JP2016200208A - Toroidal type non-stage transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a toroidal type non-stage transmission capable of restricting fretting wear on contact surfaces between a piston part and a disk constituting a pressing device without increase in the number of parts and cost.SOLUTION: Since contact surfaces 82a and 83a between an input side disk 2 and a piston part 83 are inclined toward the shaft side of the input side disk 2 as it goes from the cylinder part 81 side to the input side disk 2 side, a force directed outward in a radial direction of the input side disk 2 is applied to the input side disk 2 from the piston part 83, and this force resists a force acting on the input side disk 2 so as to fall down toward the shaft side of its outer diameter portion. Since the falling of the input side disk 2, which is therefore considered as a cause of fretting wear, can be restricted, the fretting wear on the contact surfaces 82a and 83a between the input side disk 2 and the piston part 83 can be restricted.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a toroidal continuously variable transmission that can be used for transmissions of automobiles and various industrial machines.

  For example, a double-cavity toroidal continuously variable transmission used as an automobile transmission is configured as shown in FIGS. As shown in FIG. 3, an input shaft 1 is rotatably supported inside the casing 50, and two input side disks 2, 2 and two output side disks 3 are disposed on the outer periphery of the input shaft 1. 3 is attached. An output gear 4 is rotatably supported on the outer periphery of the intermediate portion of the input shaft 1. Output side disks 3 and 3 are connected to cylindrical flange portions 4a and 4a provided at the center of the output gear 4 by spline coupling.

  The input shaft 1 is driven to rotate by a drive shaft 22 via a loading cam type pressing device 12 provided between an input side disk 2 and a cam plate (loading cam) 7 located on the left side in the drawing. It has become. The output gear 4 is supported 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. A power roller is provided between the inner side surfaces (concave surface; also referred to as a traction surface) 2a and 2a of the input side disks 2 and 2 and the inner side surfaces (concave surface; also referred to as a traction surface) 3a and 3a of the output disks 3 and 3. 11 (see FIG. 4) 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. 3, 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. 3) of the input side disk 2 is abutted against a loading nut 9 screwed into a screw portion formed on the outer peripheral surface of the input shaft 1. Thereby, the displacement of the input side disk 2 in the direction of the axis O with respect to the input shaft 1 is substantially prevented. Further, a disc spring 8 is provided between the cam plate 7 and the flange 1d of the input shaft 1, and this disc spring 8 is a concave surface 2a, 2a, 3a of each disk 2, 2, 3, 3. , 3a and 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 about a pair of pivots 14, 14 that are twisted with respect to the input shaft 1 are provided inside the casing 50. In FIG. 4, the input shaft 1 is not shown. Each trunnion 15, 15 has 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 side surface 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 center portion of the support plate portion 16, and a base end portion (first shaft 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. In addition, each power roller 11 is rotatably supported around the tip end portion (second shaft portion) 23b of the displacement shaft 23 protruding from the inner surface of each trunnion 15, 15. 11 is sandwiched between the input disks 2 and 2 and the output disks 3 and 3. In addition, the base end part 23a and the front-end | tip part 23b of each displacement shaft 23 and 23 are mutually eccentric.

  The pivot shafts 14 and 14 of the trunnions 15 and 15 are supported so as to be swingable and displaceable in the axial direction (vertical direction in FIG. 4) with respect to the pair of yokes 23A and 23B, respectively. The horizontal movement of the trunnions 15 and 15 is restricted by 23B. Each yoke 23A, 23B is formed in a rectangular shape by pressing or forging a metal such as steel. Four circular support holes 18 are provided at the four corners of each of the yokes 23 </ b> A and 23 </ b> B, and the pivot shafts 14 provided at both ends of the trunnion 15 swing through the radial needle bearings 30. It is supported freely. In addition, a circular locking hole 19 is provided in the central portion of the yokes 23A and 23B in the width direction (the left-right direction in FIG. 3), and the inner peripheral surface of the locking hole 19 is a cylindrical surface. 64 and 68 are fitted inside. That is, the upper yoke 23A is swingably supported by the spherical post 64 supported by the casing 50 via the fixing member 52, and the lower yoke 23B is supported by the spherical post 68 and the drive for supporting the same. The upper cylinder body 61 of the cylinder 31 is swingably supported.

  The displacement shafts 23 and 23 provided in the trunnions 15 and 15 are provided at positions 180 degrees opposite to the input shaft 1. Further, the direction in which the distal end portion 23b of each of the displacement shafts 23, 23 is eccentric with respect to the base end portion 23a is the same direction as the rotational direction of both the disks 2, 2, 3, 3 (in FIG. (Reverse direction). Further, the eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 1 is disposed. Accordingly, the power rollers 11 and 11 are supported so that they can be slightly displaced in the longitudinal direction of the input shaft 1. As a result, even if each power roller 11, 11 tends to be displaced in the axial direction of the input shaft 1 due to elastic deformation of each component member based on the thrust load generated by the pressing device 12, each component This displacement is absorbed without applying an excessive force to the member.

  Further, between the outer surface of the power roller 11 and the inner surface of the support plate portion 16 of the trunnion 15, a thrust ball bearing (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, driving rods (trunnion shafts) 29 and 29 are provided at one end portions (lower end portions in FIG. 4) of the trunnions 15 and 15, respectively, and a driving piston ( Hydraulic pistons) 33, 33 are fixed. Each of these drive pistons 33 and 33 is oil-tightly fitted in a drive cylinder 31 constituted by an upper cylinder body 61 and a lower cylinder body 62. The drive pistons 33 and 33 and the drive cylinder 31 constitute a drive device 32 that displaces the trunnions 15 and 15 in the axial direction of the pivots 14 and 14 of the trunnions 15 and 15.

  In the case of the toroidal 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. 4 is displaced to the lower side in the figure, and the power roller 11 on the right side in the figure is displaced to the upper side in the figure.

  As a result, the peripheral surfaces 11a and 11a of the power rollers 11 and 11 act on contact portions of the input side disks 2 and 2 and the inner side surfaces 2a, 2a, 3a and 3a of the output side disks 3 and 3, respectively. The direction of the tangential force changes. As the force changes, the trunnions 15 and 15 swing (tilt) in opposite directions around the pivots 14 and 14 pivotally supported by the yokes 23A and 23B.

  As a result, the contact position between the peripheral surfaces 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.

By the way, in a toroidal-type continuously variable transmission, a hydraulic pressing device that is expected to improve fuel consumption and reduce costs may be used as a pressing device for securing the surface pressure of the traction portion.
In the conventional toroidal type continuously variable transmission equipped with this hydraulic pressing device, fretting wear at the contact surface between the piston portion and the input side disk becomes a problem, and when the fretting wear increases, Burn-in may occur on the surface.

The cause of this fretting wear is as follows.
In the toroidal type continuously variable transmission, in order to transmit power from the input side disk 2 to the output side disk 3 as shown in FIG. 5, a plurality of (usually two or three) powers per one cavity. A roller 11 is used. Further, in order to perform traction drive on the contact surface between the disks 2 and 3 and the power roller 11, it is necessary to generate a pressing force from the back surface of the input side disk 2. At this time, because of the presence or absence of the power roller 11 depending on the phase, that is, the input side disc 2 has a portion where the power roller 11 abuts and a portion where the power roller 11 does not abut, Deforms asymmetrically. That is, the input side disk 2 is repeatedly elastically deformed based on the force received from the power roller 11 so that the portion near the outer diameter of the input side disk 2 falls in a direction approaching the shaft side.
In this way, the contact state of the input side disc 2 and the abutting portion (contact portion) of the piston portion that presses the input side disc 2 to generate a pressing force differs depending on the phase, and is closer to the outer diameter of the input side disc 2. Since the portion is repeatedly elastically deformed, fretting wear occurs at the abutting portion (contact portion) when the pressing force is large and the deformation of the input side disk 2 is large or when the operation is performed at a high speed.

Patent Documents 1 and 2 are known as examples of toroidal type continuously variable transmissions that suppress fretting wear at the contact portion between the piston portion and the input side disk.
In the toroidal-type continuously variable transmission described in Patent Document 1, a rolling bearing is disposed at the abutting portion (abutting portion) between the piston portion of the hydraulic pressure device and the input side disk, and fretting wear is achieved by rolling the bearing. Is suppressed.
Further, in the toroidal-type continuously variable transmission described in Patent Document 2, fretting wear is achieved by disposing an anti-wear shim on the piston portion of the hydraulic pressing device and the abutting portion (contact portion) of the input side disk. Is suppressed.

JP 2011-149481 A JP 2007-2928 A

However, in the toroidal type continuously variable transmission described in Patent Document 1, an increase in the number of parts and an increase in cost due to the arrangement of the bearings become a problem, and the rolling element contact portion has a high surface pressure, which promotes wear and fretting wear. There is concern.
In addition, in the toroidal type continuously variable transmission described in Patent Document 2, an increase in the number of parts and an increase in cost due to the addition of shims are problematic.

  The present invention has been made in view of the above circumstances, and can suppress fretting wear on the contact surface between the piston portion and the disk constituting the pressing device without increasing the number of parts and increasing the cost. An object is to provide a toroidal type continuously variable transmission.

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 provided concentrically and rotatably in a state in which the respective inner side surfaces face each other. And a power roller sandwiched between the two disks, and a hydraulic chamber on the back side of one of the input side disk and the output side disk, and exerts a pressing force on both the disk and the power roller. In a toroidal type continuously variable transmission provided with a hydraulic pressing device to be applied,
The pressing device includes a cylinder part that constitutes the hydraulic chamber, and a piston part that is provided in the cylinder part and comes into contact with the one disk.
A contact surface between the one disk and the piston part is inclined toward the shaft side of the one disk as it goes from the cylinder part side to the one disk side.

In the present invention, the abutting surface between one disk and the piston portion is inclined toward the shaft side of the one disk as it goes from the cylinder portion side to the one disk side. When abutting against and pressing the disc, a force is exerted on the disc from the piston portion toward the outer side in the radial direction of the disc, and this force falls on the disc in a direction in which the portion closer to the outer diameter approaches the axial side. Resist the forces acting like. For this reason, since the fall of the disk considered to be the cause of fretting wear can be suppressed, fretting wear on the contact surface between the disk and the piston portion can be suppressed.
In addition, since the contact surface between the one disk and the piston portion is merely inclined, the dimensions are increased in the radial and axial directions of the disk and the piston portion without increasing the number of parts and increasing the cost. There is nothing.

In the configuration of the present invention, crowning may be applied to at least a part of at least one of the contact surfaces of the one disk and the piston portion.
Here, the term “crowning” refers to processing at least a part of the surface shape of the abutting surface into a medium height (middle).

  Due to the deformation of the disk and the piston part and the inaccuracy of the processing of the inclined contact surface between the two, the surface pressure of the contact surface may increase locally and stress concentration may occur. Since at least a part of at least one of the contact surfaces of the piston portion and the piston portion is crowned, such stress concentration can be prevented.

  According to the present invention, the contact surface between the one disk and the piston portion is inclined toward the shaft side of the one disk from the cylinder side toward the one disk side. It is possible to suppress the fall of the disc that is considered. Therefore, fretting wear on the contact surface between the piston portion and the disk can be suppressed without causing an increase in the number of parts and an increase in cost.

BRIEF DESCRIPTION OF THE DRAWINGS The pressing apparatus of the toroidal type continuously variable transmission which concerns on the 1st Embodiment of this invention is shown, (a) is a half sectional view of a pressing apparatus, (b) is sectional drawing of the principal part. It is sectional drawing of the principal part which shows the state which formed the crowning surface in the contact surface of an input side disk and piston part. It is sectional drawing which shows an example of the conventional toroidal type continuously variable transmission. It is sectional drawing which follows the AA line in FIG. It is a perspective view which shows the arrangement | positioning relationship between the disk of a toroidal type continuously variable transmission, and a power roller.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
The feature of the toroidal type continuously variable transmission of the present embodiment is the configuration of the pressing device, and the other configurations and operations are substantially the same as the conventional configuration and operations described above. The characteristic part will be described.

1A and 1B show a pressing device 80 of a toroidal type continuously variable transmission according to the present embodiment. FIG. 1A is a half sectional view of the pressing device 80, and FIG.
As shown in FIG. 1A, a hydraulic pressing device 80 that presses the input side disk 2 in the axial direction is provided on the back surface 2 d side of the input side disk 2 positioned on the input side of the input shaft 1. Yes.
The pressing device 80 includes a first cylinder portion 81 coupled to a base end portion (left end portion in FIG. 1A) 1 e of the input shaft 1 and a second cylinder portion 82 provided on the input side disk 2. And an annular first piston portion (hydraulic piston) 83 and an annular second piston portion (hydraulic piston) 84.

  The first cylinder part 81 is formed in a substantially bottomed cylindrical shape, the cylindrical part is located outside the outer periphery of the second cylinder part 82, and the bottom part is the back surface (outer surface) 2d of the input side disk 2. It is arranged in a state of facing. Further, the bottom portion of the first cylinder portion 81 is fixed by being fitted around the input shaft 1. The second cylinder portion 82 is formed in a cylindrical shape and extends from the outer peripheral edge of the input side disk 2 toward the first piston portion 83.

  The second piston portion 84 has an inner peripheral surface fitted to the outer peripheral surface of the input shaft 1 and an outer peripheral surface fitted to the inner peripheral surface of the second cylinder portion 82. It is arranged in a state facing the rear surface 2d of the. The first piston portion 83 has an inner peripheral surface fitted to the outer peripheral surface of the input shaft 1 and an outer peripheral surface fitted to the inner peripheral surface of the first cylinder portion 81. The second piston portion 84 and the first cylinder portion 81 are disposed.

A space surrounded by the inner surface of the first cylinder portion 81, the first piston portion 83, and a part of the outer peripheral surface of the input shaft 1 constitutes a first hydraulic chamber 85. The first hydraulic chamber 85 is kept fluid tight by a plurality of seal members 86 and 87.
In addition, the space surrounded by the inner peripheral surface of the second cylinder portion 82, the second piston portion 84, the back surface 2d of the input side disk 2, and a part of the outer peripheral surface of the input shaft 1 is a second space. The hydraulic chamber (oil chamber) 90 is configured. The second hydraulic chamber 90 is kept fluid tight by a plurality of seal members 91 and 92.

  Further, on the inner peripheral side of the second cylinder portion 82, a space 93 located between the second piston portion 84 and the first piston portion 83 is an air chamber. The air chamber 93 is kept fluid tight by a plurality of seal members 87 and 91. Further, the second cylinder portion 82 can come into contact with the first piston portion 83. Then, using a part of the first hydraulic chamber 85, a disc spring 94 for applying a preload is inserted between the first piston portion 83 and the first cylinder portion 81. The first piston portion 83 that is movable along the input shaft 1 is urged toward the input side disk 2 with respect to the cylinder portion 81.

Further, as shown in FIG. 1 (b), the contact surface between the input side disk 2 and the (first) piston portion 83 is the (first) cylinder portion 81 side (left side in FIG. 1 (b)). As it goes from the input side disk 2 side (right side in FIG. 1B) toward the input side disk 2, it is inclined toward the axis O side of the input side disk 2.
That is, the front end surface 82a of the cylinder portion 82 of the input side disk 2 is a contact surface 82a with which the piston portion 83 abuts, and the abutment surface 82a becomes closer to the right side from the left side in FIG. The inclined surface is inclined downward (on the shaft side).
Further, a contact surface 83a that contacts the contact surface 82a is provided on the outer peripheral portion of the side surface of the annular piston 83 facing the input side disk 2, and this contact surface 83a is shown in FIG. In addition, the inclined surface is inclined downward (shaft side) from the left side toward the right side.
Further, the inclination angles of the contact surfaces 82a and 83a (inclination angle with respect to the input shaft 1) are equal, and the lengths of the contact surfaces 82a and 83a in the inclination direction are substantially equal.

  Further, as shown in FIG. 1A, an oil passage is formed on the drive shaft on the engine side in order to supply oil to the hydraulic chambers 85 and 90. Specifically, an oil passage 95 that is inclined at a predetermined angle with respect to the input shaft 1 is provided at the base end portion 1 e of the input shaft 1 so as to extend to the vicinity of the inner peripheral surface of the second piston portion 84. . An oil passage 96 is branched from the middle of the oil passage 95, and pressure oil is supplied from the oil passage 96 to the first hydraulic chamber 85. An oil passage 97 is connected to the tip of the oil passage 95, and pressure oil is supplied from the oil passage 97 to the second hydraulic chamber 90 through an oil passage 98 provided in the inner peripheral portion of the second piston portion 84. It comes to be supplied.

In such a pressing device 80, pressure oil of a predetermined pressure is fed into the first hydraulic chamber 85 and the second hydraulic chamber 90. Then, a force is generated in the hydraulic chambers 85 and 90 in the direction in which the axial dimensions of the hydraulic chambers 85 and 90 increase.
When pressure oil is fed into the first hydraulic chamber 85, the first piston portion 83 is pressed to the right side (input side disk 2 side) in FIG. 1 (a), thereby being integrated with the back surface of the input side disk 2. The input side disk 2 is pressed rightward through the formed second cylinder portion 82. That is, the contact surface 83a of the first piston portion 83 contacts the contact surface 82a of the second cylinder portion 82, and the input is performed by pressing the contact surface 82a to the right side in FIG. The side disk 2 is pressed to the right.

On the other hand, when the pressure oil is fed into the second hydraulic chamber 90, the movement of the second piston portion 84 to the left side in FIG. 1A is restricted, so that the input side disk 2 is pressed to the right side. .
The forces generated in both the hydraulic chambers 85 and 90 as described above both push the input side disk 2 toward the output side disk (not shown) (right side) and push the input shaft 1 toward the base end side (FIG. ) Is applied to the other side as a force in the direction of pressing the other input side disk (not shown) against the output side disk (not shown).

Here, when the contact surface 83a of the first piston portion 83 contacts the contact surface 82a of the second cylinder portion 82 and the contact surface 82a is pressed to the right in FIG. On the surface 82a, that is, the input side disk 2, a force Fr directed from the contact surface 83a to the radially outer side (upper side in FIG. 1B) of the input side disk 2 and an inner side in the axial direction (right side in FIG. 1B) ) Force Fa.
On the other hand, the input side disk 2 is such that the portion closer to the outer diameter of the input side disk 2 falls in a direction approaching the shaft side as indicated by an arrow A based on a force Fc received from a power roller (not shown). Repeated elastic deformation.
Therefore, the force Fr directed outward in the radial direction of the input side disk 2 resists the force acting on the input side disk 2 so as to tilt the portion closer to the outer diameter toward the axis side. For this reason, since the fall of the input side disk 2 considered to be the cause of fretting wear can be suppressed, fretting wear at the contact surfaces 82a and 83a between the input disk 2 and the piston portion 83 can be suppressed.

As described above, according to the present embodiment, since the falling of the input side disk 2 considered to be the cause of fretting wear can be suppressed, the fretting wear on the contact surfaces 82a and 83a between the input side disk 2 and the piston portion 83 is prevented. Can be suppressed.
Further, since the contact surfaces 82a and 83a between the input side disk 2 and the piston portion 83 are only inclined, the diameters of the input side disk 2 and the piston portion 83 are not increased without increasing the number of parts and the cost. There is no increase in dimensions in the direction and axial direction.

In this embodiment, the contact surfaces 82a and 83a between the cylinder part 82 and the piston part 83 of the input side disk 2 are conical, but the cylinder part 82 and the piston part 83 of the input side disk 2 Crowning may be applied to at least a part of at least one of the contact surfaces 82a and 83a.
For example, as shown in FIG. 2A, a crowning surface 83b may be formed on a radially inner portion of the contact surface 83a of the piston portion 83, or as shown in FIG. A crowning surface 83c may be formed on the radially outer portion of the contact surface 83a.
Further, as shown in FIG. 2C, a crowning surface 82b may be formed on the radially inner portion of the contact surface 82a of the cylinder portion 82 of the input side disk 2, or the contact surface of the cylinder portion 82 may be formed. A crowning surface 82c may be formed on the radially outer portion of 82a.

  Due to the deformation of the input side disk 2 and the piston part 83 and the influence of the processing accuracy of the inclined contact surfaces 82a and 83a inclined between them, the surface pressure of the contact surfaces 82a and 83a locally increases and stress concentration occurs. However, as described above, such stress concentration can be prevented by forming the crowning surfaces 82b, 82c, 83b, 83c on at least a part of the contact surfaces 82a, 83a.

  Further, in the present embodiment, the toroidal type continuously variable transmission provided with the double cylinder type pressing device 80 having the first cylinder part 81 and the second cylinder part 82 has been described as an example. You may apply to the toroidal type continuously variable transmission provided with the single cylinder type pressing device which has only the part 81. FIG.

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

2 Input side disk 3 Output side disk 11 Power roller 80 Press device 81 Cylinder part 82 Cylinder part 83 Piston part 82a, 83a Contact surface 82b, 82c, 83b, 83c Crowning surface 85 Hydraulic chamber

Claims (2)

An input side disk and an output side disk provided concentrically and rotatably with the respective inner side surfaces facing each other, a power roller sandwiched between the two disks, the input side disk, and the disk In a toroidal continuously variable transmission having a hydraulic chamber on the back side of one of the output side disks and a hydraulic pressing device that applies a pressing force to both the disks and the power roller,
The pressing device includes a cylinder part that constitutes the hydraulic chamber, and a piston part that is provided in the cylinder part and comes into contact with the one disk.
A toroidal type characterized in that the contact surface between the one disk and the piston part is inclined toward the axis side of the one disk as it goes from the cylinder part side to the one disk side. Continuously variable transmission.   2. The toroidal continuously variable transmission according to claim 1, wherein crowning is applied to at least a part of at least one of the contact surfaces of the one disk and the piston portion.

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