JP2002181151A - Toroidal-type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the durability of a displacement shaft in a toroidal-type continuously variable transmission having a displacement shaft integrated with an outer ring of a thrust rolling bearing. SOLUTION: A layer hardened by heating treatment is formed on a surface of the displacement shaft 81. Corner parts F formed by a supporting shaft part 83 and the outer ring 84, corner parts G formed by the outer ring 84 and a pivoting part 82, and a corner part formed by a large part 85 and a small part 86 of the pivoting part 82 are respectively worked after the formation of the hardened layer, and an abnormally heated layer in the hardened layer is eliminated by these workings.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a toroidal type continuously variable transmission used for a transmission of an automobile.

[0002]

2. Description of the Related Art Conventionally, as a vehicle transmission, for example,
2. Description of the Related Art A toroidal type continuously variable transmission as shown in FIGS. 2 and 3 is known. In this toroidal type continuously variable transmission, an input side disk 2 is provided so as to have the same central axis as the input shaft 1, and an output side is provided at an end of an output shaft 3 arranged so as to have the same central axis as the input shaft 1. The disk 4 is fixed. Inside the casing containing the toroidal type continuously variable transmission,
Plural units (2 in this example) swinging about pivots 5 and 5
) Trunnions 6 and 6 are provided. That is,
Each of the pivots 5, 5 is provided at an intermediate portion between the two disks 2, 4 with respect to the axial direction (the left-right direction in FIGS. 2 and 3) of the two disks 2, 4 on the input side and the output side. The trunnions 6, 6 are provided on the outer surfaces of both ends of the trunnions 6, 6 in a direction orthogonal to the axial direction and at a position twisted with respect to the central axis of the two disks 2, 4.

[0003] In the middle of each trunnion 6,6,
The base ends of the displacement shafts 7, 7 are supported, and the respective pivots 5, 5
By swinging the trunnions 6 around the center, the inclination angles of the displacement shafts 7 change. Each of the displacement shafts 7, 7 has a power roller 8,
8 is rotatably supported. These power rollers 8, 8 are sandwiched between both the input side and output side disks 2, 4. In other words, the inner surfaces 2a and 4a of the input and output disks 2 and 4 facing each other respectively define an arc centered on the pivot 5 with the input shaft 1 and the output shaft 3.
Are formed on the concave surface obtained when rotating around the center, and the peripheral surfaces 8a, 8a of the power rollers 8, 8 formed as spherical convex surfaces are in contact with these inner surfaces 2a, 4a.

[0004] Between the input shaft 1 and the input side disk 2,
A loading cam type pressing device 9 is provided, and the input side disk 2 is connected to the output side disk 4 by the pressing device 9.
Pressed toward. The pressing device 9 includes the input shaft 1
And a plurality of (for example, four) rollers 12 held by a holder 11. On one side surface (left side surface in FIGS. 2 and 3) of the cam plate 10, a cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and an outer side surface of the input side disk 2 (right side in FIGS. 2 and 3). Surface), a similar cam surface 14 is formed, between which a plurality of rollers 12 are rotatably supported about a radial axis with respect to the center of the input shaft 1. .

In the toroidal type continuously variable transmission configured as described above, when the cam plate 10 rotates with the rotation of the input shaft 1, the cam surface 13 causes the plurality of rollers 12 to move to the outer surface of the input side disk 2. To the cam surface 14. As a result, the input side disk 2 is pressed by the two power rollers 8, 8 and the input side disk 2 is pressed based on the pressing of the pair of cam surfaces 13, 14 and the plurality of rollers 12.
Rotates. Then, the rotation of the input side disk 2 is
The power is transmitted to the output disk 4 via both power rollers 8, 8, and the output shaft 3 fixed to the output disk 4 rotates.

When the rotational speed ratio (speed change ratio) between the input shaft 1 and the output shaft 3 is changed, and when the speed between the input shaft 1 and the output shaft 3 is reduced, the pivots 5 and 5 are As shown in FIG. 2, the peripheral surfaces 8a, 8a of the power rollers 8, 8
The displacement shafts 7, 7 are inclined so as to abut against the central portion of the inner surface 2a of the inner surface 2a and the outer peripheral portion of the inner surface 4a of the output side disk 4, respectively. On the other hand, when increasing the speed, the trunnions 6, 6 are swung about the pivots 5, 5, so that the peripheral surfaces 8a, 8a of the power rollers 8, 8, as shown in FIG. Each of the displacement shafts 7 is tilted so as to abut on a portion of the inner surface 2a of the disk 2 near the outer periphery and a portion of the inner surface 4a of the output side disk 4 near the center, respectively. If the inclination angles of the displacement shafts 7, 7 are set between those in FIGS. 2 and 3, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIGS. 4 and 5 show a more specific toroidal-type continuously variable transmission. In this toroidal type continuously variable transmission, the input side disk 2 and the output side disk 4 are each provided with a needle bearing 16,
It is rotatably supported via 16. Further, the cam plate 10 is spline-engaged with the outer peripheral surface of the end portion (the left end portion in FIG. 4) of the input shaft 15, and is prevented from moving in the direction away from the input side disk 2 by the flange portion 17. The cam plate 10 and the rollers 12, 12 constitute a loading cam type pressing device 9 for rotating the input disk 2 while pressing the input disk 2 toward the output disk 4 based on the rotation of the input shaft 15. are doing. Output disk 4
, The output gear 18 is connected by keys 19, 19,
The output side disk 4 and the output gear 18 rotate integrally. The output gear 18 and a gear (not shown) meshed with the output gear 18 constitute a power take-out means for taking out the rotation of the output side disk 4.

The pivots 5, 5 provided at both ends of the pair of trunnions 6, 6 are swingably and axially (front and back in FIG. 4, and left and right in FIG. 5) on the pair of support posts 20, 20, respectively. It is displaceably supported. The pair of support posts 20, 20 are formed in a plate shape having sufficient rigidity, and circular holes 21, 21 formed in the central portions of the support posts 20, 20 are respectively formed on the inner surface of the casing 22 and the casing 22. By being externally fitted to support pins 24a, 24b fixed to the side surface of a cylinder case 23 provided therein, the cylinder is supported inside the casing 22 so as to be swingable and displaceable in the axial direction of each of the pivots 5, 5. ing. Further, circular support holes 25 are formed at both end portions of the support posts 20, 20, respectively.
The respective pivots 5, 5 provided at both ends of the trunnions 6, 6 are supported by radial needle bearings 27, 27 having outer rings 26, 26, respectively. With these configurations, the trunnions 6 and 6 are supported in the casing 22 so as to be swingable about the respective pivots 5 and 5 and displaceable in the axial direction of the respective pivots 5 and 5.

[0009] Displacement shafts 7, 7 are supported in circular holes 40, 40 formed in the intermediate portions of the trunnions 6, 6, respectively. Each displacement shaft 7 includes a support shaft 28 and a pivot shaft 29 which are parallel and eccentric to each other. Each support shaft 2
8 is a radial needle bearing 30 inside each circular hole 40.
And is swingably supported via the. A power roller 8 is rotatably supported on the outer peripheral portion of each pivot shaft portion 29 via a radial needle bearing 31.

The pair of displacement shafts 7, 7 are arranged so as to be symmetrical with respect to the input shaft 15 (a position opposite by 180 degrees). Further, each of the pivot shafts 29, 29 of each of the displacement shafts 7, 7 is connected to each of the support shafts 28, 2
The direction eccentric with respect to 8 is the same direction (left and right opposite directions in FIG. 5) with respect to the rotation direction of both the input side and output side disks 2 and 4. Further, the axial direction of each pivot shaft portion 29, 29 is the axial direction of the input shaft 15 (the left-right direction in FIG.
The direction is substantially orthogonal to the direction (front and back in FIG. 5). Therefore, the power rollers 8, 8 are supported while allowing a slight displacement in the axial direction of the input shaft 15. As a result, even if each of the power rollers 8, 8 is slightly displaced in the axial direction of the input shaft 15 due to variations in dimensional accuracy of the constituent components or elastic deformation during power transmission, the displacement can be absorbed. Also, no excessive force is applied to each component.

Further, between the outer surface of each of the power rollers 8, 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6,
Thrust rolling bearings 32, 32, such as thrust ball bearings, and thrust bearings 34, 34, such as thrust needle bearings for supporting a thrust load applied to the outer rings 33, 33, which will be described later. Is provided. Of these, thrust rolling bearings 32, 32
The rotation of each of the power rollers 8, 8 is allowed while supporting the load in the thrust direction applied to each of the power rollers 8, 8. Further, the respective thrust bearings 34, 34 are connected to the outer ring 3 of the respective thrust rolling bearings 32, 32 from the respective power rollers 8, 8.
The pivot shafts 29, 29 and the outer rings 33, 33 are supported by the support shafts 28, 28 while supporting the thrust load applied to the shafts 3, 33.
Swinging around the center.

Further, one end of each trunnion 6, 6 (FIG. 5)
Drive rods 35, 35 at the left end, respectively).
And a drive piston 36 is fixedly provided on the outer peripheral surface of the intermediate portion of each of the drive rods 35, 35. Each of the drive pistons 36, 36 is oil-tightly fitted in a drive cylinder 37, 37 provided in the cylinder case 23, respectively.
Further, a pair of rolling bearings 39 are provided between the support wall 38 provided in the casing 22 and the input shaft 15, and the input shaft 15 is rotatably supported in the casing 22.

In the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 15 is transmitted to the input side disk 2 via the pressing device 9. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8, 8, and the rotation of the output side disk 4 is extracted from the output gear 18. When changing the rotation speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 36, 36 are displaced in opposite directions. Then, each of these drive pistons 36,
The pair of trunnions 6 and 6 are displaced in opposite directions in accordance with the displacement of 36. For example, in FIG. 5, the lower power roller 8 is displaced to the right in FIG. 5, and the upper power roller 8 is displaced to the left in FIG. As a result, the direction of the tangential force acting on the contact portions between the peripheral surfaces 8a, 8a of these power rollers 8, 8 and the inner surfaces 2a, 4a of the input side disk 2 and the output side disk 4 changes. .
Then, with the change in the direction of this force, each trunnion 6,
6 swing in opposite directions in FIG. 4 about pivots 5, 5 pivotally supported by the support posts 20, 20, respectively. As a result, as shown in FIGS. 2 and 3 described above, the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a
, The rotational speed ratio between the input shaft 15 and the output gear 18 changes.

When each of the power rollers 8, 8 is displaced in the axial direction of the input shaft 15 as a result of elastic deformation of the components during power transmission, each of the displacement shafts pivotally supporting the power rollers 8, 8 is displaced. 7, 7 slightly swing about the respective support shafts 28, 28. As a result of this swing, the outer surfaces of the outer rings 33, 33 of the thrust rolling bearings 32, 32 and the inner surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust bearings 34 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, as described above, the force for changing the inclination angle of each of the displacement shafts 7 can be small.

Japanese Patent Application Laid-Open No. 11-51140 discloses that the inclination of the support shaft is suppressed by constraining the support shaft with a back plate so that the toroidal-type continuously variable transmission can operate regardless of the shift operation state. In order to stably maintain a predetermined gear ratio, as shown in FIG.
A displacement shaft 54 in which an outer ring 53 of a thrust rolling bearing is integrally formed in addition to the pivot shaft portion 51 and the support shaft portion 52 has been proposed.

[0016]

By the way, as shown in FIG. 7, the power roller 8 has a peripheral surface (traction surface) 8.
At points A and B at two locations on the opposite side in the circumferential direction of a, the inner disk is strongly pressed against the inner peripheral surfaces of the input side disk and the output side disk, thereby not only deforming the inner ring into an elliptical shape but also backing up the trunnion. Due to the shortage, both the power roller 8 and the outer ring 33 warp so that the trunnion side becomes concave (see FIG. 7B).

In such a case, as shown in FIGS. 4 and 5, in the case of the displacement shaft 7 in which the outer ring 33 and the pivot shaft portion 29 are formed separately, as shown in FIG. Pivot shaft 2
No bending stress due to the deformation of the outer ring 33 acts on 9. However, as shown in FIG.
In the case of the displacement shaft 54 formed integrally with the outer ring 53, bending stress due to deformation of the outer ring 53 acts on the pivot shaft 51, as shown in FIG. Therefore, there is a problem that stress concentration occurs in the corner C formed by the large diameter portion 51A and the small diameter portion 51B of the pivot shaft portion 51.

Further, the trunnion is deformed,
The bearing for supporting the support shaft portion is similarly deformed. However, in the case of the displacement shaft 7 in which the outer race 33 and the support shaft portion 28 are formed separately as shown in FIGS. This deformation can be dealt with by tilting the pivot shaft 29 as shown in FIG. However, as shown in FIG.
In the case of the displacement shaft 54 in which the outer ring 53 and the outer ring 53 are integrally formed, as shown in FIG. 11, the deformation cannot be absorbed, and the corner formed by the support shaft 52 and the outer ring 53 cannot be absorbed. (Root corner of the support shaft 52) There is a problem that stress concentration occurs at E.

The present invention has been made in view of the above circumstances, and improves the durability of a displacement shaft in a toroidal type continuously variable transmission having a displacement shaft integrally formed with an outer ring of a thrust rolling bearing. It is an object of the present invention to provide a toroidal-type continuously variable transmission that can be driven.

[0020]

According to a first aspect of the present invention, there is provided a toroidal-type continuously variable transmission having an input shaft rotatably supported and an input side rotatable with the input shaft. A disc, an output disc arranged with the same central axis as the input disc, and supported rotatably with respect to the input disc;
It is arranged in the middle of the two discs in the axial direction of the two discs on the output side, in a direction perpendicular to the axial direction of the two discs, and at a twisted position with respect to the central axis of the two discs, and swings at this position. A plurality of trunnions, a plurality of power rollers rotatably supported on a displacement shaft supported by each of the trunnions, and sandwiched between the input side and the output side discs; A thrust rolling bearing provided between the inner surface of each trunnion and an inner surface of each of the input and output disks facing each other, the cross-section of which is a concave surface having an arc shape, and a peripheral surface of each of the power rollers. A toroidal-type continuously variable transmission in which the peripheral surface and the inner surface are in contact with each other as a spherical convex surface, wherein the displacement shaft is supported by the trunnion in a swingable manner. A shaft portion, a pivot shaft portion that is parallel to and eccentric to the support shaft portion and rotatably supports the power roller, and the pivot shaft portion that is disposed between the support shaft portion and the pivot shaft portion. A toroidal-type continuously variable transmission in which an outer ring of a thrust rolling bearing is integrally formed, wherein at least one of the following conditions (1) to (6) is satisfied.

(1) A hardened layer formed by heat treatment is formed on the surface of the displacement shaft, and the hardened layer is formed by machining a corner formed by the support shaft and the outer ring of the thrust rolling bearing. Later, the heat treatment abnormal layer of the hardened layer is removed by this processing. (2) A hardened layer formed by heat treatment is formed on the surface of the displacement shaft, and machining of a corner formed by the outer ring of the thrust rolling bearing and the pivot shaft portion is performed after the hardened layer is formed. The abnormal heat treatment layer of the hardened layer has been removed by this processing. (3) The pivot shaft portion of the displacement shaft includes a large-diameter portion on the outer ring side of the thrust rolling bearing and a small-diameter portion on which the bearing is mounted on an outer peripheral portion. A hardened layer formed by heat treatment is formed, and processing of a corner formed by the large-diameter portion and the small-diameter portion is performed after forming the hardened layer. It has been removed by processing. (4) Shot peening is applied to a corner formed by the support shaft and the outer ring of the thrust rolling bearing, and a compressive residual stress due to the shot peening exists in the corner. (5) Shot peening is applied to a corner formed by the outer race of the thrust rolling bearing and the pivot shaft, and a compressive residual stress due to the shot peening exists in the corner. (6) The pivot shaft portion of the displacement shaft has a large-diameter portion on the outer ring side of the thrust rolling bearing and a small-diameter portion on which the bearing is mounted on an outer peripheral portion, and the large-diameter portion and the small-diameter portion. Shot peening is applied to the corner formed by the part and
A compressive residual stress due to the shot peening exists in the corner.

According to the first aspect of the present invention, the corner formed by the support shaft and the outer ring where the stress is concentrated, the corner formed by the outer ring and the pivot shaft, and the size of the pivot shaft are large. The generation of cracks and the like at the corners formed by the diameter portion and the small diameter portion is suppressed, thereby improving the durability of the displacement shaft.

[0023]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a sectional view showing a portion of a displacement shaft of the toroidal type continuously variable transmission according to the present embodiment. In the present embodiment, the structure of the parts other than those shown in FIG. 1 is the same as the conventional structure shown in FIGS. The displacement shaft 81 according to the present embodiment has a columnar support shaft portion 83 that is swingably supported by the trunnion 6 via the radial needle bearing 30, and is parallel and eccentric to the support shaft portion 83. In addition, a columnar pivot shaft 82 that rotatably supports the power roller 8 via a radial needle bearing (bearing) 31, and a disk disposed between the support shaft 83 and the pivot shaft 82. The thrust rolling bearing (thrust ball bearing) 32 is formed integrally with an outer ring 84. The pivot shaft portion 82 has a cylindrical large-diameter portion 85 on the outer ring 84 side and a radial needle bearing (bearing) 31 on the outer peripheral portion.
And a columnar small-diameter portion 86 to which is attached. Outer ring 84
An outer raceway 87 is formed on the inner surface (lower surface in FIG. 1) of the power roller 8. The outer raceway 87 and the inner raceway 42 formed on the outer surface (upper surface in FIG. 1) of the power roller 8 are formed.
A plurality of balls 41 held by a ring-shaped retainer 44 are provided so as to roll freely.

On the surface of the displacement shaft 81, a hardened layer is formed by heat treatment. The support shaft 83 and the outer race 84
F, the corner G formed by the outer race 84 and the pivot shaft 82, and the large-diameter portion 8 of the pivot shaft 82.
Each of the corners formed by the small diameter portion 5 and the small diameter portion 86 is processed after forming the hardened layer, and the heat treatment abnormal layer in the hardened layer is removed by these processes.

By forming each of the corners F, G, and H after forming the hardened layer by the heat treatment in this manner, even when a large bending stress is applied to the displacement shaft 81 during operation of the toroidal type continuously variable transmission. In addition, it is possible to suppress the occurrence of damage such as cracks in the corners F, G, H.

That is, the outer ring 84 is deformed by applying a pressing force to two circumferentially opposite positions of the circumferential surface (traction surface) 8a of the power roller 8 or by deforming the trunnion 6, and the outer ring 84 is deformed. A bending stress due to the deformation of 84 acts, and stress (tensile stress) concentrates on each corner F, G, H. On the other hand, when heat treatment such as induction hardening or carburizing quenching is performed to harden the surface of the displacement shaft 81, the heat treatment abnormal layer with the internal strain remaining at each corner F, G, H remains. become. If such an abnormal heat treatment layer exists, cracks or the like may be generated in the corners F, G, and H due to stress concentration accompanying the bending stress, and the displacement shaft 81 may be damaged or broken. On the other hand, after the heat treatment is performed on the displacement shaft 81 as described above, each of the corners F, G, and H is processed to remove the hardened layer existing at each of the corners F, G, and H. If the heat treatment abnormal layer existing in the layer portion is removed, it is possible to prevent the displacement shaft 81 from being damaged such as breakage due to the above-described cause.

After forming the hardened layer by the heat treatment, shot peening is performed after forming the hardened layer instead of or in addition to processing the corners F, G, and H of the displacement shaft 81. Alternatively, a compressive residual stress based on the shot peening may be present at each corner F, G, H.

Thus, each corner F, G, H of the displacement shaft 81
The presence of the compressive residual stress prevents the corners F, G, and H from being damaged, such as cracks, even when bending stress is applied to the displacement shaft 81 during operation of the toroidal-type continuously variable transmission. be able to. That is, each corner F, G,
In the case of breakage from H, a large tensile stress is applied to these corners F, G, H. On the contrary,
When a compressive residual stress is present in each of the corners F, G, H as described above, the compressive residual stress cancels the tensile stress, thereby suppressing damage such as cracks.

Alternatively, shot peening may be applied to the corners F, G, H without forming a hardened layer on the displacement shaft 81 by heat treatment.

[0030]

As described above, according to the present invention,
In a toroidal type continuously variable transmission having a displacement shaft in which an outer ring of a thrust rolling bearing is integrally formed, a corner formed by a support shaft portion where the stress is concentrated and an outer ring, an outer ring and a pivot shaft portion. Since it is possible to suppress the occurrence of cracks and the like at the corners formed and the corners formed by the large-diameter portion and the small-diameter portion of the pivot shaft portion, it is possible to improve the durability of the displacement shaft. it can.

[Brief description of the drawings]

FIG. 1 is a sectional view showing a portion of a displacement shaft of a toroidal type continuously variable transmission according to an embodiment of the present invention.

FIG. 2 is a side view showing a basic configuration of the toroidal-type continuously variable transmission in a state of maximum deceleration.

FIG. 3 is a side view showing a state at the time of maximum deceleration.

FIG. 4 is a cross-sectional view of a main part showing an example of a specific structure of a conventionally known toroidal type continuously variable transmission.

FIG. 5 is a sectional view taken along line XX of FIG. 4;

FIG. 6 is a view showing a conventional example, and is a cross-sectional view showing a portion of a displacement shaft integrally formed with an outer ring of a thrust rolling bearing.

FIGS. 7A and 7B are diagrams illustrating a deformed state of the inner and outer races of the thrust rolling bearing when the power roller is pressed, wherein FIG. 7A illustrates a state before deformation and FIG. is there.

FIG. 8 is a diagram illustrating a deformed state when the power roller is pressed when the pivot shaft portion and the outer ring are separate displacement shafts.

FIG. 9 is a diagram illustrating a deformed state when the power roller is pressed when the pivot shaft and the outer ring are integral displacement shafts.

FIG. 10 shows a case where the support shaft and the outer ring are separate displacement shafts.
It is a figure which shows the deformation state when a trunnion is deformed.

FIG. 11 shows a case where the support shaft and the outer ring are integral displacement shafts.
It is sectional drawing which shows the deformation | transformation state when a trunnion is deformed.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 input side disk 2a inner surface 3 output shaft 4 output disk 4a inner surface 5 pivot 6 trunnion 8 power roller 8a peripheral surface 9 pressing device 15 input shaft 30 radial needle bearing 31 radial needle bearing 32 thrust rolling bearing 34 thrust bearing 81 Displacement shaft 82 Pivot shaft part 83 Support shaft part 84 Outer ring 85 Large diameter part 86 Small diameter part E, F, G Corner

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J051 BB02 BE09 EC00 FA02 3J101 AA02 AA32 AA42 AA53 AA62 BA54 BA56 DA11 DA20 FA31 GA11

Claims (1)

[Claims] An input shaft rotatably supported, an input disk rotatable with the input shaft, a central axis arranged with the input disk and rotating with respect to the input disk. A freely supported output side disk and an intermediate portion between the input side and the output side disks with respect to the axial direction of the input side and the output side disks, in a direction perpendicular to the axial direction of the both disks and at the center axis of the both disks. A plurality of trunnions arranged at a twisting position and swinging at the position, and a plurality of trunnions rotatably supported by a displacement shaft supported by each of the trunnions and sandwiched between both input side and output side disks Power rollers, and a thrust rolling bearing provided between an outer surface of each of the power rollers and an inner surface of each of the trunnions. A toroidal-type continuously variable transmission in which the facing inner surfaces are concave surfaces having a circular cross section, and the peripheral surfaces of the power rollers are spherical convex surfaces, and the peripheral surfaces are brought into contact with the inner surfaces. The displacement shaft is a support shaft portion swingably supported by the trunnion, and a pivot shaft that is parallel and eccentric to the support shaft portion and rotatably supports the power roller. And a toroidal-type continuously variable transmission in which the outer ring of the thrust rolling bearing disposed between the support shaft and the pivot shaft is integrally formed. The following (1) to (6) A toroidal-type continuously variable transmission, wherein at least one of the conditions is satisfied. (1) A hardened layer formed by heat treatment is formed on the surface of the displacement shaft, and a corner formed by the support shaft and the outer ring of the thrust rolling bearing is processed after the hardened layer is formed. The heat treatment abnormal layer of the hardened layer has been removed by this processing. (2) A hardened layer formed by heat treatment is formed on the surface of the displacement shaft, and machining of a corner formed by the outer ring of the thrust rolling bearing and the pivot shaft portion is performed after the hardened layer is formed. The abnormal heat treatment layer of the hardened layer has been removed by this processing. (3) The pivot shaft portion of the displacement shaft includes a large-diameter portion on the outer ring side of the thrust rolling bearing and a small-diameter portion on which the bearing is mounted on an outer peripheral portion. A hardened layer formed by heat treatment is formed, and processing of a corner formed by the large-diameter portion and the small-diameter portion is performed after forming the hardened layer. It has been removed by processing. (4) Shot peening is applied to a corner formed by the support shaft and the outer ring of the thrust rolling bearing, and a compressive residual stress due to the shot peening exists in the corner. (5) Shot peening is applied to a corner formed by the outer race of the thrust rolling bearing and the pivot shaft, and a compressive residual stress due to the shot peening exists in the corner. (6) The pivot shaft portion of the displacement shaft includes a large-diameter portion on the outer ring side of the thrust rolling bearing and a small-diameter portion on which the bearing is mounted on an outer peripheral portion, and the large-diameter portion and the small-diameter. Shot peening is applied to the corner formed by the part and
A compressive residual stress due to the shot peening exists in the corner.