paper surface). ) They are arranged in parallel and constitute a linear motion bearing 218. As a result, the outer ring 41 and the integral member portion 240 can be translated in the width direction of the trunnion 6 (the direction orthogonal to the paper surface in FIG. 1) and are restricted in movement in the longitudinal direction of the trunnion 6. 6 is supported.

  That is, in the present embodiment, the linear motion bearing 218 has both sides of the center axis O2 of the outer ring 41 parallel to the axis O of the pivot 5 (or the center axis of the main portion 240c of the integral member 240 parallel to the axis O of the pivot 5). Are provided on both sides of O3.

  Thus, in the present embodiment, the outer ring 41 is arranged between the trunnion 6 and the outer ring 41 (between the integral member 240 and the trunnion 6 integrated with the outer ring 41 in the present embodiment). A linear motion bearing 218 that is movably supported in a direction orthogonal to O is provided, and the linear motion bearing 218 is provided on both sides of the central axis O2 of the outer ring 41 parallel to the axis O (or an integral member 240 parallel to the axis O). Since the main support portion 240c is provided on both sides of the central axis O3 of the main portion 240c, the number of the shaft support portions is increased as compared with the conventional case, and a shift that rotates on the linear bearing 218 can be suppressed. Therefore, the shift in the rotation direction of the power roller 11 can be reduced, and the torque shift caused by the shift can be reduced.

  FIG. 4 shows a second embodiment of the present invention. As illustrated, in the present embodiment, the integral member 240 has an opening 240a in the surrounding extension portion 240d so as to open the pocket portion P on the power roller 11 side. Other configurations are the same as those in the first embodiment. Even with such a configuration, the same effects as those of the first embodiment can be obtained.

  FIG. 5 shows a third embodiment of the present invention. As illustrated, in the present embodiment, the integral member 240 is not provided with the surrounding extension 240d. Therefore, on the power roller 11 side with respect to the central axes O2 and O3, the linear motion bearing 218A is interposed between the ends of the leg portions 240b and 240b of the integral member 240 and the closed portion 229 of the trunnion 6. In this case, the linear motion bearing 218A is formed as a ball bearing. Other configurations are the same as those in the first embodiment. Therefore, even with such a configuration, it is possible to obtain the same effect as that of the first embodiment.

  FIG. 6 shows a fourth embodiment of the present invention. This embodiment is a modification of the third embodiment, and the trunnion 6 is not provided with the closing portion 229. Other configurations are the same as those of the third embodiment. Therefore, even with such a configuration, it is possible to obtain the same effect as that of the first embodiment.

  FIG. 7 shows a fifth embodiment of the present invention. As illustrated, in this embodiment, the integral member 240 does not have the surrounding extension portion 240d and the leg portions 240b and 240b, and the trunnion 6 does not have the closing portion 229. Therefore, on the power roller 11 side with respect to the central axis O2 (or O3), between both end portions of the main portion 240c of the integral member 240 and the flange portion 250 of the trunnion 6 protruding toward the pocket portion P side, A linear motion bearing 218 is inserted. Other configurations are the same as those in the first embodiment. Therefore, the same effect as the first embodiment can be obtained.

  FIG. 8 shows a sixth embodiment of the present invention. This embodiment is a modification of the fifth embodiment, and is the same as the fifth embodiment except that the outer ring 41 and the integral member 240 are integrally formed. Therefore, the same effect as the first embodiment can be obtained.

  FIG. 9 shows a seventh embodiment of the present invention. This embodiment is a modification of the fourth embodiment, and is the same as the fourth embodiment except that the outer ring 41 and the integral member 240 are integrally formed. Therefore, the same effect as the first embodiment can be obtained.

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

The principal part of the toroidal type continuously variable transmission which concerns on the 1st Embodiment of this invention is shown, It is sectional drawing which follows the BB line of (a) of FIG. (A) is a top view of the part shown by FIG. 1, (b) is a front view of the part shown by FIG. 1, (c) is a perspective view of the part shown by FIG. (A) is a top view which shows the state which pulled the outer ring | wheel, the integral member, and the power roller from the pocket part of the trunnion, (b) is a perspective view which shows the state which pulled the outer ring | wheel, the integral member, and the power roller from the pocket part of the trunnion. is there. It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on the 2nd Embodiment of this invention. It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on the 3rd Embodiment of this invention. It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on the 4th Embodiment of this invention. It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on the 5th Embodiment of this invention. It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on the 6th Embodiment of this invention. It is principal part sectional drawing of the toroidal type continuously variable transmission which concerns on the 7th Embodiment of this invention. It is a side view which shows the fundamental structure of the toroidal type continuously variable transmission conventionally known in the state at the time of maximum deceleration. It is a side view which shows the basic structure of the toroidal type continuously variable transmission conventionally known in the state at the time of maximum acceleration. It is sectional drawing which shows an example of the conventional concrete structure. It is sectional drawing which follows the AA line of FIG. It is principal part sectional drawing of the toroidal type continuously variable transmission which has a linear motion bearing, and the conventional structure from which the intersection of the normal lines from the center of a linear motion bearing is greatly separated from the surface where a power roller receives traction force It is a principal part sectional view shown. It is principal part sectional drawing which shows the state which the torque shift produced in the structure of FIG.

Explanation of symbols

2 Input side disk 4 Output side disk 6 Trunnion 11 Power roller 41 Outer ring 215a, 215b Slope 218, 218a Linear motion bearing 240 Integral member

Claims (1)

An input side disk and an output side disk arranged coaxially with the first axis and facing the first axis direction, a plurality of power rollers sandwiched between these two disks, A trunnion provided so as to be swingable about a second axis that is twisted with respect to the first axis, and a pocket provided in the central portion of the trunnion in the second axial direction. In a toroidal continuously variable transmission that is housed and includes an outer ring that rotatably supports the power roller,
A linear motion bearing is provided between the trunnion and the outer ring or an integral member integral with the outer ring to support the outer ring so as to be movable in a direction perpendicular to the second axis.
The toroidal continuously variable transmission, wherein the linear motion bearings are provided on opposite sides of a center axis of the outer ring parallel to the second axis.

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