JP2003090402A - Toroidal continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To simplify the structure of sending lubrication oil to a necessary part concerning power rollers 9, 9 supported by trunnions 7b, 7c which are displaced by double-acting hydraulic actuators 67a', 67b', and realize miniaturization, lightness in weight and cost reduction. SOLUTION: The transmission supplies lubrication oil into the lubrication oil passages 64, 64 in the trunnions 7b, 7c through a lubrication connector terminal 77, 77 provided at the opposite side of the hydraulic actuators 67a', 76b'. The rod 70a, 70a of each hydraulic actuator 67a', 76b' are formed in a solid round-rod shape capable of reducing the diameter, and besides, a flexible lubrication hose is not required.

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 unit for an automatic transmission of an automobile 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. 2 and 3 has been studied and partially implemented as an automatic transmission for automobiles. This toroidal type continuously variable transmission supports the input side disk 2 concentrically with the input shaft 1 and is arranged concentrically with the input shaft 1, as disclosed in, for example, Japanese Utility Model Laid-Open No. 62-71465. The output disk 4 is fixed to the end of the output shaft 3. Inside the casing 5 (see FIG. 5 described later) in which the toroidal type continuously variable transmission is housed, a trunnion 7 swinging around the pivot shafts 6, 6 which are twisted with respect to the input shaft 1 and the output shaft 3 is provided. , 7 are provided.

The trunnions 7, 7 are provided with the pivots 6, 6 on the outer surfaces of both ends thereof, concentrically with each trunnion 7, 7 and one pair for each trunnion 7, 7.
The central axes of the pivots 6 and 6 are the discs 2 and 4 described above.
It does not intersect with the central axis of
4 exists at a twist position that is at a right angle or a substantially right angle with respect to the direction of the central axis of 4. In addition, each trunnion 7,
The base half of the displacement shafts 8 and 8 is supported at the center of 7, and the trunnions 7 and 7 are swung about the pivots 6 and 6 to adjust the inclination angles of the displacement shafts 8 and 8. It is freely adjustable. Power rollers 9 and 9 are provided around the first half of the displacement shafts 8 and 8 supported by the trunnions 7 and 7, respectively.
Is rotatably supported. The power rollers 9, 9 are sandwiched between the inner side surfaces 2a, 4a of the input side and output side disks 2, 4.

The inner surfaces 2a, 4a of the input side and output side disks 2 and 4 facing each other are obtained by rotating an arc centered on the pivot 6 or a curve close to such an arc. It has a concave surface with an arcuate cross section. Then, the peripheral surfaces 9a, 9a of the power rollers 9, 9 formed in the spherical convex surface are brought into contact with the inner side surfaces 2a, 4a. Further, a loading cam device 10 is provided between the input shaft 1 and the input side disc 2 and the loading side cam 2 is used by the loading cam device 10.
While being elastically pressed toward the output side disk 4, it can be rotationally driven.

When the toroidal type continuously variable transmission configured as described above is used, the loading cam device 10 causes the input side disk 2 to move to the plurality of power rollers 9 and 9 as the input shaft 1 rotates. Rotate while pressing. And
The rotation of the input side disk 2 is transmitted to the output side disk 4 via the plurality of power rollers 9, 9, and the output shaft 3 fixed to the output side disk 4 rotates.

In the case of changing the rotational speeds of the input shaft 1 and the output shaft 3, first, when decelerating between the input shaft 1 and the output shaft 3, the trunnions 7 with the pivot shafts 6, 6 as the centers, 7 is swung, and the peripheral surfaces 9 of the power rollers 9 and 9 are swung.
As shown in FIG. 2, the displacement shafts 8 and 9a are arranged so that the a and 9a come into contact with the central portion of the inner side surface 2a of the input side disk 2 and the outer peripheral side portion of the inner side surface 4a of the output side disk 4, respectively. Incline 8

On the contrary, when increasing the speed, the trunnions 7 and 7 are swung so that the power rollers 9 and 9 are rotated.
As shown in FIG. 3, the peripheral surfaces 9a, 9a of the input side disk 2
The displacement shafts 8 and 8 are tilted so as to contact the outer peripheral portion of the inner side surface 2a and the central portion of the inner side surface 4a of the output side disk 4, respectively. These displacement axes 8, 8
If the inclination angle is set to an intermediate value between FIG. 2 and FIG. 3, an intermediate gear ratio can be obtained between the input shaft 1 and the output shaft 3.

Further, FIGS. 4 to 5 show Japanese Utility Model 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
And are rotatably supported around the cylindrical input shaft 11. A loading cam device 10 is provided between the end of the input shaft 11 and the input side disk 2. On the other hand, the output side disk 4 has an output gear 1
2 are connected so that the output side disk 4 and the output gear 12 rotate in synchronism with each other.

The pivots 6 and 6 provided concentrically with each other at both ends of the pair of trunnions 7 and 7 swing on the pair of support plates 13 and 13, which are support members, and in the axial direction (front and back directions in FIG. 4). ,
It is supported so that it can be displaced in the left-right direction in FIG. And
The base parts of the displacement shafts 8, 8 are supported by the intermediate parts of the trunnions 7, 7. The displacement shafts 8 and 8 decenter the base half portion and the front half portion from each other. Then, the base half portion of these is rotatably supported on the intermediate portion of each trunnion 7, 7 and the power rollers 9, 9 are provided on the respective front half portions.
It is rotatably supported via a radial needle bearing which is the rolling bearing described in the claims.

The pair of displacement shafts 8 and 8 are provided 180 degrees opposite to the input shaft 11. or,
The directions in which the base half and the front half of these displacement shafts 8, 8 are eccentric are the same as the rotational directions of the input side and output side disks 2 and 4 (left and right opposite directions in FIG. 5). .
Further, the eccentric direction is a direction substantially orthogonal to the disposing direction of the input shaft 11. Therefore, the power rollers 9, 9 are supported so as to be slightly displaceable with respect to the arrangement direction of the input shaft 11.

Further, between the outer side surface of each of the power rollers 9 and 9 and the inner side surface of the intermediate portion of each of the trunnions 7 and 7, in order from the outer surface side of each of the power rollers 9 and 9, thrust ball bearings are provided. 14, 14 and thrust needle bearing 15, 1
And 5 are provided. Of these, thrust ball bearings 14, 1
Reference numeral 4 denotes a rolling bearing as set forth in the claims, which allows the power rollers 9, 9 to rotate while supporting a load in the thrust direction applied to the power rollers 9, 9.
In addition, the thrust needle bearings 15 and 15 are connected to the thrust roller bearings 14 and 1 from the power rollers 9 and 9, respectively.
While supporting the thrust load applied to the outer races 16 and 16 that form part 4, the first half of each displacement shaft 8 and the outer race 1 described above.
6 and 16 are allowed to oscillate around the base halves of the respective displacement shafts 8 and 8. Furthermore, each of the trunnions 7,
The hydraulic actuators 17, 17 allow the pivot shafts 6, 6 to be displaced in the axial direction.

In the case of the toroidal type continuously variable transmission configured as described above, the rotation of the input shaft 11 is transmitted to the input side disk 2 via the loading cam device 10. And
The rotation of the input side disk 2 is transmitted to the output side disk 4 via the pair of power rollers 9, 9, and the rotation of the output side disk 4 is taken out from the output gear 12.

When changing the rotational speed ratio between the input shaft 11 and the output gear 12, the actuators 17 and 1 are used.
7, the pair of trunnions 7 and 7 in opposite directions, for example, the lower power roller 9 of FIG. 5 is on the right side of the figure, the upper power roller 9 of FIG. 5 is on the left side of FIG. Displace each. As a result, the direction of the tangential force acting on the abutting portions between the peripheral surfaces 9a, 9a of the power rollers 9, 9 and the inner side surfaces 2a, 4a of the input side disk 2 and the output side disk 4 changes. To do. Then, with the change in the direction of the force, the trunnions 7, 7 swing in opposite directions about the pivots 6, 6 pivotally supported by the support plates 13, 13. As a result, as shown in FIGS. 2 to 3, the contact positions between the peripheral surfaces 9a, 9a of the power rollers 9, 9 and the inner side surfaces 2a, 4a change, and the input shaft 11 and The rotation speed ratio with the output gear 12 changes.

During power transmission by the toroidal type continuously variable transmission, the power rollers 9, 9 are displaced in the axial direction of the input shaft 11 due to elastic deformation of the respective constituent parts. Then, the displacement shafts 8, 8 supporting the power rollers 9, 9 slightly rotate about their respective base halves. As a result of this rotation, the thrust ball bearings 14 and 1
4, the outer surface of the outer ring 16, 16 and the trunnions 7, 7
Relative to the inner surface of the. Since the thrust needle bearings 15, 15 are present between the outer side surface and the inner side surface, the force required for this relative displacement is small.

In the case of the toroidal type continuously variable transmission constructed and operated as described above, the input shaft 11 and the output gear 12 are provided.
The power transmission between the two is performed by two power rollers 9, 9. Therefore, the peripheral surface 9 of each power roller 9, 9
a, 9a and the inner side surface 2 of both the input side and output side disks 2 and 4
The force per unit area transmitted between a and 4a becomes large, and the limit of the power that can be transmitted is relatively low. In view of such circumstances, it has been conventionally considered to increase the number of power rollers 9 in order to increase the power that can be transmitted by the toroidal type continuously variable transmission.

As an example of a structure for increasing the number of power rollers 9, 9 for such a purpose, conventionally, three power rollers 9, between a pair of input side disk 2 and output side disk 4, 9 is arranged and the power is transmitted by these three power rollers 9, 9, for example, JP-A-3-746.
It is conventionally known as described in Japanese Patent Publication No. 67. In the case of the structure described in this publication, as shown in FIG. 6, there are support members at three positions at equal intervals in the circumferential direction of the fixed frame 18, and the support pieces 19 bent at 120 degrees. , 19 in the middle. The trunnions 7, 7 are respectively supported between the adjacent support pieces 19, 19 so as to be swingable and axially displaceable.

The trunnions 7 and 7 are displaceable in the axial direction of a pivot 6 which is concentrically provided at both ends by hydraulic actuators 17 and 17, respectively. The hydraulic cylinders 20, 20 forming the actuators 17, 17 communicate with the discharge port of the pump 22, which is a hydraulic pressure source, via the control valve 21. The control valve 21 includes a sleeve 23 and a spool 24, each of which is axially displaceable (left and right in FIG. 6). Each of the actuators 17 and 17 is of a double-acting type which generates an axial force in any direction with respect to the axial direction by switching the pressure oil supply / discharge direction.

When changing the inclination angle of the power rollers 9, 9 pivotally supported by the displacement shafts 8, 8 to the trunnions 7, 7, the sleeve 23 is axially moved by the control motor 25 (see FIG. 6). Left and right). As a result, the pressure oil discharged from the pump 22 is sent to each of the hydraulic cylinders 20, 20 through the hydraulic pipe. The drive pistons 26, 26 fitted into the hydraulic cylinders 20, 20 for displacing the trunnions 7, 7 in the axial direction of the pivot shaft are provided with the input side discs 2.
And the output side disk 4 (see FIGS. 2 to 3) is displaced in the same direction with respect to the rotation direction. The trunnions 7, 7 are displaced in the axial direction of the pivot along with this displacement, and are further swung about the pivot as in the case of the structure shown in FIGS. In addition, the drive pistons 26,
The hydraulic oil pushed out from each of the hydraulic cylinders 20 and 20 with the displacement of 26 is returned to the oil sump 27 through a hydraulic pipe (not partly shown) which also includes the control valve 21.

On the other hand, the displacement of the drive piston 26 and the trunnion 7 connected to the drive piston 26 due to the feeding of the pressure oil is transmitted to the spool 24 via the recess cam 28 and the link 29, and the spool 24 is axially moved. Shift to. As a result, with the drive piston 26 displaced by a predetermined amount, the flow path of the control valve 21 is closed, and the supply and discharge of pressure oil to and from the hydraulic cylinders 20, 20 is stopped. Therefore, the amount of displacement of each trunnion 7 in the axial direction is determined by the sleeve 2 by the control motor 25.
It is only according to the displacement amount of 3.

In the case of the conventional toroidal type continuously variable transmission constructed and operated as described above, the installation space for the actuators 17, 17 becomes large and the device becomes large. On the other hand, Japanese Patent Laid-Open No. 7-259947 discloses a double-acting hydraulic actuator in which three trunnions 7 and 7 are connected in series by link mechanisms 30 and 30 as shown in FIG.
A structure for displacing the plurality of trunnions 7 by the actuator 17 is described. Further, in Japanese Patent Laid-Open No. 11-303963, as shown in FIG. 8, the supporting pieces 19a, 19a are supported so as to be capable of swinging displacement.
A structure is described in which the movement can be transmitted between the trunnions 7 and 7 that are adjacent to each other in the circumferential direction by the support pieces 19a and 19a. Also in the case of the structure shown in FIG. 8, the driving actuators 17, 17 can axially press the end faces of the pivots 6, 6 attached to the trunnions 7, 7 provided at both ends in the circumferential direction.

In the case of the conventional structure shown in FIGS. 7 to 8, the installation space for the actuator 17 can be made small and the size and weight can be reduced. However, in order to strictly regulate the displacement amount of all the trunnions 7, 7. However, it is necessary to configure each movable part with extremely high precision, which increases the cost. That is, the toroidal type continuously variable transmission is
Although depending on the size, the trunnions 7, 7 are displaced by about 0.1 mm in the axial direction of the pivots 6, 6,
The shift operation may start. Therefore, when the displacement amount of the trunnions 7, 7 is different by about 0.1 mm, the inclination angles of the trunnions 7, 7 about the pivots 6, 6 are different from each other, and the toroidal type continuously variable transmission is There is a possibility that the transmission efficiency and the durability will be significantly reduced.

Therefore, when the structure shown in FIGS. 7 to 8 is carried out, the rattling of each movable portion is made extremely small, and the displacement of the three trunnions 7, 7 is set to more than 0.1 mm. Must be synchronized to each other with a sufficiently small level (accuracy). On the other hand, in order to smoothly perform the displacement of each movable part and to suppress the rattling to a minimum, the dimensional accuracy and the shape accuracy of each constituent member must be extremely high. The processing work becomes troublesome and the cost increases. Moreover, as shown in FIGS.
The trunnions 7, 7 are connected in series with each other in the displacement direction, and the actuators 17, 1 are provided only at the ends in the connection direction.
When 7 is provided, the trunnions 7 and 7 are included.
The elastic deformation of the member that transmits the displacement must also be taken into consideration. In this state, all the above trunnions 7, 7
It is very difficult to precisely synchronize the displacements of (at levels well below 0.1 mm) with each other.

[0023]

Description of the Prior Invention As an invention made in view of such circumstances, there is an invention of a toroidal type continuously variable transmission as shown in FIGS. 9 to 12 (Japanese Patent Application No. 2000-280189). Since the embodiment of the present invention described later and the embodiment of the prior invention are common in many parts, the embodiment of the prior invention will be described in detail below. In addition, the above-mentioned FIGS.
Is a so-called double-cavity type in which two input side disks 2 and two output side disks 4 are provided in parallel with each other in the direction of power transmission, and a power is provided between each input side disk 2 and output side disk 4. The figure shows the case where the previous invention is applied to a toroidal type continuously variable transmission in which three rollers 9 are provided and three rollers are provided in total. FIG. 10 shows only one of the cavities (a portion for transmitting power by arranging the input side disk 2, the output side disk 4, and the power rollers 9, 9). However, there is another cavity. The basic structure and operation of such a double-cavity toroidal type continuously variable transmission are well known in the art, and therefore the illustration and description of the overall configuration are omitted.

Mounting portion 31 provided on the inner surface of the casing 5a
The frame 18 is fitted with studs 33, 3 which are inserted through the mounting holes 32, 32 at three positions on the outer diameter side end of the frame 18.
3 and nuts 3 screwed to the studs 33, 33.
It is fixed by binding with 4. In the illustrated example, the gear housing 35 is fixed between the mounting portion 31 and the frame 18 by the studs 33, 33 and the nut 34. One on the inner diameter side of the gear housing 35
An output sleeve 36 having a pair of output side disks 4 spline-engaged at both ends thereof is provided with a pair of rolling bearings 37, 37.
Is rotatably supported by the output sleeve 3
The output gear 38 provided on the outer peripheral surface of the intermediate portion of No. 6 is housed inside the gear housing 35.

Further, the frame 18 is formed in a star shape as a whole, and the radial middle portion or outer diameter side portion thereof is formed into a bifurcated shape so that the three holding portions 39, 39 are circumferentially or the like. Formed at intervals. Then, these holding portions 39, 3
The intermediate portions of the support pieces 19b, 19b are pivotally supported by the second pivots 40, 40 via the needle bearings 41, 41 at the radial intermediate portions of 9, respectively. Each supporting piece 19
b and 19b are cylindrical mounting portions 42 arranged around the second pivots 40, 40, and a pair of support plate portions 43 protruding radially outward from the outer peripheral surface of the mounting portions 42, And 43. The intersecting angle between the pair of support plate portions 43, 43 is 120 degrees. Therefore, the support plate portions 43, 43 of the support pieces 19b, 19b adjacent to each other in the circumferential direction are parallel to each other.

Circular holes 44, 44 are formed in each of the support plate portions 43, 43 as described above. Each supporting piece 19
When b and 19b are in a neutral state, the circular holes 44 and 44 formed in the support plate portions 43 and 43 of the support pieces 19b and 19b adjacent to each other in the circumferential direction are concentric with each other. Then, in each of these circular holes 44, 44, each of the trunnions 7a, 7b, 7
The pivots 6, 6 provided at both ends of c are supported by radial needle bearings 45, 45. The outer peripheral surfaces of the outer rings 46, 46 constituting the radial needle bearings 45, 45 are spherical convex surfaces. Such outer rings 46, 46 are fitted in the respective circular holes 44, 44 so as to be swingably displaceable without rattling.

Further, studs 48 and 48 are screwed into the screw holes 47 and 47 provided in the support plate portions 43 and 43, respectively, and the tip surfaces of the studs 48 and 48 are attached to the trunnion 7a and the trunnion 7a, respectively. It is in contact with both end faces of 7b and 7c. The tip surfaces of the studs 48, 48 are spherical convex surfaces, and the trunnions 7a, 7 are provided between a pair of studs 48, 48 provided at positions facing each other.
The swing displacement of b and 7c is possible. Further, lock nuts 49, 49 are provided at the base end portions of these studs 48, 48.
Are screwed together to prevent the studs 48, 48 from being loosened carelessly. Incidentally, such studs 48, 48
Is three trunnions 7a provided in a single cavity,
The displacements 7b and 7c in the circumferential direction of both the input side and output side disks 2 and 4 are provided so as to be synchronized with each other via the support pieces 19b and 19b. If the displacement can be sufficiently synchronized by a hydraulic actuator described later, the studs 48, 48 and the lock nut 49,
49 may be omitted.

The above three trunnions 7a, 7b, 7c
As described above, a slight displacement in the circumferential direction of the disks 2 and 4 due to the swinging of the support pieces 19b and 19b about the second pivots 40 and 40, respectively, and The oscillating displacement around the pivots 6 provided at both ends is freely supported. In order to displace the trunnions 7a, 7b, 7c in the axial direction of the pivot shafts 6, 6 provided at both ends of the trunnions 7a, 7b, 7c in order to perform a speed change operation,
In the case of the toroidal type continuously variable transmission of the previous invention, the following actuator is provided,

First, the trunnion 7a, which corresponds to a part of the trunnions described in claim 2 and is horizontally provided at the center of the lower part, is formed by a pair of hydraulic actuators 50a and 50b provided below both ends of the trunnion 7a. The displacement is freely driven via the link arms 51a and 51b, respectively. Each of these hydraulic actuators 50a and 50b pushes out the rod 53 by supplying pressure oil into the cylinder 52, but even if the supply of pressure oil to the cylinder 52 is stopped, the rod 53 will not move unless the external force acts. 5
It uses a single-acting type that is not drawn into 2.
The above hydraulic actuators 50a and 50b are
The rods 5 are concentric with each other and the pushing directions of the rods 53 are opposite to each other.
3 is pushed out in a direction away from another hydraulic actuator 50a (or 50b), and is supported and fixed in the casing 5a.

Further, the respective link arms 51a and 51b have their respective intermediate parts supported by a third pivot 54 having a hollow cylindrical shape so as to be swingable. Each of these third pivots 54, 54 is parallel to each of the second pivots 40, 40,
The inside communicates with the discharge port of a fuel pump (not shown).
During operation of the toroidal type continuously variable transmission, each of the above-mentioned third pivots 5
Lubricating oil (traction oil) is fed into the inside of 4, 54. The link arms 51a, 51, each of which has an intermediate portion pivotally supported by the third pivots 54, 54 as described above.
b is abutting one side surface of each base end portion (lower end portion of FIG. 9) against the tip end surface of the rod 53 forming each of the hydraulic actuators 50a and 50b, and one side surface of each tip end portion (upper end portion of FIG. 9). The sides are engaged with the ends of pivots 6, 6 provided at both ends of the trunnion 7a. The portions of the base ends of the link arms 51a and 51b that abut the tip surfaces of the rods 53 are partially cylindrical convex curved surfaces so that the abutting portions can be smoothly swung and displaced.

In the illustrated example, as shown in detail in FIG. 11, cylindrical protrusions 55 are formed on the surfaces of the distal ends of the link arms 51a and 51b which face each other.
On the other hand, the pivots 6, 6 provided at both ends of the trunnion 7a
A circular hole 56 having an inner diameter larger than the outer diameter of the cylindrical convex portion 55 is formed in the central portion of the above so as to be open to the end faces of the respective pivots 6, 6. And each of the link arms 5
1a, 51b of the cylindrical convex portion 55 in the circular hole 56,
Inserted loosely. In this state, the inner peripheral edge of the O-ring 57, which is locked to the inner peripheral surface of the circular hole 56, is elastically contacted with the outer peripheral surface of the intermediate portion of the cylindrical convex portion 55 over the entire circumference. Oil-tightness is maintained between the inner peripheral surface of the hole 56 and the outer peripheral surface of the cylindrical convex portion 55.

A thrust needle bearing 58 is provided between the end faces of the pivots 6 and 6 and the side faces of the tip portions of the link arms 51a and 51b. Of the pair of races forming the thrust needle bearing 58, one side of the races 59 on the side of the link arms 51a and 51b, which is in contact with the side surface of the tip end of each of the link arms 51a and 51b, has a spherical shape. It is a convex surface or a conical convex surface. With such a structure, the displacement can be freely transmitted between the link arms 51a and 51b and the trunnion 7a, and the link arms 51 centered on the third pivots 54 and 54 are provided.
smooth swing displacement of a and 51b, and the above-mentioned pivots 6,
A smooth rocking displacement of the trunnion 7a around 6 is freely possible.

Further, the inside of each of the third pivots 54, 54 and the inside of the cylindrical convex portion 55 are defined by the respective link arms 5.
Concave groove 6 formed in the axially intermediate portion of the center holes of 1a and 51b
0 and an oil passage hole 61 formed inside the first half (upper half of FIGS. 9 and 11) of each of the link arms 51a and 51b. The downstream end opening of the oil passage 61 is closed by a plug 62. Therefore, the total amount of the lubricating oil fed into the third pivots 54, 54 from the oil feed pump (not shown) is the pivots 6, 6 respectively.
It is fed into a circular hole 56 provided at the center of the. The lubricating oil thus fed into the circular hole 56 is used to lubricate the rolling contact portion of the toroidal type continuously variable transmission. That is, a part of this lubricating oil is ejected from the nozzle holes 63, 63 provided in the trunnion 7a and is supported by the inner side surfaces 2a, 4a of the input side disk 2 and the output side disk 4 and the trunnion 7a. Lubricate the rolling contact portion of the power roller 9 with the peripheral surface 9a.

Further, the remaining portion of the lubricating oil is sent to each rolling bearing and the sliding contact portion through the lubricating oil passage 64 provided inside the trunnion 7a. First, the radial needle bearing 45 supporting the above-mentioned pivots 6, 6,
The lubricating oil can be fed into 45 through a throttle plug 65. Further, another throttle plug 6 is also provided at the sliding contact portion between the tip surface of the stud 48 and the trunnion 7a.
It is possible to send it via 6 freely. Further, the remaining lubricating oil was provided between the thrust needle bearing 15 and the thrust ball bearing 14 supporting the power roller 9 with respect to the trunnion 7a, and further between the displacement shaft 8 and the trunnion 7a and the power roller 9. It can be fed freely into a radial needle bearing.

On the other hand, the trunnions 7b and 7c, which correspond to the remaining trunnions described in claim 2 and are provided on both sides of the upper portion in the inclined direction, are the extension of the pivots 6 and 6 with respect to these trunnions 7b and 7c. The double-acting hydraulic actuators 67a and 67b as described in detail above are provided for each of the trunnions 7b and 7c. By supplying and discharging the pressure oil to and from the hydraulic actuators 67a and 67b, the trunnions 7b and 7c can be displaced in the axial direction of the pivot shafts 6 and 6 provided at both ends thereof.

Each of the hydraulic actuators 67a and 67b described above.
Is a piston 69 fitted in a cylinder 68 in an oil-tight manner, and a base end portion (lower end portion in FIG. 12) of the rod 70 is attached in an axial direction (see FIG.
(2) (up and down direction) is rotatably connected while preventing rattling. In the illustrated example, the piston 69 is sandwiched by a pair of thrust needle bearings 73, 73 so as to be freely rotatable.
Since both surfaces of the piston 69 have a function as raceway surfaces of the thrust needle bearings 73, 73, they are hardened by quenching and have a smooth surface.
Further, in order to prevent the rattling in the axial direction, in the illustrated example, the piston 69 and the pair of thrust needle bearings 73,
73 is sandwiched between an outward flange-shaped collar portion 71 provided in the intermediate portion of the rod 70 and a taper snap ring 72 locked to a portion of the rod 70 near the intermediate portion proximal end.

Each hydraulic actuator 67a as described above,
A male screw is formed on the outer peripheral surface of the first half (the upper half of FIG. 12) of the rod 70 that constitutes 67b. The tip portion of such a rod 70 is screwed into a screw hole 74 provided at the center of the pivot shaft projecting from one end surface (lower end surface of FIG. 9) of each of the trunnions 7b and 7c, and further by a lock nut 75. It is fixed. In this state, the trunnions 7b and 7c are displaced in the axial direction of the pivot shafts 6 and 6 provided at both ends by supplying and discharging the pressure oil to and from the hydraulic actuators 67a and 67b.

Further, in the case of the toroidal type continuously variable transmission according to the previous invention, the rod 70 constituting each of the hydraulic actuators 67a and 67b has a circular tubular shape. And
A lubricating oil passage provided in the rod 70 by connecting a downstream end of a flexible oil supply hose (not shown) having flexibility to a connecting portion provided at a base end portion (lower end portion in FIGS. 9 and 12) of the rod 70. 7
Lubricating oil can be fed into 6 freely. Then, in this way, through the lubricating oil flow passage 76 in the rod 70, the nozzle hole 63 and the lubricating oil flow passage 64 in each of the trunnions 7b and 7c.
The lubricating oil sent in is used to lubricate each part, as in the case of the lubricating oil sent into the circular hole 56 of the trunnion 7a.

The supply and discharge of pressure oil to and from the pair of hydraulic actuators 50a and 50b, each of which is a single-acting type, and the pressure oil to the hydraulic actuators 67a and 67b, which are of a double-acting type, are described above. Supply and discharge is controlled by a single control valve 21
(Refer to FIG. 6) to perform them in synchronization with each other. And
The three trunnions 7a, 7b, 7c are displaced in the same direction and by the same length with respect to the rotation directions of the input side and output side disks 2 and 4. Each trunnion 7
The displacement of a, 7b, and 7c is caused by the stud 4 as described above.
It is also mechanically synchronized by 8, 48. Further, since the trunnions 7a, 7b, 7c are driven by the hydraulic actuators 50a, 50b, 67a, 67b provided respectively, the members are elastically deformed by transmitting the force for displacement, and the trunnions are There is no difference in the displacement of 7a, 7b and 7c. Therefore, each of these trunnions 7
The displacement amounts of a, 7b, and 7c are exactly matched.

Each of these trunnions 7a, 7b, 7c is
Based on the displacements thus synchronized with each other, the pivots 6, 6 provided at both ends of the respective shafts swing. That is, based on this displacement, as described above, the force applied in the tangential direction to the rolling contact portion between the peripheral surfaces 9a and 9a of the power rollers 9 and 9 and the inner side surfaces 2a and 4a of the disks 2 and 4, respectively. The direction changes. Due to this change, the trunnions 7a, 7b, 7c are pivotally displaced about the pivots 6, 6 provided at both ends thereof. The displacement of each of the trunnions 7a, 7b, 7c performed in this manner is caused by any one of the trunnions 7c (on the upper left side in FIG. 9).
It is taken out by a precess cam 28 fixed around the intermediate portion proximal end portion of the rod 70 connected to the. And
The displacement of the precess cam 28 is
It is transmitted to the spool 24 of the control valve 21 (FIG. 6), and the opening / closing control of the control valve 21 is performed. The control of this portion is the same as that of the conventional structure shown in FIG.

The toroidal type continuously variable transmission of the prior invention constructed and operated as described above is shown in FIG. 9 showing the structure of the prior invention and FIG. 6 showing the conventional structure viewed from the same direction as FIG. As is clear by comparing the above, it is possible to make the whole compact. That is, the hydraulic actuators 50a, 50b, 67a, 67b for displacing the trunnions 7a, 7b, 7c.
However, the amount of radial projection from the outer peripheral edges of both the input side and output side disks 2 and 4 can be reduced. In other words, the hydraulic actuators 50a, 50b, 67a, 67b can be efficiently arranged, and the outer size of the casing 5a for housing the toroidal type continuously variable transmission can be reduced. As a result, the toroidal type continuously variable transmission can be made smaller and lighter, so that the degree of freedom in designing a vehicle incorporating the toroidal type continuously variable transmission can be increased.

[0042]

In the case of the structure according to the previous invention shown in FIGS. 9 to 12, the nozzle holes 63 in the trunnions 7b and 7c which are displaced by the double-acting hydraulic actuators 67a and 67b are provided. In order to feed the lubricating oil into the lubricating oil passage 64, the above-mentioned hydraulic actuators 67 are provided.
The rod 70 forming a and 67b has a circular tubular shape, and the end portion of a flexible oil supply hose is connected to the connecting portion provided at the base end portion of the rod 70. By adopting such a configuration, the following problems to be solved occur. A screw portion for connecting the end portion of the oil supply hose to the base end portion of the rod 70 is required. As the threaded portion, a female threaded portion provided on the rod 70 side and a male threaded portion provided on the refueling hose side are necessary, but in both cases, strength is ensured while satisfying functions such as smooth oil circulation. In order to do this, sufficient wall thickness is required. Therefore, the outer diameter of the rod 70 increases, and the hydraulic actuators 67 are correspondingly increased.
The inner diameter of the piston 69 forming a and 67b becomes large. Therefore, each of these hydraulic actuators 67a, 67
In order to secure the pressure receiving area of the piston 69 in order to secure the output of b, these hydraulic actuators 67a,
It becomes difficult to reduce the size (size) of 67b. It is difficult to ensure the durability of a flexible oil supply hose that is stored in the casing 5a and is continuously exposed to lubricating oil (traction oil) that becomes hot during operation, and an expensive material is required to ensure sufficient durability. Will have to be used, which will increase the cost. The structure of the part that connects the downstream end of the oil supply hose to the end of the rod 70 having the precess cam 28 fixed to the end becomes complicated, and the volume of the structure of this part is increased to accommodate the toroidal type continuously variable transmission. The outer size of the casing 5a (particularly the width dimension in the left-right direction in FIG. 9) becomes large, which deteriorates the vehicle mountability. The toroidal type continuously variable transmission of the present invention is
The present invention was devised to solve all of the above problems.

[0043]

All of the toroidal type continuously variable transmissions of the present invention include a casing and a casing, like the conventionally known toroidal type continuously variable transmissions shown in FIGS. An input shaft rotatably supported in the casing, an input side disk rotatably supported around the input shaft together with the input shaft, and an inner side surface thereof opposed to an inner side surface of the input side disk. In the state, it is arranged concentrically with this input side disk and is provided between the input side disk and the output side disk, and the output side disk which is freely rotatable relative to this input side disk. With respect to a pair of input side discs and output side discs that swing about a pivot in a twisted position (in the case of claim 2, as shown in FIG.
Individual trunnions, and one displacement axis for each trunnion protruding from the inner surface of each of these trunnions, and a rolling bearing around each of these displacement axes on the inner surface of each of these trunnions. One power roller for each trunnion sandwiched between the inner surfaces of the input side disc and the output side disc in a state of being rotatably supported, and these trunnions at their respective end portions. An actuator for axially displacing the pivot shaft provided in the above, and a lubricating oil passage provided inside each of the trunnions for supplying lubricating oil to a portion of each power roller that requires lubrication.

Particularly, in the toroidal type continuously variable transmission according to the first aspect, at least a part of the trunnions among the plurality of trunnions for each of the pair of input side disks and output side disks is displaced. The actuators for this are double-acting hydraulic actuators, one for each trunnion provided on the extension of the pivot for the trunnion. The upstream end opening of the lubricating oil passage provided inside the trunnion that is displaced by the double-acting hydraulic actuator is the pivot on the opposite side of the pivot to which the output member of each of these double-acting hydraulic actuators is connected. Is provided at the center of the end face of the.

Further, in the toroidal type continuously variable transmission according to the second aspect, a part of the trunnions among the three trunnions provided for each of the pair of input side disks and output side disks. Is a pair of single-acting hydraulic actuators for displacing some of the trunnions in opposite directions via the link arms. On the other hand, the actuator for displacing the remaining trunnions is a double-acting hydraulic actuator provided for each of the remaining trunnions on the extension of the pivot axis related to the remaining trunnions. Then, the upstream end opening of the lubricating oil passage provided inside the trunnion displaced by these double-acting hydraulic actuators is
The output member of each of these double-acting hydraulic actuators is provided at the center of the end face of the pivot opposite to the pivot to which it is coupled.

[0046]

In the case of the toroidal type continuously variable transmission of the present invention configured as described above, the double-acting hydraulic actuator of the double-acting hydraulic actuator is constructed based on the structure for feeding the lubricating oil into the lubricating oil passage inside the trunnion. There is no need to increase the outer diameter of the rod. Therefore, even in consideration of ensuring the output of the hydraulic actuator, the hydraulic actuator can be downsized (smaller in diameter). Further, it becomes possible to feed the lubricating oil into the lubricating oil passage without using a flexible oil supply hose, and it is possible to secure sufficient durability without using an expensive material. it can. Furthermore, it is not necessary to connect the downstream end of the refueling hose to the end portion of the rod having the precess cam fixed to the end portion, and it is possible to prevent the outer size of the casing that houses the toroidal type continuously variable transmission from increasing. The vehicle mountability can be improved.

Further, in the case of the toroidal type continuously variable transmission according to the second aspect of the invention, in addition to the above-mentioned operation, the installation space for the actuator for displacing each trunnion is provided as in the case of the above-mentioned invention. At the same time as reducing the size and weight of the trunnion, the amount of displacement of each trunnion is strictly regulated so that an accurate gear shift operation can be performed. Further, the displacement amount of each trunnion can be strictly regulated without extremely increasing the shape accuracy and dimensional accuracy of each constituent member. Furthermore,
Since an actuator is provided for each trunnion,
An error due to elastic deformation due to displacement transmission does not enter, and the displacement amount of each trunnion can also be strictly regulated from this aspect. As a result, the transmission efficiency and durability of a toroidal type continuously variable transmission in which three power rollers are provided between a pair of input-side discs and output-side discs are sufficiently secured while aiming for downsizing and weight reduction. it can.

[0048]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows a first embodiment of the present invention.
An example is shown. The features of this example are that the nozzle holes 63 and the lubricating oil passages 64, 64 provided in the trunnions 7b, 7c that are displaced in the axial direction of the pivots 6, 6 by the double-acting hydraulic actuators 67a ', 67b'. This is the structure of the part that feeds the lubricating oil (traction oil) inside. Since the structure and operation of the other parts are the same as the structure according to the previous invention shown in FIGS. 9 to 12 described above, the same parts are designated by the same reference numerals to omit or simplify duplicate description, and The description will focus on the characteristic parts of the present invention and the parts not shown in FIGS. In the case of the illustrated example, each of the trunnions for supplying the lubricating oil to the portion of the power roller which requires lubrication by the nozzle hole 63 and the lubricating oil passages 64, 64 is described. Corresponds to the lubricating oil flow path provided inside.

The actuators 67a 'and 67b', each of which is a double-acting type, are different from the case of the above-mentioned invention in that they are rods 70 having a solid rod shape (not a circular tube shape).
The output members are a and 70a. Then, the male screw portions provided at the tips of the rods 70a, 70a are screwed into the screw holes 74, 74 provided at the central portion of the pivot shaft 6 at one end portion (the lower end portion in FIG. 1) of the trunnions 7b, 7c. The trunnions 7b and 7c are joined and fixed to the trunnions 7b and 7c by tightening the lock nuts 75 and 75. By forming the rods 70a, 70a into a solid rod shape, the outer diameters of the rods 70a, 70a can be adjusted to those shown in FIGS.
It is smaller than the case of the cylindrical rods 70, 70 incorporated in the structure according to the previous invention shown in FIG. Therefore, the nozzle holes 63 are provided in the rods 70a, 70a.
Also, the lubricating oil passages 76 (see FIGS. 9 and 12) for feeding the lubricating oil into the lubricating oil passages 64, 64 are not provided.

As described above, in accordance with the fact that the lubricating oil passages 76 are not provided in the rods 70a, 70a, the nozzle holes 63 and the lubricating oil passages 64 provided in the trunnions 7b, 7c are provided. The circular hole 56 provided at the upstream end of the above is provided on the opposite side to the case of the above-mentioned prior invention. That is, this circular hole 5
6 is a pivot 6 to which rods 70a, 70a, which are output members of the double-acting actuators 67a ', 67b', of both ends of the trunnions 7b, 7c are coupled,
The pivot shafts 6, 6 on the side opposite to 6 (upper side in FIG. 1) are opened at the end face central portions. Then, the oil supply connector terminals 77, 77 fixed to the inner surface of the casing 5a are connected to the trunnion 7 described above.
A circular hole 5 opened at the end faces of the pivots 6, 6 at the ends of b, 7c
Inserted loosely in 6, 56.

Each of the oil supply connector terminals 77, 77 has a circular tubular shape and is formed by bending the middle thereof. The portions of the oil supply connector terminals 77, 77 which are inserted into the circular holes 56, 56 at the front half of the refueling connector terminals 77, 77 with the trunnions 7b, 7c in the neutral position are provided with the pivot shafts 6, 6 respectively. And the circular hole 56,
Concentric with 56. However, the above trunnions 7b and 7c
Is slightly displaced (axial displacement and swing displacement in which the central axes do not coincide with each other) with respect to the above-mentioned oil supply connector terminals 77, 77 during operation of the toroidal type continuously variable transmission. The engaging portion between the outer peripheral surface of the first half of the above and the inner peripheral surface of each of the circular holes 56, 56 allows such displacement, and from the oil supply connector terminals 77, 77 to each of the circular holes 56. Lubricating oil can be fed freely into 56 and 56. For this reason, each of the oil supply connector terminals 7
The outer diameters of the first halves of 7, 77 are made slightly smaller than the inner diameters of the circular holes 56, 56, and the oil supply connector terminals 7 are provided.
The first halves of 7, 77 are loosely (slightly oscillatingly displaced) inserted into the circular holes 56, 56. Then, by the O-rings 78, 78, the respective oil supply connector terminals 77, 77
The gap between the outer peripheral surface of the first half of the above and each of the circular holes 56, 56 is closed.

In the oil supply connector terminals 77, 77 as described above, an oil supply passage 79 provided in the upper portion of the casing 5a is provided.
Lubrication oil can be fed freely through. During operation of the toroidal type continuously variable transmission, lubricating oil is fed into the respective oil supply connectors 77, 77 through the oil supply passage 79, and the lubricating oil is further supplied through the circular holes 56, 56 to the nozzle hole 63 and the lubricating oil. Rolling bearings, such as thrust ball bearings 14 and radial needle bearings, which are fed to the oil passage 64 and require lubrication with respect to the power rollers 9, 9, that is, the rotation supporting portions of the power rollers 9, 9. , Inner surfaces 2a, 4a of the peripheral surfaces 9a, 9a of the respective power rollers 9, 9 and the input side and output side disks 2, 4
(See FIG. 10) Lubricating oil is supplied to the rolling contact part.

In the illustrated example, the lower trunnion 7a
, A single-acting hydraulic actuator 50a, 50b for displacing the shaft 6 in the axial direction of the pivots 6, 6 provided at both ends thereof (the left-right direction in FIG. 1), a support beam 80 provided inside the lower portion of the casing 5a. Support. The pressure oil is supplied to and discharged from each of the hydraulic actuators 50a and 50b, and the supply and discharge flow paths 81 are provided in the casing 5a and the support beam 80.
It is designed to be performed via 81.

In the case of the toroidal type continuously variable transmission of the present invention configured as described above, the trunnion 7 which is displaced by each of the double-acting type actuators 67a 'and 67b'.
Nozzle hole 63 and lubricating oil flow path 6 provided inside b and 7c
4, the rods 70a, 70 of the actuators 67a ', 67b' are based on the structure for feeding the lubricating oil into
It is not necessary to increase the outer diameter of a. Therefore, even considering that the outputs of the actuators 67a ′ and 67b ′ are secured, the actuators 67a ′ and 6
7b 'can be downsized (smaller diameter). Further, since the labor for processing the lubricating oil flow path in each of the rods 70a, 70a is unnecessary, the cost can be reduced.

Further, unlike the structure of the previous invention, the above trunnions 7b and 7b can be provided without using a flexible oil supply hose.
Lubricating oil can be fed into the nozzle hole 63 and the lubricating oil passage 64 provided inside 7c, and sufficient durability can be secured without using an expensive material. Further, since the structure for feeding the lubricating oil to the trunnions 7b and 7c can be centrally arranged on the upper portion of the casing 5a,
It is easy to reduce the size and weight of the toroidal type continuously variable transmission as a whole. Furthermore, it is not necessary to connect the downstream end of the refueling hose to the end of the rod 70a having the precess cam 28 fixed at the end, and it is possible to prevent the outer size of the casing 5a that houses the toroidal type continuously variable transmission from increasing. As a result, the vehicle mountability can be improved.

Since the oil supply connector terminals 77, 77 and the trunnions 7b, 7c are assembled in the casing 5a in a state in which the lubricating oil can be delivered and received, the oil supply connectors are provided in the casing 5a. Prior to assembling the terminals 77, 77 and the trunnions 7b, 7c, the refueling connector terminals 77, 77 and the trunnions 7b, 7c are assembled in advance. Then, these refueling connector terminals 77, 77 and the trunnions 7b, which have been assembled (sub-assembled) in advance,
7c are incorporated in the casing 5a. Incidentally, the oil supply connectors 77, 77 for feeding the lubricating oil to the trunnions 7b, 7c may have a common mounting flange 82, 82 provided at the base end thereof so that they can be handled integrally. .

The above description has been given for the case where the present invention is applied to a structure in which three power rollers are provided for each of a pair of input side and output side disks. However, in the case of the invention described in claim 1, the present invention has a structure in which two power rollers are provided for each of a pair of input side and output side disks as shown in FIGS. It can also be applied. Also in the case of such a structure, as is apparent from FIG. 5, conventionally, the lubricating oil is fed into the lubricating oil passages 64, 64 in the trunnions 7, 7 from the actuator 17, 17 side. . This is the actuator 17, 17
By performing from the opposite side, it is possible to reduce the size and weight and cost by simplifying the oil supply passage.

[0058]

Since the present invention is constructed and operates as described above, it is possible to reduce the size and weight of the toroidal type continuously variable transmission and reduce the cost thereof, and contribute to the spread of the toroidal type continuously variable transmission. . Furthermore, in the case of the invention described in claim 2, in addition to the above effects, an automatic system incorporating a toroidal type continuously variable transmission that can transmit a large amount of power, is compact, and can be installed in a limited installation space. It is possible to facilitate the design of the transmission and ensure a stable speed change operation.

[Brief description of drawings]

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

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

FIG. 3 is a side view similarly showing a state at maximum acceleration.

FIG. 4 is a sectional view showing an example of a conventional specific structure.

5 is a cross-sectional view taken along the line AA of FIG.

FIG. 6 is a front view of an essential part showing an example of a conventionally known structure for increasing the power that can be transmitted, with a part thereof cut away.

FIG. 7 is a cross-sectional view of a main part showing a first example of a conventionally known structure capable of reducing the number of actuators.

FIG. 8 is a sectional view of an essential part showing the second example.

FIG. 9 is a sectional view showing an example of an embodiment of the prior invention.

10 is a sectional view taken along line BB of FIG.

FIG. 11 is an enlarged view of part C of FIG.

FIG. 12 is a cross-sectional view showing a double-acting hydraulic actuator taken out.

[Explanation of symbols]

1 Input Shaft 2 Input Side Disk 2a Inner Side Surface 3 Output Shaft 4 Output Side Disk 4a Inner Side Surface 5, 5a Casing 6 Pivots 7, 7a, 7b, 7c Trunnion 8 Displacement Shaft 9 Power Roller 9a Circumferential Surface 10 Loading Cam Device 11 Input Shaft 12 Output Gears 13, 13a Support Plate 14 Thrust Ball Bearing 15 Thrust Needle Bearing 16 Outer Ring 17 Actuator 18 Frames 19, 19a, 19b Support Piece 20 Hydraulic Cylinder 21 Control Valve 22 Pump 23 Sleeve 24 Spool 25 Control Motor 26 Drive Piston 27 Oil Sump 28 Precess cam 29 Link 30 Link mechanism 31 Mounting part 32 Mounting hole 33 Stud 34 Nut 35 Gear housing 36 Output sleeve 37 Rolling bearing 38 Output gear 39 Holding part 40 Second pivot 41 Needle bearing 42 Mounting part 43 Support plate part 44 Circular hole Four Radial needle bearing 46 Outer ring 47 Screw hole 48 Stud 49 Lock nuts 50a, 50b Hydraulic actuator 51a, 51b Link arm 52 Cylinder 53 Rod 54 Third pivot 55 Cylindrical convex portion 56 Circular hole 57 O-ring 58 Thrust needle bearing 59 Orbital ring 60 recessed groove 61 oil passage hole 62 plug 63 nozzle hole 64 lubricating oil passage 65 throttle plug 66 throttle plug 67a, 67b, 67a ', 67b' hydraulic actuator 68 cylinder 69 piston 70, 70a rod 71 flange 72 taper snap ring 73 Thrust needle bearing 74 Screw hole 75 Lock nut 76 Lubricating oil passage 77 Lubrication connector terminal 78 O-ring 79 Oil supply passage 80 Support beam 81 Supply / drain passage 82 Mounting flange

Claims (2)

[Claims] 1. A casing, an input shaft rotatably supported in the casing, an input side disk rotatably supported around the input shaft together with the input shaft, and an inner surface of the input side disk. Provided between the input side disc and the output side disc, which is arranged concentrically with the input side disc in a state of facing the inner surface of the disc and is rotatable relative to the input side disc. And a plurality of trunnions for each of the pair of input-side disks and output-side disks that swing about a pivot that is in a twisted position with respect to the center axes of these disks.
One displacement axis for each of these trunnions protruding from the inner side surface of each of these trunnions, and a state of being rotatably supported via rolling bearings around each of these displacement axes on the inner side surface of each of these trunnions. , One power roller for each trunnion sandwiched between the inner side surfaces of the input side disc and the output side disc, and the axial direction of the pivot provided with each of the trunnions at both ends thereof. To a toroidal-type continuously variable transmission including an actuator for displacing the power roller and a lubricating oil passage provided inside each of the trunnions in order to supply lubricating oil to a portion of the power roller that requires lubrication. An actuator for displacing at least a part of the plurality of trunnions for each of the pair of input side disks and output side disks. A double-acting hydraulic actuator provided for each trunnion on the extension of the pivot axis for the trunnion, and a lubricating oil passage provided inside the trunnion displaced by the double-acting hydraulic actuator. The upstream end opening of the toroidal type continuously variable transmission is characterized in that it is provided at the center of the end face of the pivot shaft opposite to the pivot shaft to which the output members of these double-acting hydraulic actuators are coupled. 2. A casing, an input shaft rotatably supported in the casing, an input side disk rotatably supported around the input shaft together with the input shaft, and an inner surface of the input side disk. Provided between the input side disc and the output side disc, which is arranged concentrically with the input side disc in a state of facing the inner surface of the disc and is rotatable relative to the input side disc. 3 trunnions for each pair of the input side disc and the output side disc that swing around a pivot that is in a twisted position with respect to the central axes of these discs, and project from the inner surface of each of these trunnions. In addition, one displacement shaft is provided for each of the trunnions, and the inner surface of each trunnion is rotatably supported around each of these displacement shafts via rolling bearings. In this state, one power roller for each trunnion sandwiched between the inner side surfaces of the input side disc and the output side disc, and a pivot shaft provided with these trunnions at both ends thereof. A toroidal type continuously variable transmission equipped with an actuator for axial displacement and a lubricating oil passage provided inside each trunnion for supplying lubricating oil to a portion of each power roller that requires lubrication. In the machine, an actuator for displacing a part of the three trunnions provided for each of the pair of the input side disc and the output side disc is connected via the link arm. A pair of single-acting hydraulic actuators for displacing the trunnions in opposite directions, and the actuators for displacing the remaining trunnions are the remaining trunnions. Is a double-acting hydraulic actuator provided for each of the remaining trunnions on the extension of the pivot axis related to the engine, and a lubricating oil passage provided inside the trunnion that is displaced by these double-acting hydraulic actuators. The upstream end opening of the toroidal type continuously variable transmission is characterized in that it is provided at the center of the end face of the pivot shaft opposite to the pivot shaft to which the output members of these double-acting hydraulic actuators are coupled.