JPH11210852A - Toroidal type continuously variable transmission - Google Patents

Abstract

(57) [Summary] [Problem] A stopper 33a for regulating the swing displacement angle of a pair of trunnions 6, 6, and each of these trunnions 6,
6 is prevented. A support post fixed to a housing is provided.
In addition, the stopper 33a is slightly displaceably supported with respect to the holding member 36. With this configuration, the above-described one-side contact can be prevented irrespective of some dimensional errors and assembly errors. or,
The disc spring 46 prevents the stopper 33a from rattling due to vibration during traveling.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a toroidal type continuously variable transmission used as a transmission for an automobile, for example, and realizes a structure having sufficient durability without performing high-precision machining. Things.

[0002]

2. Description of the Related Art The use of a toroidal-type continuously variable transmission as schematically shown in FIGS. This toroidal type continuously variable transmission supports an input disk 2 concentrically with an input shaft 1 as disclosed in, for example, Japanese Utility Model Laid-Open Publication No. 62-71465.
The output side disk 4 is fixed to the end of the output shaft 3 which is arranged concentrically. At the axially intermediate position between the input side and output side disks 2 and 4 inside the casing containing the toroidal type continuously variable transmission, there is provided a pivot 5 which is twisted with respect to the input shaft 1 and the output shaft 3. , 5 are provided.

That is, each of the trunnions 6, 6 has the pivots 5, 5 concentrically provided on the outer surfaces of both ends. In addition, a base end of the displacement shafts 7, 7 is supported at an intermediate portion between the trunnions 6, 6, and the trunnions 6, 6 are pivoted about the pivots 5, 5, whereby
The tilt angles of the displacement shafts 7, 7 can be adjusted freely. Power rollers 8 are rotatably supported around the displacement shafts 7 supported by the trunnions 6 respectively. And each of these power rollers 8, 8 is
The input side and output side disks 2 and 4 are sandwiched between inner surfaces 2a and 4a facing each other. Each of the inner side surfaces 2a, 4a has a concave section obtained by rotating an arc around the pivot 5 as described above.
Each of the power rollers 8, 8 formed on a spherical convex surface
Are brought into contact with the inner side surfaces 2a, 4a.

A loading device 9 of a loading cam type is provided between the input shaft 1 and the input disk 2, and the input device 2 is elastically pressed toward the output disk 4 by the pressing device 9. It is free. The pressing device 9 includes a cam plate 10 that rotates together with the input shaft 1 and a retainer 1.
1 and a plurality (for example, four) of rollers 12 and 12 held rotatably. On one side surface (the right side surface in FIGS. 3 and 4) of the cam plate 10, a cam surface 13 which is uneven in the circumferential direction is formed, and the outer side surface of the input side disk 2 (the left side surface in FIGS. 3 and 4). 3), a cam surface 14 having a similar shape is formed. The plurality of rollers 12 are rotatably supported about a radial axis with respect to the center of the input shaft 1.

When the cam plate 10 rotates with the rotation of the input shaft 1 when the toroidal type continuously variable transmission having the above-described configuration is used, the cam surface 13 causes the plurality of rollers 12, 12 to move to the input side disk. 2 against the cam surface 14 formed on the outer surface. As a result, the input side disk 2 is pressed by the plurality of power rollers 8, and at the same time, the input disk 2 is pressed based on the pressing of the cam surfaces 13, 14 and the plurality of rollers 12, 12. The side disk 2 rotates. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 8, and the output shaft 3 fixed to the output side 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 deceleration is first performed between the input shaft 1 and the output shaft 3, each of the pivots 5 The trunnions 6, 6 are swung in a predetermined direction as a center. The peripheral surfaces 8a, 8a of the power rollers 8, 8 are shown in FIG.
As shown in FIG. 5, the displacement shafts 7, 7 are inclined so as to abut against the central portion of the inner surface 2a of the input disk 2 and the outer peripheral portion of the inner surface 4a of the output disk 4, respectively. Conversely, when increasing the speed,
, Each of the trunnions 6 is swung in the opposite direction. The peripheral surface 8 of each of the power rollers 8
As shown in FIG. 4, each of the displacement shafts 7a and 8a comes into contact with a portion of the inner surface 2a of the input disk 2 near the outer periphery and a portion of the inner surface 4a of the output disk 4 near the center. , 7 are tilted. If the inclination angle of each of the displacement shafts 7, 7 is set between those in FIGS. 3 and 4, an intermediate speed ratio can be obtained between the input shaft 1 and the output shaft 3.

FIGS. 5 and 6 show Japanese Utility Model Application No. 63-69293.
FIG. 1 shows an example of a more specific toroidal type continuously variable transmission described in the microfilm of Japanese Utility Model Application Publication No. Hei 1-173552. The input-side disk 2 and the output-side disk 4 are rotatably supported around a cylindrical input shaft 15 via needle bearings 16 and 16, respectively.
The cam plate 10 is spline-engaged with the outer peripheral surface of the input shaft 15 at the end (the left end in FIG. 5), and is prevented from moving away from the input disk 2 by the flange 17. The cam plate 10 and the rollers 12, 12 constitute a 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. . The output side disk 4
The output gear 18 is connected by keys 19, 19 so that the output disk 4 and the output gear 18 rotate synchronously.

The pivots 5, 5 provided at both ends of the pair of trunnions 6, 6 respectively swing on the pair of support plates 20, 20 in the axial direction (the front-back direction in FIG. 5, the left-right direction in FIG. 6). It is supported so as to be freely displaceable. The displacement shafts 7, 7 are supported in circular holes 21, 21 formed in the middle portions of the trunnions 6, 6, respectively. Each of the displacement shafts 7 has a support shaft 22, 22 and a pivot shaft 23, 23 which are parallel and eccentric to each other. Among these, the respective support shaft portions 22 are rotatably supported inside the respective circular holes 21 via radial needle bearings 24. Further, the power rollers 8, 8 are provided around the pivot shafts 23, 23, respectively, with the other radial needle bearings 25, 25.
, It is rotatably supported.

The pair of displacement shafts 7, 7 are provided at positions opposite to the input shaft 15 by 180 degrees. or,
The direction in which the respective pivot shaft portions 23, 23 of the respective displacement shafts 7, 7 are eccentric with respect to the respective support shaft portions 22, 22 is the same as the rotation direction of the input side and output side disks 2, 4. In FIG. 6, the left and right directions are opposite. The eccentric direction is a direction substantially orthogonal to the direction in which the input shaft 15 is provided. Accordingly, the power rollers 8 are supported so as to be slightly displaceable in the axial direction of the input shaft 15 (the left-right direction in FIG. 5 and the front-back direction in FIG. 6). As a result, the power rollers 8, 8 tend to be displaced in the axial direction of the input shaft 15 due to elastic deformation of the constituent members based on a large load applied to the constituent members in the state of transmission of the rotational force. In this case, the displacement can be absorbed without applying excessive force to the components.

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, a thrust ball bearing 26, 26 and thrust needle bearings 27, 27 are provided. The thrust ball bearings 26 support rotation of the power rollers 8 while supporting the load applied to the power rollers 8 in the thrust direction. Also, the thrust needle bearings 27, 27
From each of the power rollers 8 and 8 to each of the thrust ball bearings 2
Each of the pivot shafts 23 and 23 and the outer rings 28 and 28 swing about the support shafts 22 and 22 while supporting the thrust load applied to the outer rings 28 and 28 constituting the shafts 6 and 26. Tolerate.

Further, drive rods 29, 29 are connected to one end (left end in FIG. 6) of each of the trunnions 6, 6, and a drive piston 30, 30 are fixed. The drive pistons 30 are oil-tightly fitted in the drive cylinders 31, 31, respectively.

In the case of 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. The rotation of the input disk 2 is transmitted to the output disk 4 via the pair of power rollers 8, 8, and the rotation of the output disk 4 is extracted from the output gear 18. When changing the rotational speed ratio between the input shaft 15 and the output gear 18, the pair of drive pistons 30, 30 are displaced in opposite directions. The pair of trunnions 6, 6 are displaced in opposite directions with the displacement of the drive pistons 30, 30, respectively. For example, the lower power roller 8 in FIG. Are displaced to the left in FIG. As a result, these power rollers 8, 8
The direction of the tangential force acting on the abutting portion between the peripheral surfaces 8a, 8a 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 of the trunnions 6, 6
Swing in opposite directions about pivots 5, 5 pivotally supported by 20. As a result, as shown in FIGS. 3 and 4 described above, the contact positions between the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner surfaces 2a, 4a change, and the input shaft 15 The rotation speed ratio with the output gear 18 changes.

The input shaft 15 and the output gear 1 are
When transmitting the rotational force to the power rollers 8, the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 based on the elastic deformation of the constituent members. Each of the displacement shafts 7 that pivotally support 8 rotates slightly about each of the support shaft portions 22. As a result of this rotation, the outer ring 2 of each of the thrust ball bearings 26, 26
The outer surfaces of the trunnions 6, 6 and the inner surfaces of the trunnions 6, 6 are relatively displaced. Since the thrust needle bearings 27 exist between the outer surface and the inner surface, the force required for the relative displacement is small. Therefore, the force for changing the inclination angle of each of the displacement shafts 7 can be small as described above.

The space between each of the trunnions 6 and the housing 32 accommodating the toroidal-type continuously variable transmission is described in JP-A-57-47060 and JP-A-6-43404. In this manner, a mechanism for preventing the inclination angle of the trunnion 6 from becoming excessive is provided. As shown in FIG. 7, for example, this inclination angle limiting mechanism is a plate-like stopper 3 having a tip edge formed in a part of the housing 32 and facing one end surface of the trunnion 6.
3 is fixed, and the front edge of the stopper 33 and one end of the trunnion 6 are opposed to each other. By providing such an inclination angle limiting mechanism, the trunnion 6 can swing freely within a range where one end surface of the trunnion does not collide with the tip edge of the stopper 33. Accordingly, if the inclination angle of the leading edge is appropriately determined, the displacement shaft 7 (FIGS. 3 to 6) is excessively displaced, and the peripheral surface 8a of each power roller 8 is moved to both the input side and the output side disks 2, 4. Can be prevented from coming off from the inner side surfaces 2a, 4a.

The stopper 33 controls the angle of inclination of the two trunnions 6 with one sheet. Also, at the time of a general shift operation, the stopper 33
And the trunnions 6 and 6 do not conflict with each other. The stopper 33 and the trunnions 6, 6 may collide with each other for some reason when the inclination angles of the trunnions 6, 6 exceed the maximum shift state (maximum deceleration state and maximum acceleration state). This is the case where swing displacement occurs. The swing angle of each of the trunnions 6, 6 from the maximum shift state until the stopper 33 and the trunnions 6, 6 abut is set to, for example, about 1 to 2 degrees.

[0016]

In the case of the inclination angle limiting mechanism of the trunnions 6, 6 incorporated in the conventional toroidal type continuously variable transmission, in order to prevent an excessive force from being applied to each part, each of the constituent elements is required. It was necessary to increase the dimensional accuracy and assembly accuracy of the members. That is, since the stoppers 33 are used to restrict the inclination angles of the two trunnions 6, 6 inclined in synchronization with each other, one end surface of the two trunnions 6, 6 and the stopper 33 In order to simultaneously contact the leading edge, the dimensional accuracy and assembling accuracy of the trunnion 6 and the stopper 33 must be increased.

If the accuracy is not sufficiently ensured,
As shown in FIG. 8, only one end of one end (right side in FIG. 8) of the trunnion 6 abuts on the leading edge of the stopper 33, and the other end (left side in FIG. 8) of the trunnion 6. One surface and the leading edge of the stopper 33 remain separated. In such a state, based on the load applied to the stopper 33 from the one trunnion 6, the stopper 33
A force in the direction of twisting around the support post 34 is applied. The engaging portion between the stopper 33 and the support post 34 may be worn out by such a force, or may be damaged if the engaging portion is extremely severe. If the above dimensional accuracy and assembling accuracy are increased to eliminate such inconvenience, the cost of the toroidal type continuously variable transmission increases. In view of such circumstances, the toroidal type continuously variable transmission of the present invention does not increase the dimensional accuracy and assembling accuracy of the constituent members, and the components that constitute the tilt angle limiting mechanism have a force that leads to wear and breakage. It was invented to realize a structure that does not add.

[0018]

The toroidal type continuously variable transmission according to the present invention, like the above-described conventional toroidal type continuously variable transmission, has a housing and a concentric and independent inside of the housing inside the housing. The input side and output side disks rotatably supported, and one of the concentric ones located in a twisted position with respect to the center axis of the input side and output side disks
A plurality of trunnions swinging about a pair of pivots,
A displacement shaft supported for each of these trunnions, a power roller rotatably supported on each of these displacement shafts, and sandwiched between inner surfaces of the input-side and output-side disks,
A stopper is supported inside the housing at a portion near each of the trunnions, and prevents each of the trunnions from swinging around the pivot beyond an allowable limit. Then, the inner surfaces of the input side and the output side disks facing each other are concave surfaces having an arc-shaped cross section,
The peripheral surface of each power roller is a spherical convex surface, and each peripheral surface is brought into contact with each inner surface. In particular, in the toroidal type continuously variable transmission of the present invention, the stopper is supported by the support member fixed to the housing so as to be slightly displaceable, and an elastic member for pressing the stopper toward the support member is provided. Provided.

[0019]

With the toroidal-type continuously variable transmission of the present invention constructed as described above, the function of transmitting the torque between the input side disk and the output side disk, and the speed ratio between these two disks. Is the same as that of the conventionally known toroidal-type continuously variable transmission as described above. In order to change the gear ratio, each trunnion is swung about a pivot axis. And prevent based on conflict. In particular, in the case of the toroidal-type continuously variable transmission of the present invention, the stopper is supported so as to be slightly displaceable with respect to the support member fixed to the housing. Even if the assembling precision is not particularly strictly regulated, each of the trunnions and the stopper can be uniformly abutted. Therefore, it is possible to prevent a large force from being applied to a part of the mechanism for restricting the swing angle of the trunnion, thereby preventing each part of the mechanism from being significantly worn. In addition, since the stopper is pressed toward the support member by the elastic member, the stopper and the support member are slightly displaceably engaged with each other. Stopper does not rattle.

[0020]

1 and 2 show an embodiment of the present invention. A feature of the present invention is that a pair of trunnions 6, 6 are provided between the input-side disk 2 and the output-side disk 4 (see FIGS. 3 to 5) so as to be freely displaceable about pivots 5, 5. In the mechanism for limiting the swing angle of the motor. The structure and operation of the other parts, including the conventional structure described above, are the same as those of various conventionally known or considered toroidal-type continuously variable transmissions. Therefore, the description of the equivalent parts will be omitted or simplified. Hereinafter, the description will focus on the characteristic portions of the present invention and the portions not described in the description of the prior art.

On the inner surface of the housing 32, an intermediate portion of a support plate 20 for supporting the trunnions 6, 6 is supported for swinging and displaceable in the axial direction of the pivots 5, 5 (vertical direction in FIG. 1). The support post 34 is fixed. And
A holding member 36 is fixedly connected to a center portion of the inner surface of the support plate 20 (a surface facing the center side of the housing 32 and a lower surface in FIG. 1) at a tip end portion of the support post 34 by a connecting screw 37. The holding member 36 together with the support post 34 constitutes a support member described in the claims. The outer peripheral surface of the holding member 36 has a substantially oval cross section.
A pair of flat surfaces 38, 38 (FIG. 2) parallel to each other are formed at two positions on the outer peripheral surface opposite to each other in the diameter direction.
Also, at the tip (the lower end in FIG. 1) of the holding member 36,
An outward flange-shaped restraining flange portion 39 having an outer diameter larger than that of a portion near the base end (upward in FIG. 1) is formed.
The coupling screw 37 is screwed and fastened to a support plate 40 having a distal end fixed to the inner surface of the housing 32 in a state where the coupling screw 37 penetrates the support post 34 and the holding member 36.
1 is in contact with the retaining flange 39. In this state, the support post 34 and the holding member 36 are sandwiched between the support plate 40 and the head 41 and fixed to the inner surface of the housing 32 via the support plate 40.

A stopper 33a is provided between the front end face (lower end face in FIG. 1) of the support post 34 and the holding flange 39.
The middle part of is loosely clamped. As shown in FIG. 2, the outer peripheral edge of the stopper 33a is a hexagon whose two parallel sides are long. In the center of the stopper 33a, there is a pair of straight edges 42, 42 parallel to each other.
A substantially oval through hole 43 is formed. Then, the portion near the base end of the holding member 36 is loosely inserted into the through hole 43. The inner diameter R _{43 of the} through hole 43 is slightly larger (R ₄₃ > D ₃₆ ) than the outer diameter D _{36 of the} portion near the base end of the holding member 36. Further, the distance D between the pair of straight edges 42, 42 forming the inner peripheral edge of the through hole 43,
_42, the restraining slightly greater than the distance D ₃₈ of the flat surfaces 38, 38 between the pair constituting the outer peripheral surface of the proximal end portion near the brackets 36, the outer diameter D ₃₆ of the proximal end portion near the restraining bracket 36 (D ₃₈ <D ₄₂ <D ₃₆ ). Accordingly, the stopper 33a extends around the holding member 36 in a slight swinging displacement around the holding member 36 and in the arrangement direction of the pair of trunnions 6, 6 (the left-right direction in FIGS. 1 and 2). It is slightly displaceable. The fitting hole 35 formed in the support plate 40 and the base end of the support post 34 are non-circularly fitted to prevent the support post 34 from rotating around the coupling screw 37. hand,
The positioning of the support post 34 in the circumferential direction is achieved. Also, the joint between the support post 34 and the holding member 36 is formed in a similar non-circular shape.

A recess 44 is provided at the center of the stopper 33a at a position facing the holding flange 39. The diameter D _{44 of the} concave portion 44 is the same as the diameter of the plate spring 46 described below.
It is slightly larger (D _44> D ₄₆₎ than the diameter D _46. Further, the stopper 3 having such a concave portion 44 formed thereon is used.
The thickness T ₃₃ of the central portion of the 3a is reduced (T ₃₃ <T ₄₅₎ than the thickness T ₄₅ of the gap 45 existing between the tip end surface and the restraining flange portion 39 of the support posts 34 . A plate spring 46, which is an elastic member, is provided between the bottom surface of the concave portion 44 and the holding flange 39, and the central portion of the stopper 33a is moved by the plate spring 46 to the front end surface of the support post 34. , And is elastically pressed.

Further, in the illustrated example, the nozzle holes 4 for ejecting traction oil toward the peripheral surfaces 8a, 8a of the power rollers 8, 8 are formed on the outer peripheral surface of the retaining flange 39.
7, 47 are provided. During operation of the toroidal type continuously variable transmission, these nozzle holes 47, 47 are provided in the lubricating oil supply groove 48 formed in the inner surface of the housing 32 and the coupling screw 37 by the action of an oil feed pump (not shown). ,
The distal end surface (upper end surface in FIG. 1) of the coupling screw 37 and the head 41
Refueling passage 49 opened to the outer peripheral surface closer to this head 41
The traction oil is fed through a cylindrical gap between the closer outer peripheral surface and the inner peripheral surface of the holding member 36.

In the case of the toroidal-type continuously variable transmission of the present invention constructed as described above, the stopper 33a is slightly displaceably supported on a support post 34 which is a support member fixed to the housing 32. ing. For this reason, each of the trunnions 6, 6 and the stopper 33a can be uniformly abutted with each other without strictly regulating the dimensional accuracy and the assembling accuracy of the stopper 33a and the respective trunnions 6, 6. . That is, when each of the trunnions 6 is largely rocked and displaced, a part of one of the trunnions 6 is temporarily moved ahead of a part of the other trunnion 6.
This stopper 33a is displaced even if it abuts a part of the outer periphery of 3a.

That is, when a biasing force is applied only from the one trunnion 6 to the stopper 33a, the stopper 33a is moved within a range in which a portion near the base end of the holding member 36 can be displaced inside the through hole 43. , Against the elastic force of the plate spring 46. With this displacement, not only a part of the one trunnion 6 but also a part of the other trunnion 6 abuts on the outer peripheral edge of the other part of the stopper 33a. In this state, the pair of flat surfaces 38, 38 and the straight edge 4
Either one of the flat surfaces 38 and the straight edge 4
2 uniformly abut over substantially the entire length. For this reason, a large force is prevented from being applied to a part of the stopper 33a and the holding member 36 constituting the mechanism for limiting the swing angle of the trunnions 6, 6, and the stopper 33a and the holding member 36 are significantly worn. Can be prevented.

Further, even when vibration is applied to the toroidal type continuously variable transmission based on the running of the automobile, the stopper 33a does not rattle. That is, this stopper 33
“a” is elastically sandwiched between the support post 34 and the holding member 36 that constitute the support member by a plate spring 46 that is an elastic member. For this reason, the stopper 33a does not rattle due to the vibration even though the stopper 33a and the retainer 36 are slightly displaceably engaged. Therefore, there is no occurrence of abnormal noise due to rattling at the mounting portion of the stopper 33a during traveling.

The size of the gap provided between the outer peripheral surface of the portion near the base end of the holding member 36 and the inner peripheral surface of the through hole 43 is designed in consideration of the dimensional accuracy and the assembly accuracy. Although it is regulated, in the case of a toroidal-type continuously variable transmission generally used as an automobile transmission, about 0.2 to 1.0 mm is appropriate. When the swing angle of each of the trunnions 6, 6 is increased, a portion that abuts each other, that is, a part of each of the trunnions 6, 6 and a part of the outer peripheral edge of the stopper 33a are soaked. , Induction hardening, carburizing and other quenching treatments to harden the surface hardness to H
Rc of 40 or more prevents wear of these parts.
Further, the stopper 3 is provided at a portion near the base end of the holding member 36.
The structure for slightly displacing the support 3a is not limited to the oval cross section as shown in the figure, but the stopper 33a is provided around the holding member 36, such as a spline engagement with rattling. Any structure may be used as long as it can support the stopper 33a so that it can be slightly displaced and displaced in the plane direction of the stopper 33a itself. Further, the elastic member for preventing the rattling based on the vibration is not limited to the plate spring 46 as shown in the figure, but may be another spring such as a coil spring or another elastic material such as oil-resistant rubber. Can also be used. Further, the support post 34 and the holding member 36 may be integrated without necessarily being separate bodies. When integrated, the inner peripheral edge of the plate spring 46 is held down on the outer peripheral surface of the distal end of the support post by a retaining ring (not shown) which is locked to the outer peripheral surface of the distal end of the support post.

[0029]

The toroidal-type continuously variable transmission according to the present invention is constructed and operated as described above. Therefore, the dimensional accuracy, the shape accuracy and the assembling accuracy of each component constituting the portion for limiting the swing angle of the trunnion. Can be limited without applying a large force to each part without specifically restricting the trunnion. Therefore, an inexpensive toroidal type continuously variable transmission having excellent durability can be realized.

[Brief description of the drawings]

FIG. 1 is a partial cross-sectional view showing an example of an embodiment of the present invention.

FIG. 2 is a cross-sectional view taken along line AA of FIG. 1, showing only main parts.

FIG. 3 is a side view showing a basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 4 is a side view showing a state at the time of maximum speed increase.

FIG. 5 is a sectional view showing a first example of a specific structure of the toroidal type continuously variable transmission.

FIG. 6 is a sectional view taken along line BB of FIG. 5;

FIG. 7 is a partial side view showing an example of a conventionally known trunnion swing angle limiting mechanism.

FIG. 8 is a partial schematic side view for explaining a problem of the conventional structure.

[Explanation of symbols]

 Reference Signs List 1 input shaft 2 input side disk 2a inner surface 3 output shaft 4 output side disk 4a inner surface 5 pivot 6 trunnion 7 displacement shaft 8 power roller 8a peripheral surface 9 pressing device 10 cam plate 11 retainer 12 roller 13, 14 cam surface 15 Input shaft 16 Needle bearing 17 Flange 18 Output gear 19 Key 20 Support plate 21 Circular hole 22 Support shaft 23 Pivot shaft 24 Radial needle bearing 25 Radial needle bearing 26 Thrust ball bearing 27 Thrust needle bearing 28 Outer ring 29 Drive rod 30 Driving piston 31 Driving cylinder 32 Housing 33, 33a Stopper 34 Support post 35 Fitting hole 36 Holder 37 Coupling screw 38 Flat surface 39 Suppressing flange 40 Support plate 41 Head 42 Linear edge 43 Through hole 44 Depression 45 Gap 46 Plate Spring 47 Nozzle hole 4 Lubricating oil supply groove 49 oil passage

Claims (1)

[Claims] 1. A housing, an input side disk, an output side disk supported concentrically and independently rotatably inside the housing, and a torsion with respect to a center axis of the input side disk and the output side disk. , A plurality of trunnions swinging about a pair of concentric pivots, a displacement shaft supported for each of the trunnions, and a rotatably supported by each of the displacement shafts. A power roller sandwiched between the inner surfaces of the two output-side disks, and a power roller supported by a portion near each of the trunnions inside the housing, and each of the trunnions swings about an allowable limit around the pivot. A stopper is provided to prevent the input and output disks from facing each other. In a toroidal-type continuously variable transmission in which each of the peripheral surfaces is in contact with each of the inner surfaces by using a spherical convex surface as a surface, the stopper is slightly displaced with respect to a support member fixed to the housing. A toroidal-type continuously variable transmission, wherein an elastic member that freely supports and presses the stopper toward the support member is provided.