JP3503393B2 - Toroidal type continuously variable transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The toroidal type continuously variable transmission according to the present invention is used, for example, as a transmission for automobiles or as a transmission for various industrial machines.

[0002]

2. Description of the Related Art The use of a toroidal type continuously variable transmission as schematically shown in FIGS. 6 to 7 has been studied as a transmission for an automobile. This toroidal type continuously variable transmission supports an input side disk (first disk) 2 concentrically with the input shaft 1 as disclosed, for example, in Japanese Utility Model Laid-Open No. 62-71465. An output side disk (second disk) 4 is fixed to the end portion of the output shaft 3 arranged concentrically with. Inside the casing containing the toroidal type continuously variable transmission, there is a trunnion 6 which swings around a pivot shaft 5, 5 in a twisted position with respect to the input shaft 1 and the output shaft 3.
6 is provided.

The trunnions 6, 6 are provided with the pivots 5, 5 on the outer surfaces of both ends. Further, the base end portions of the displacement shafts 7, 7 are supported on the central portions of the trunnions 6, 6 and the trunnions 6, 6 are swung about the pivot shafts 5, 5 so that the trunnions 6, 6 are rotated. The inclination angles of the displacement shafts 7, 7 can be freely adjusted. Each trunnion 6,
Power rollers 8, 8 are rotatably supported around displacement shafts 7, 7 supported by 6, respectively. The power rollers 8 and 8 are sandwiched between the input side and output side disks 2 and 4.

The inner side surfaces 2a, 4a of the input side and output side disks 2, 4 facing each other have cross sections, respectively.
A concave surface obtained by rotating an arc centered on the pivot 5 about the input shaft 1 and the output shaft 3 is formed. The peripheral surfaces 8a, 8a of the power rollers 8, 8 formed in the spherical convex surface are in contact with the inner side surfaces 2a, 4a.

A loading cam type pressing device 9 is provided between the input shaft 1 and the input side disk 2, and the input side disk 2 is directed toward the output side disk 4 by the pressing device 9 and elastically. Pressing. This pressing device 9
Is a cam plate 10 that rotates together with the input shaft 1, and a retainer 11.
A plurality of (for example, four) rollers 12 held by
It is composed of 12 and. On one side surface (left side surface of FIGS. 6 to 7) of the cam plate 10, a cam surface 13 which is an uneven surface extending in the circumferential direction is formed, and the outer side surface of the input side disk 2 (right side of FIGS. 6 to 7). The same cam surface 14 is also formed on the surface). Then, the plurality of rollers 12, 12 are rotatably supported around a shaft in the radial direction with respect to the center of the input shaft 1.

When the toroidal type continuously variable transmission configured as described above is used, when the cam plate 10 rotates with the rotation of the input shaft 1, the cam surface 13 causes the plurality of rollers 12, 12 to rotate.
The cam surface 14 on the outer surface of the input side disk 2 is pressed. As a result, the input side disk 2 is pressed by the power rollers 8, 8 and at the same time, the pair of cam surfaces 13,
The input side disk 2 rotates based on the pressing force of 14 and the plurality of rollers 12, 12. The rotation of the input side disk 2 causes the power rollers 8,
It is transmitted to the output side disk 4 via 8, and the output shaft 3 fixed to the output side disk 4 is rotated.

When the rotational speed ratio (gear 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, the respective pivot shafts 5 and 5 are The trunnions 6, 6 are swung about the center, and the power rollers 8, 8
As shown in FIG. 6, the peripheral surfaces 8a, 8a of the input side disk 2
The displacement shafts 7, 7 are tilted so as to come into contact with the central portion of the inner side surface 2a and the outer peripheral portion of the inner side surface 4a of the output side disk 4, respectively.

On the contrary, 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 are shown in FIG. As shown, in the inner peripheral surface 2a of the input side disk 2 and the outer peripheral part of the output side disk 4, the inner surface 4a of the output side disk 4 near the center,
The displacement shafts 7, 7 are tilted so that they come into contact with each other.
By setting the inclination angles of the displacement shafts 7, 7 in the middle between FIG. 6 and FIG. 7, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIGS. 8 to 9 show Japanese Patent Application No. 63-6929.
3 shows a more specific toroidal-type continuously variable transmission described in the microfilm of No. 3 (Actual Kaihei No. 1-173552). Input side disk 2 and output side disk 4
Is rotatably supported around a circular tubular input shaft 15 which is a rotary shaft via needle bearings 16 and 16, respectively. Further, the cam plate 10 has an end portion of the input shaft 15 (see FIG. 8).
The left end portion of the above) is spline-engaged with the outer peripheral surface, and the collar portion 17 prevents movement in the direction away from the input side disk 2. Then, the cam plate 10 and the rollers 12 and 1
2 constitutes a loading cam type pressing device 9 for rotating the input side disk 2 while pressing the input side disk 2 toward the output side disk 4 based on the rotation of the input shaft 15. An output gear 18 is connected to the output side disk 4 by keys 19 and 19 so that the output side disk 4 and the output gear 18 rotate in synchronization with each other.

Pivots 5 and 5 provided at both ends of the pair of trunnions 6 and 6 are supported on the pair of support plates 20 and 20 in the swinging and axial directions (front and back directions in FIG. 8, left and right directions in FIG. 9). It is supported so that it can move freely. Then, the displacement shafts 7, 7 are formed in the circular holes 23, 23 formed in the intermediate portions of the trunnions 6, 6 respectively.
I support you. The displacement shafts 7, 7 are parallel to each other and eccentric to the support shaft portions 21, 21 and the pivot shaft portions 22, 2, respectively.
2 and 2, respectively. Of these, each support shaft portion 21,
21 is rotatably supported inside the circular holes 23, 23 via radial needle bearings 24, 24.
The power rollers 8, 8 are rotatably supported around the pivot shafts 22, 22 via radial rolling bearings such as radial needle bearings 25, 25.

The pair of displacement shafts 7, 7 are provided 180 degrees opposite to each other with the input shaft 15 as the center. Also, the pivot shafts 22, 22 of the displacement shafts 7, 7 are
The direction of eccentricity with respect to each of the support shaft portions 21, 21 is the same direction (left and right opposite directions in FIG. 9) with respect to the rotation direction of the input side and output side disks 2, 4. The eccentric direction is the direction in which the input shaft 15 is arranged (the left-right direction in FIG.
(The front and back directions of) are set to be substantially orthogonal to the direction. Therefore, the power rollers 8, 8 are supported so as to be slightly displaceable in the arrangement direction of the input shaft 15. As a result, due to dimensional accuracy of each component, elastic deformation during power transmission, etc., the power rollers 8, 8 are moved in the axial direction of the input shaft 15 (left and right direction in FIG. 8, front and back sides in FIG. 9). Direction), this displacement can be absorbed without applying excessive force to each component.

Between the outer surface of each of the power rollers 8 and 8 and the inner surface of the intermediate portion of each of the trunnions 6, 6, there are thrust ball bearings 26, in order from the outer surface of the power rollers 8, 8. There are provided thrust rolling bearings such as 26 and thrust bearings such as thrust needle bearings 27 and 27 that support the thrust load applied to the outer rings 30 and 30 described below. Of these, the thrust ball bearings 26, 26 support the loads in the thrust direction applied to the power rollers 8, 8 while allowing the power rollers 8, 8 to rotate. Such thrust ball bearings 26, 26 are each provided with a plurality of balls 29, 29 and the balls 29, 2 respectively.
An annular retainer 28, 28 for holding 9 in a rollable manner,
It is composed of an annular outer ring 30 which is a thrust bearing ring. The inner ring raceways of the thrust ball bearings 26, 26 are formed on the outer side surfaces of the power rollers 8, 8 and the outer ring raceways are formed on the inner side surfaces of the outer rings 30, 30 respectively.

The thrust needle bearings 27, 2 are also used.
7 includes a race 31, a retainer 32, and needles 33, 33. Race 31 and cage 32
And are combined so that they can be displaced slightly in the direction of rotation. Such thrust needle bearings 27, 27 are provided between the inner surfaces of the trunnions 6 and 6 and the outer surfaces of the outer rings 30, 30 in a state where the races 31, 31 are in contact with the inner surfaces of the trunnions 6, 6. It is sandwiched. The thrust needle bearings 27 and 27 as described above support the thrust load applied from the power rollers 8 and 8 to the outer rings 30 and 30, while the pivot shafts 22 and 22 and the outer rings 30 and 30 are supported by the thrust bearings 27 and 27. It is allowed to swing around the support shaft portions 21, 21.

Further, drive rods 34, 34 are respectively coupled to one end portion (the left end portion in FIG. 9) of each trunnion 6, 6, and a drive piston 35, is provided on an outer peripheral surface of an intermediate portion of each drive rod 34, 34. 35 is fixed. Then, each of these drive pistons 35, 35 is connected to a drive cylinder 36,
It is fitted in 36 in an oiltight manner.

Further, the casing 37, which is a fixed portion,
The support wall 38 provided inside, the input shaft 15 and the output gear 1
A pair of rolling bearings 39a, 39b are provided between the input shaft 15 and the output gear 18 and the supporting wall 3
It is rotatably supported inside 8. Further, in order to support the rolling bearings 39a and 39b around the input shaft 15, the rear surface of the holder 40, which is a thrust load supporting member, is fitted around the input shaft 15 so as to be displaceable in the axial direction (Fig. The disc leaf spring 42 is sandwiched between the right side of 8) and the loading nut 41 fixed to the outer peripheral surface of the input shaft 15. Even if the pressing device 9 is not operated, the disc leaf spring 42 can prevent the inner surfaces 2a, 4 of the discs 2, 4 from contacting each other.
It is provided in order to apply a preload by elastically contacting a with the peripheral surfaces 8a, 8a of the power rollers 8, 8.

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. Then, the rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 8 and the rotation of the output side disk 4 is taken out from the output gear 18. When transmitting the rotational force in this way, the input shaft 15 is pulled to the left in FIG. 8 based on the operation of the pressing device 9, and the outside of the pair of rolling bearings 39a and 39b (see FIG. 8). A thrust load to the left in FIG. 8 is applied to the rolling bearing 39a on the right side. or,
Based on the operation of the pressing device 9, the output gear 18 moves the input side disk 2, the power rollers 8, 8 and the output side disk 4.
8 is pushed to the right in FIG. 8, and the thrust load in the right direction in FIG. 8 is applied to the inside (left side in FIG. 8) rolling bearing 39b of the pair of rolling bearings 39a and 39b.

When the rotation speed ratio between the input shaft 15 and the output gear 18 is changed, the pair of drive pistons 3
5, 35 are displaced in opposite directions. As the drive pistons 35, 35 are displaced, the pair of trunnions 6, 6 are displaced in opposite directions. For example, the lower power roller 8 in FIG. 9 is located on the right side in FIG. The power rollers 8 are displaced to the left side in FIG. As a result, the peripheral surfaces 8a, 8a of the power rollers 8, 8 and the inner side surfaces 2 of the input side disk 2 and the output side disk 4 described above.
The direction of the tangential force acting on the contact portion with a and 4a changes. Then, with the change in the direction of the force, the trunnions 6, 6 swing about the pivots 5, 5 pivotally supported by the support plates 20, 20 in opposite directions in FIG. As a result, as shown in FIGS. 6 to 7, the peripheral surfaces 8a and 8a of the power rollers 8 and 8 and the inner surface 2 are
The contact position with a and 4a changes, and the rotation speed ratio between the input shaft 15 and the output gear 18 changes.

When the power rollers 8, 8 are displaced in the axial direction of the input shaft 15 as a result of elastic deformation of the components during power transmission, the power rollers 8, 8 are pivotally supported. The displacement shafts 7, 7 correspond to the support shaft portions 2 described above.
It rotates slightly around 1, 21. As a result of this rotation, the outer rings 30, 30 of the thrust ball bearings 26, 26 are
The outer surface and the inner surface of each trunnion 6, 6 are relatively displaced. Since the thrust needle bearings 27, 27 are present between the outer side surface and the inner side surface, the force required for this relative displacement is small. Therefore, as described above, a small force is required to change the inclination angles of the displacement shafts 7, 7.

[0019]

In the case of the conventional toroidal type continuously variable transmission constructed and operated as described above, the disc leaf spring 42, the rear surface of the holder 40 and the front surface of the loading nut 41 are accompanied by the operation. The contact part with (the left side of FIG. 8) rubs strongly. In the case of the conventional structure shown in FIGS. 8 to 9, since the lubrication of the space portion where the disc leaf spring 42 is installed between the back surface of the holder 40 and the front surface of the loading nut 41 is not particularly considered, each of the above-mentioned respective parts is Metal contact is likely to occur at the contact parts, and wear called fretting is likely to occur at each of these contact parts. When such wear occurs, the disc leaf spring 42
Edge of the holder and the back surface of the holder 40 or the loading nut 41
The front surface of the contact portion is caught, and the sliding of the contact portions cannot be performed smoothly. As a result, the displacement of the holder 40 in the axial direction with respect to the input shaft 15 is not smoothly performed, which causes performance degradation such as reduction in transmission efficiency of the toroidal-type continuously variable transmission.

When the wear is further remarkable, the disc leaf spring 4 is
Not only is the durability of the installation portion of No. 2 impaired, but abrasion powder may cause damage to other rolling contact portions, which may impair the overall durability of the toroidal type continuously variable transmission, which is not preferable. The toroidal type continuously variable transmission of the present invention was invented to eliminate the above-mentioned inconvenience.

[0021]

The toroidal type continuously variable transmission according to the present invention includes a rotary shaft, first and second disks, and a pressing device, like the conventional toroidal type continuously variable transmission described above. A trunnion, a power roller, a loading nut, a thrust load supporting member, and a spring member.
Of these, the first and second disks are rotatably supported with respect to the rotary shaft around the rotary shaft with their inner side surfaces facing each other. The pressing device is provided between the outer surface of the first disk and the rotary shaft, and rotates the first disk together with the rotary shaft while pressing the first disk toward the second disk. . Further, the trunnion swings around a pivot shaft that is twisted with respect to the center shafts of the first and second disks. The power roller is sandwiched between the first and second disks while being rotatably supported on the inner surface of the trunnion. The loading nut is fixed to a part of the rotary shaft.
Further, the thrust load supporting member is supported around the rotary shaft in a portion facing the loading nut so as to be movable in the axial direction with respect to the rotary shaft and can support the thrust load. Further, the spring member is sandwiched between the thrust load supporting member and the loading nut in an elastically compressed state. In particular, in the toroidal type continuously variable transmission of the present invention, a concave groove for circulating lubricating oil is provided on at least one of the surfaces of the thrust load supporting member and the loading nut that face each other. There is.

[0022]

The toroidal type continuously variable transmission of the present invention constructed as described above is based on the same action as that of the above-described conventional toroidal type continuously variable transmission, and is based on the operation between the first disk and the second disk. The rotational force is transmitted by, and the inclination angle of the trunnion is changed to change the rotational speed ratio between these two disks.

In particular, in the case of the toroidal type continuously variable transmission of the present invention, the spring member is formed due to the existence of the concave groove formed on at least one of the surfaces of the thrust load supporting member and the loading nut which face each other. A sufficient amount of lubricating oil can be circulated to the contact portion between the thrust load supporting member and the loading nut. Therefore, it is possible to prevent metal contact from occurring at each of these contact portions by interposing an oil film at each of these contact portions. Further, the torque to be transmitted by the toroidal type continuously variable transmission becomes large, and even when the spring member is completely crushed between the thrust load supporting member and the loading nut based on the action of the pressing device, Since the lubricating oil existing between the thrust load supporting member and the loading nut can be discharged through the groove, the contact portion can be efficiently lubricated.

[0024]

1 and 2 correspond to claims 1 and 2.
A first example of an embodiment of the present invention is shown. still,
The feature of the present invention resides in the structure for efficiently distributing the lubricating oil in the spring space 43 in which the disc leaf spring 42a for applying the preload is provided. Since the configuration and operation of the other parts are the same as those of the conventional structure described above, the description of the equivalent parts will be omitted or simplified, and the characteristic part of the present invention will be mainly described below.

The thrust load supporting member described in the claims and the cam plate 10 which constitutes the pressing device 9 has an outer peripheral surface of a portion of the input shaft 15 which is a rotating shaft near the one end of the intermediate portion (to the left in FIG. 1). The spline engagement allows the input shaft 15 to be freely supported only in the axial displacement. A main oil passage 44 is provided at the center of the input shaft 15,
The main oil supply passage 44 and the cam space 46 in which the rollers 12, 12 of the pressing device 9 are installed are formed in the input shaft 15 and the cam plate 10, and the branched oil supply passages 45, 4 are formed.
5 is connected.

Further, at a portion near one end of the input shaft 15,
The loading nut 41 is fixed. The loading nut 41 is screwed into a male screw portion formed on a portion of the input shaft 15 near one end. The tip end of the locking pin 48 inserted into the locking hole 47 formed in the diametrical direction of the loading nut 41 in a state where the inner peripheral surface and the outer peripheral surface of the loading nut 41 are in communication with each other is The loading nut 41 is prevented from loosening by engaging with any one of the locking grooves 49 formed in the portion. Further, the locking bolt 50 prevents the locking pin 48 from coming out of the locking hole 47.

Between the back surface of the cam plate 10 (left surface in FIG. 1) and the front surface of the loading nut 41 (right surface in FIG. 1), the disc spring 42a is axially arranged (left and right direction in FIG. 1). ) Is attached in a state in which the thickness dimension is elastically compressed. In this state, a portion of one side (the right side in FIG. 1) of the disc spring 42a near the outer peripheral edge is on the back side of the cam plate 10,
Similarly, the inner peripheral edge portions of the other surface (the left surface in FIG. 1) are elastically abutted on the front surface of the loading nut 41, respectively.

Further, an annular convex portion 51 is formed at a diametrically intermediate position on a part of the back surface of the cam plate 10, and a part of the outer diameter side opening of the spring space 43 in which the disc spring 42a is provided. Is blocking. On the other hand, a branch oil supply passage 45 is provided in a portion of the input shaft 15 facing the inner diameter side opening of the spring space 43.
A is formed so that the lubricating oil sent from the oil supply pump (not shown) into the main oil supply passage 44 can be sent into the spring space 43.

Further, in the case of the toroidal type continuously variable transmission of the present invention, the concave groove 5 for circulating the lubricating oil is formed on the front surface of the loading nut 41 facing the spring space 43.
2a and 52b are provided. In the case of this example, the concave groove 52
The reference numerals a and 52b are annular recessed grooves 52a formed over the entire circumference of the inner peripheral edge portion, and each is formed in the radial direction, and the annular recessed groove 52a and the loading nut 4 are formed.
A plurality (4 in the illustrated example) that communicate with the outer peripheral edge of 1
And concave grooves 52b and 52b.

In the case of the toroidal type continuously variable transmission of the present invention constructed as described above, the loading nut 41 is used.
Based on the existence of the concave grooves 52a and 52b formed on the front surface of the
A sufficient amount of lubricating oil can be spread in the spring space 43. That is, during operation of the toroidal type continuously variable transmission, a part of the lubricating oil fed into the main oil supply passage 44 is introduced into the spring space 43 through the branch oil passage 45a from the inner diameter side of the spring space 43. Sent in. The lubricating oil then flows into the spring space 43 through the grooves 52a and 52b. Since the outer diameter side opening of the spring space 43 is narrowed based on the existence of the convex portion 51, the lubricating oil that has flowed into the spring space 43 through the branch oil supply passage 45a is the concave groove 52a, The entire spring space 43 is distributed through 52b.

As a result, a sufficient amount of lubricating oil can be spread over the respective abutting portions between the disc leaf spring 42a installed in the spring space 43 and the back surface of the cam plate 10 and the front surface of the loading nut 41. You can Therefore, an oil film having sufficient strength (thickness) is interposed between each of these contact portions,
It is possible to prevent metal contact from occurring at each of these contact portions.
Further, the torque to be transmitted by the toroidal type continuously variable transmission is increased, and based on the action of the pressing device 9 (the amount of the rollers 12, 12 riding on the cam surfaces 13, 14 is increased), the cam plate 10 and The above loading nut 41
Even if the disc leaf spring 42a is completely crushed between the cam plate 1 and the cam plate 1 through the concave grooves 52a and 52b.
The lubricating oil existing between the rear surface of 0 and the front surface of the loading nut 41 can be discharged. Therefore, even if the torque to be transmitted is large, the contact portions can be lubricated efficiently.

In order to supply the lubricating oil into the spring space 43, the shape of the concave groove formed on the front surface of the loading nut 41 can be appropriately changed depending on the portion where fretting wear is likely to occur. For example, in the case where fretting wear is likely to occur at the inner peripheral edge portion of the disc leaf spring 42a and the front inner diameter portion of the loading nut 41, as in the second example shown in FIG.
A relatively wide concave groove 52c is formed in the portion near the inner diameter of the front surface over the entire circumference. On the other hand, when fretting wear is likely to occur on the outer peripheral edge portion of the other side of the disc leaf spring 41 and the diametrically intermediate portion of the back surface of the cam plate 10, as in the third example shown in FIG. A concave groove 52d is formed in the nut 41 at a portion near the outer diameter of the front surface over the entire circumference. Further, if necessary, the concave grooves 52a to 52d may be formed on the back surface of the cam plate 10 (FIG. 1) instead of the front surface of the loading nut 41 or together with the front surface of the loading nut 41. .

Next, FIG. 5 corresponds to claims 1 and 3,
The 4th example of embodiment of this invention is shown. In the case of the present example, as in the case of the conventional structure shown in FIGS. 8 to 9 described above, the thrust load supporting member described in the claims is mounted on the outer side of the pair of rolling bearings 39a and 39b. A holder 40 is provided for supporting the inner ring of the bearing 39a around the input shaft 15. In the case of this example, this holder 40
Is spline-engaged with the outer peripheral surface of the input shaft 15. In the case of this example, the back surface of the holder 40 (right surface of FIG. 5) and the front surface of the loading nut 41 (FIG. 5).
On the left side) and a plurality of concave grooves 52 extending in the radial direction.
A plurality of b and 52b are formed. Also in the case of this example, since the lubricating oil can be efficiently spread between the holder 40 and the loading nut 41, both surfaces of the disc spring 42a, the back surface of the holder 40, and the front surface of the loading nut 41 can be efficiently processed. It is possible to efficiently lubricate the contact portion with and.

[0034]

Since the present invention is constructed and operates as described above, it can contribute to the realization of a toroidal type continuously variable transmission having excellent durability and stable performance.

[Brief description of drawings]

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

2A and 2B are views showing a loading nut incorporated in the first example, FIG. 2A is a view seen from the right side of FIG. 1, and FIG. 2B is a sectional view taken along line YY of FIG.

3A and 3B are views showing a loading nut incorporated in the second example, in which FIG. 3A is a view seen from the right side of FIG. 1, and FIG. 3B is a cross-sectional view of FIG.

4A and 4B are views showing a loading nut incorporated in the third example, FIG. 4A being a view seen from the right side of FIG. 1, and FIG. 4B being a sectional view taken along the line of FIG.

FIG. 5 is a sectional view showing a fourth example of the embodiment of the present invention.

FIG. 6 is a side view showing the basic configuration of a conventionally known toroidal type continuously variable transmission in a state of maximum deceleration.

FIG. 7 is a side view showing the same state at the time of maximum acceleration.

FIG. 8 is a sectional view showing an example of a conventional specific structure.

9 is a cross-sectional view taken along line II of FIG.

[Explanation of symbols]

1 input axis 2 Input side disc (first disc) 2a Inside surface 3 output axes 4 Output side disc (second disc) 4a inner surface 5 Axis 6 trunnions 7 Displacement axis 8 power rollers 8a circumference 9 Pressing device 10 cam plate 11 cage 12 roller 13, 14 Cam surface 15 Input axis 16 needle bearing 17 Tsuba 18 output gears 19 keys 20 Support plate 21 Support shaft 22 Pivot shaft 23 circular holes 24, 25 radial needle roller bearings 26 Thrust ball bearings 27 Thrust needle bearing 28 cage 29 balls 30 outer ring 31 races 32 cage 33 needles 34 Drive rod 35 Drive piston 36 drive cylinder 37 casing 38 Support wall 39a, 39b Rolling bearing 40 holder 41 loading nut 42, 42a Disc spring 43 spring space 44 Main oil supply passage 45, 45a Branch oil supply passage 46 Cam space 47 Locking hole 48 Locking pin 49 Locking groove 50 locking bolt 51 convex 52a, 52b, 52c, 52d concave groove

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Claims (3)

(57) [Claims] 1. A rotating shaft, first and second discs rotatably supported around the rotating shaft in a state in which inner surfaces of the rotating shaft are opposed to each other, and a first disc A pressing device which is provided between the outer surface of the one disk and the rotary shaft, and which rotates the first disk together with the rotary shaft while pressing the first disk toward the second disk;
A trunnion that swings about a pivot that is twisted with respect to the central axes of the first and second discs, and the first and second trunnions that are rotatably supported by the inner surface of the trunnion. A power roller sandwiched between the two disks, a loading nut fixed to a part of the rotating shaft, and a portion of the rotating shaft that faces the loading nut and moves around the rotating shaft in the axial direction with respect to the rotating shaft. A toroidal stepless device including a thrust load supporting member that is freely supported and can support a thrust load, and a spring member that is sandwiched between the thrust load supporting member and the loading nut in an elastically compressed state. In a transmission, a groove for circulating lubricating oil is provided on at least one of the surfaces of the thrust load supporting member and the loading nut that face each other. Toroidal-type continuously variable transmission, characterized in that provided. 2. The toroidal stepless step according to claim 1, wherein the thrust load supporting member is a cam plate constituting a pressing device, and the concave groove is formed on the front surface of the loading nut facing the cam plate. transmission. 3. The thrust load supporting member is a holder for supporting an inner ring of a rolling bearing for rotatably supporting the rotary shaft with respect to the casing around the rotary shaft, and the concave groove is provided for the holder. The toroidal type continuously variable transmission according to claim 1, wherein the toroidal type continuously variable transmission is formed on both a rear surface and a front surface of a loading nut that is screwed to the rotary shaft so as to face the rear surface.