JP3285626B2 - Toroidal type continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a toroidal type continuously variable transmission, and more particularly, to a structure for arranging an oil passage when the continuously variable transmission is performed by hydraulic control.

[0002]

2. Description of the Related Art Conventionally, as a toroidal type continuously variable transmission, for example, as disclosed in Japanese Patent Application Laid-Open No. 62-251559, an input disk and an output disk having a toroidal surface and a toroidal surface between the two disks have been disclosed. A toroidal-type continuously variable transmission unit having a plurality of tiltable rollers disposed at a position between the input disk and the output disk via the rollers while transmitting power from the input disk to the output disk. It is known that the ratio can be adjusted steplessly.

In the above-described conventional toroidal-type continuously variable transmission, as disclosed in, for example, Japanese Patent Application Laid-Open No. 2-163567, hydraulic control is used to control the inclination angle of a plurality of rollers, and the hydraulic control is performed. Is provided with a plurality of pistons for tilting a plurality of rollers, respectively, and one hydraulic control valve for supplying a control oil pressure to a hydraulic oil chamber of each piston.

[0004]

However, when a plurality of rollers of a toroidal type continuously variable transmission are controlled to be tilted by hydraulic control as in the above-mentioned conventional art, oil is supplied from a hydraulic control valve to hydraulic oil chambers of a plurality of pistons. When the paths are branched and communicated, the branch of the oil path to the hydraulic oil chamber of each piston is generally performed using a mating surface of a valve body divided into two parts. Since there are both a shift-up side oil chamber that raises the gear ratio and a shift-down side oil chamber that lowers the gear ratio, the oil passage is connected to the system for the shift-up oil chamber and to the shift-down oil chamber. Therefore, it is necessary to distinguish the oil passage into two systems by only one mating surface of the valve body, and to branch the oil passage into the hydraulic oil chambers of a plurality of pistons for each system. It is difficult to do.

[0005] The present invention has been made in view of the above-mentioned point, and an object of the present invention is to provide a toroidal-type continuously variable transmission as described above, in which when a plurality of rollers are tilt-controlled by hydraulic control, each piston is controlled. Another object of the present invention is to provide a configuration in which branching of an oil passage to a hydraulic oil chamber can be easily performed.

[0006]

To achieve the above object, according to an aspect of, the present invention, divided into three valve body, configured to performing branching arrangement of the oil passage with the two mating surfaces.

That is, a specific solution of the present invention is directed to a toroidal-type continuously variable transmission including an input disk, an output disk, and a roller that is disposed between the two disks and that can tilt freely. A hydraulic control mechanism for adjusting the inclination angle of the roller, a hydraulic control valve, a plurality of pistons to which the control hydraulic pressure of the hydraulic control valve is supplied, and a shift-up side for moving each piston for each piston. An oil chamber and a downshift-side oil chamber are provided. The valve body of the hydraulic pressure adjusting mechanism includes a lower valve body provided with the hydraulic control valve, and an upper valve body provided with the plurality of pistons and a plurality of shift-up side oil chambers and a shift-down side oil chamber. A shift-up oil which is constituted by a middle valve body disposed between the two valve bodies and connects the hydraulic control valve and a plurality of shift-up oil chambers to the valve body of the hydraulic adjustment mechanism. A downshift-side oil passage connecting the hydraulic control valve and the plurality of downshift-side oil chambers; The upshift-side oil passage is distributed to each upshift-side oil chamber at one of a mating surface between the lower valve body and the middle valve body and a mating surface between the middle valve body and the upper valve body. The shift-down side oil passage is branched so as to be distributed to each shift-down side oil chamber on the other mating surface.

According to a second aspect of the present invention, the configuration according to the first aspect of the present invention is specified, and when a predetermined opening which hinders formation of an oil passage is formed in the upper valve body, The shift-up side oil passage is branched at the mating surface between the lower valve body and the middle valve body, and the shift-down side oil passage is branched at the mating surface between the middle valve body and the upper valve body.

Further, according to the invention described in claim 3, according to claim 1 of the present invention,
The configuration of the described invention is limited to another, the upshift-side oil passage is branched at the mating surface of the middle valve body and the upper valve body, and the downshift-side oil passage is connected to the lower valve body and the middle valve body. Are branched at the mating surface of.

[0010]

According to the above-mentioned structure, according to the first aspect of the present invention,
The branch of the oil passage to the plurality of up-shift-side oil chambers and the branch of the oil passage to the plurality of down-shift-side oil chambers are performed at each of the two mating surfaces of the valve body. Arrangement
Installation can be done easily.

In the case where an opening is formed in the upper valve body, in the oil passage branched at the upper mating surface, the passage lengths reaching the respective oil chambers are unequal due to the presence of the opening. Accordingly, the hydraulic pressure values acting on the respective oil chambers also vary among them, and the variation width increases as the hydraulic pressure increases. However, according to the second aspect of the present invention, the oil passage branched at the upper mating surface is specified as the downshift-side oil passage which is less affected by the unequal length of the branch oil passage, and the passage lengths are easily equalized. Since the shift-up side oil passage is branched at the lower mating surface, the variation of the hydraulic pressure acting between both the shift-down side oil chambers and the shift-up side oil chambers can be suppressed to be small. .

Further, according to the third aspect of the invention, in a normal case where no opening or the like is formed in the upper valve body, the shift-up side oil passage branches off at the upper mating surface. The oil path length of the shift-up oil path is ensured to be long, and the oil path length of the branch shift-up oil path in the upper valve body is restricted to be short, so that the oil pressure between the shift-up oil chambers is equalized. Secured.

[0013]

As described above, according to the toroidal type continuously variable transmission according to the first aspect of the present invention, the valve body is constituted by three stages, and a plurality of pistons are formed by using the two mating surfaces. since the oil passages branched disposed separately to the shift-up side oil chamber and the downshift side oil chamber, the arrangement of the oil passages can be easily performed.

Further, according to the second aspect of the present invention, there is a case where unequal lengths are generated in a plurality of branch oil passages in the upper valve body due to the presence of the opening formed in the upper valve body. In addition, since the shift-up side oil passage is branched at the lower mating surface, an effect that the difference in hydraulic pressure between the shift-up side oil chambers and the shift-down side oil chambers can be suppressed to be small can be obtained.

Further, according to the third aspect of the present invention, the shift-up side oil passage is branched at the lower mating surface.
Limit the oil path length of multiple branch shift-up oil paths to short,
Variations between the hydraulic pressures of the plurality of shift-up oil chambers can be reduced.

[0016]

Embodiments of the present invention will be described below with reference to the drawings.

FIGS. 1 and 2 show a toroidal-type continuously variable transmission according to the present invention, wherein 1 is an output shaft, 2 is a first toroidal-type continuously variable transmission unit disposed on the output shaft 1, Is a second toroidal-type continuously variable transmission unit arranged on the right side of the first continuously variable transmission unit in FIG.

The first toroidal type continuously variable transmission unit 2 includes an input disk 5 rotatably supported on an output shaft 1.
And an output disk 6 disposed opposite to the input disk 5 on the left side in FIG. 1. The output disk 6 is spline-coupled to the output shaft 1. Between the two disks 5, 6, two power rollers 7,, which straddle and contact two toroidal surfaces 5a, 6a formed by the two disks 5, 6, respectively.
7 are arranged.

Similarly, the second toroidal-type continuously variable transmission unit 3 includes an input disk 9 similar to the above, an output disk 10 disposed on the right side of the input disk 9 in FIG. 10 two toroidal surfaces 9a, 10a
And two power rollers 11 in contact with each other. The input disk 9 is arranged such that the rear surface thereof faces the rear surface of the input disk 5 of the first continuously variable transmission unit 2, that is, the side surface opposite to the toroidal surface 5a with which the power roller 7 abuts. The pair of input disks 5, 9 are located inside and the pair of output disks 6, 10 are located outside. An intermediate disk 15 is arranged in a space formed between the back surfaces of the pair of input disks 5 and 9, and an output is provided between the intermediate disk 15 and the input disks 5 and 9, respectively. A plurality of loading cams 16 are arranged in the circumferential direction of the shaft 1. A power transmission gear 1 composed of a helical gear for transmitting power to the pair of input disks 5 and 9 is provided on the outer periphery of the intermediate disk 15.
An engine power is transmitted to the power transmission gear 18 from an input shaft (not shown). On the other hand, the intermediate disk 15 and the input disks 5, 9 each have a cam groove formed on a side surface facing each of the loading cams 16. When the intermediate disk 15 and the input disks 5 and 9 rotate relative to each other, the larger the relative displacement, the more the loading cams 16.
9 is formed in a shape that increases the pressing force. Therefore, the engine power is sequentially transmitted from the power transmission gear 18 and the intermediate disk 15 to the loading disks 16, the input disks 5 and 9, the power rollers 7 and 11, and the output disks 6 and 9.
After being transmitted to 10, it is transmitted to the output shaft 1.

The pair of input disks 5 and 9 have inner diameter portions whose rear sides extend toward both sides thereof.
8 and are connected so as to be integrally rotatable. The intermediate disk 15 is radially divided into two parts, and a disc spring 19 for urging the input disks 5 and 9 apart from each other is disposed between the two. Between disk 6 and input disk 5
And a pressurizing force for generating a predetermined pressing force when no load is applied between the motor and the output disk 6.

On the other hand, the output disk 6 of the first toroidal type continuously variable transmission unit 2 is positioned in the axial direction of the output shaft 1 by a positioning member 94 via a hollow cylindrical member 93. On the other hand, the output disk 10 of the second toroidal type continuously variable transmission unit 3 is rotatably supported by the transmission casing 25 via the bearing 95. A nut member 96 is screwed to the output shaft 1 in a state in which the nut member 96 is in contact with the side surface of the bearing 95. By tightening the nut member 96, the output disk of the first toroidal type continuously variable transmission unit 2 is output together with the output shaft 1. 6 is moved in the axial direction, and a pair of input disks 5,
The configuration is such that the pressing force of the disc spring 19 between the input discs 9 and the input discs 5 and 9 is adjusted.

Each of the toroidal type continuously variable transmission units 2
3, the power rollers 7 and 11 are eccentric shafts 20 and 2 respectively.
0, a pair of trunnions 21 and 2 arranged vertically
1 is rotatably mounted. Each trunnion 21
A shaft member 22 disposed in the vertical direction is fixedly disposed at the lower end of the power roller 7. By displacing the shaft member 22 in the vertical direction, the trunnion 21 is displaced in the vertical direction, and the power rollers 7, 11 are displaced. By tilting, the contact points at which the power rollers 7, 11 come into contact with the input / output disks 5, 6, 9, 10 are changed to change the speed ratio steplessly. The upper end of each of the trunnions 21 is supported by a support member 27 attached to a transmission casing 25 by a link post 26 so as to allow spherical rotation of each of the trunnions 21 so as to allow the power rollers 7 and 11 to rotate around the axis. The lower end portion is rotatably supported by a spherical bearing 33 by a support member 32 attached to a partition wall 30 by a link post 31 while being rotatably supported in the axial direction by 28.

Below the shaft members 22, 22, a hydraulic adjustment mechanism 35 for adjusting the inclination angle of the power rollers 7, 11 is provided.
Is arranged.

The hydraulic adjustment mechanism 35 is connected to a substantially central position of each shaft member 22 to move the respective shaft members 22 up and down, and to hydraulic chambers 49 and 50 of the respective hydraulic cylinders 45. And a shift control device 60 that controls the supply of hydraulic oil to perform a shift. The hydraulic cylinder 4
5 is a state in which an upper valve body 47 attached and fixed to the transmission casing 25 with bolts 46 and a projecting portion 47b projecting inward from a cylindrical piston chamber 47a formed in the upper valve body 47 are vertically sandwiched. Pistons 48, 48 whose center portions are fitted and fixed to the shaft member 22 are provided. A pair of hydraulic chambers 49 and 50 are formed vertically by the piston 48 and the protruding portion 47a of the upper valve body 47, and the rotation direction is opposite between the pair of power rollers 7 and 7 and between 11 and 11. Accordingly, the upper hydraulic chamber 49 on the left side of FIG. 2 and the lower hydraulic chamber 49 on the right side of FIG. 2 constitute a shift-up side oil chamber, and the lower hydraulic chamber 50 on the left side of FIG. The shift-down-side oil chamber is constituted by the upper-side hydraulic chamber 50. The shaft member 22 is moved up and down by supply of oil pressure to the shift-up-side oil chamber 49 to reduce the gear ratio. The gear ratio is increased by moving the shaft member 22 by supplying hydraulic pressure to the downshift-side oil chamber 50. As shown in FIG. 2, the shaft member 22 is rotatably and vertically movable supported by bearings 41 in recesses 40 of the middle and lower valve bodies 37, 38 disposed below the partition wall 30, as shown in FIG. Have been.

The transmission control device 60 includes a line pressure supply oil passage 61 for supplying a line pressure from a hydraulic source (not shown) to the middle valve body 37, and a shift-up side of each of the hydraulic cylinders 45. An upshift-side oil passage 62 and a downshift-side oil passage 63 communicating with the oil chamber 49 and the downshift-side oil chamber 50 are formed. A hydraulic control valve 65 is disposed in the lower valve body 38. The control valve 65 includes a sleeve 67 slidably disposed in the valve body 66, and a sleeve 67 slidably disposed in the valve body 66. And a spool 68 that is slidably disposed on the spool 68. The sleeve 67 has a line pressure port 67 corresponding to the line pressure supply oil passage 61, the shift-up oil passage 62, and the shift-down oil passage 63.
a, a shift-up side port 67b, and a shift-down side port 67c are formed, and the oil in the line pressure supply oil passage 61 flows from the line pressure port 67a through the concave portion of the spool 68 in accordance with the movement of the sleeve 67, and then the shift-up side port 67b. 6
7b to the shift-up-side oil passage 62 or the spool 6
After passing through the recessed portion of No. 8, it is configured to communicate with the downshift-side oil passage 63 through the downshift-side port 67c.

In the vicinity of the left end of the sleeve 67 in FIG.
A pin member 70 is connected to the pin member 70, and a rotation shaft 72 a of a stepping motor 72 mounted on a vertical wall portion of an oil pan 79 disposed below the transmission casing 25 via a driving member 71 disposed in a sleeve 67. The sleeve 67 is slid in the left-right direction in FIG. 2 according to the rotation of the motor 72.

Further, the transmission control device 60 is provided with a feedback mechanism 80 which is disposed at the right end of the spool 68 in FIG. 2 and feeds back the tilting of a predetermined (right side in FIG. 2) power roller 7. The feedback mechanism 80
A precess cam 81 fixedly arranged on the shaft member 22 of the trunnion 21 on the right side of FIG. 2, a first arm 82 whose tip engages with an inclined surface 81a formed on the precess cam 81, and the first arm 82 A supported rotating shaft 83,
The hydraulic control valve 6 is rotatably supported by the rotary shaft
5 is engaged with the right end of FIG.
And a compression coil spring 85 contracted between the left side of the spool 68 in FIG. 2 and the pin member 70. The oil supply to the hydraulic cylinder 45 according to the movement of the sleeve 67 causes the shaft member 22 to move Power roller 7
Is tilted, the first and second arms 82 and 84 of the feedback mechanism 80 rotate clockwise or counterclockwise in accordance with the vertical movement of the shaft member 22, and the spool 68 moves in the same direction as the sleeve 67. By doing so, the supply oil passage 6
The oil supply to the hydraulic cylinder 45 is stopped when the tilting position of the power roller 7 reaches the target position by cutting off the communication between the power roller 1 and the first or second oil passages 62 and 63 communicating therewith. Make up.

Next, the arrangement of oil passages formed in the upper valve body 47 and the middle valve body 37 as a feature of the present invention.
Will be described. As shown in FIG.
7, a line pressure oil passage 100 communicating with the line pressure supply oil passage 61 of the lower valve body 38 is formed in the vicinity of the center portion. The oil passage 100 extends upward in FIG. The oil passage 101 is supplied with line pressure from an oil pump (not shown).

Further, on the lower surface of the middle valve body 37,
An upshift-side oil passage 62b communicating with the upshift-side oil passage 62 of the lower valve body 38 is formed.
b is an oil passage 62 extending in a direction orthogonal to the oil passage 62b.
and branches into four oil passages 62d1 to 62d4 that rise upward at positions near the four pistons 48.
The shift-up side oil passage 62d2 is used to adjust the distance between the pair of input disks 5 and 9 when adjusting the distance between the pair of input disks 5 and 9.
Due to the presence of the measurement opening 102 provided for measuring the interval between the input disks 5 and 9 of FIG.

In addition, a shift-down side oil passage 63b is formed on the lower surface of the middle valve body 37 and communicates with the shift-down side oil passage 63 of the lower valve body 38 and extends in the lateral direction. Oil passage 63c extending vertically
Are in communication.

On the other hand, as shown in FIG. 4, the upper valve body 47 communicates with the shift-up oil passages 62d1 to 62d4 branched from the middle valve body 37 into four shift-up oil passages which rise vertically. Roads 62e1-62e4
Is formed, and in the oil passage 62e2 at a position separated from the piston chamber 47a of the corresponding piston 48,
An oil passage 62f extending laterally near the piston chamber 47a.
And an oil passage 62 communicating with the oil passage 62f and extending vertically.
g is formed.

Further, on the lower surface of the upper valve body 47,
An oil passage 63d communicating with the downshift-side oil passage 63c formed in the middle valve body 37 is formed. The shift-down side oil passage 63d is provided at a distance between the pair of disks 5 and 9 .
When performing the adjustment, the distance between the pair of input disks 5 and 9 is
Since the measurement opening 103 provided for measurement interferes with the formation of the oil passage, the measurement opening 103 bypasses the opening 103 and the opening 10
Along the periphery of 3, it extends laterally in a U-shape. The U
Each of the four piston chambers 47a...
The oil passages 63e1 to 63e4, which rise at neighboring positions, communicate with each other.

As shown in FIG. 5, the upshift-side oil passage 62g of the upper valve body 47 communicates with an oil passage 62h extending obliquely upward and communicating with the upshift-side oil chamber 49, as shown in FIG. On the other hand, the downshift-side oil passage 6
As shown in FIG. 6, 3e2 extends obliquely downward, for example, and communicates with an oil passage 63f communicating with the shift-down side oil chamber 50. In FIG. 3, reference numeral 105 denotes a return oil passage for returning oil to the oil pump, reference numeral 106 in FIG. 4 denotes a line pressure oil passage communicating with the line pressure oil passage 101 in FIG. 3, and reference numeral 107 denotes a communication with the return oil passage 105. It is an oilway.

Therefore, in the above embodiment, the valve body of the hydraulic pressure adjusting mechanism 35 is constituted by the three valve bodies 48, 37, and 38 of the upper, middle and lower stages, and has two mating surfaces. The shift-up-side oil passage 62 branches into four oil passages 62d1 to 62d4 at the lower mating surface formed by the body 37 and the lower valve body 38,
At the mating surface of the middle valve body 37 and the upper valve body 47 constituting the upper mating surface, the shift-down side oil passage 6
Because 3 is 4 branches to the oil passage 63E1～62e4, compared with the case of performing disposed in respective fluid passages in the conventional one mating surface as in both systems the upshift side and the shift-down side, the oil passages Can be easily arranged .

Moreover, the common oil passages 62b, 63c before branching
Is disposed at a substantially central portion of the middle valve body 37, so that the lengths of the oil passages to the corresponding shift-up side oil chamber 49 and shift-down side oil chamber 50 can be shortened and substantially evenly arranged .

Further, when adjusting the distance between the pair of input disks 5 and 9, the upper valve body 47 is provided with the pair of input disks 5 and 9 .
Although a measurement opening 103 for measuring the interval between the input disks 5 and 9 is provided, and the oil passage 63d bypasses the opening 103, the oil passage length to each piston 48 becomes unequal. The oil passage 63d is a shift-down oil passage whose oil pressure value is sufficiently lower than the oil pressure of the shift-up oil passage 62c. Shift-side oil chambers 50... Can reduce variations in hydraulic pressure among each other.

FIGS. 7 and 8 show an embodiment of the third aspect of the present invention. In the above embodiment, the shift-down-side oil passage is branched into four at the upper mating surface in response to the presence of the measurement opening 103. Then, in place of branching the shift-up side oil passage at the lower mating surface and not having such a measurement opening 103 ,
The arrangement of the oil passage is reverse to that described above.

That is, the upshift-side oil passage 62 of the above embodiment is a downshift-side oil passage 63 'and the downshift-side oil passage 63 is an upshift-side oil passage 62'. ''. In this embodiment, although not shown, the shift-up side oil passage 62 and the shift-down side oil passage 63 formed in the lower valve body 38 in FIG.
The positions of the oil passages 62h and 63f to the shift-up side oil chamber 49 and the shift-down side oil chamber 50 in FIGS. In the opposite direction.

7 and 8, FIGS. 3 and 4
Along with not provided with a measuring opening 102 and 103, in FIG. 7, the common shift-up side oil passage extending vertically in the middle valve body 37 '62C' is located in the central part of the range surrounded by four pistons 48 In addition, in FIG. 8, a branch shift-up side oil passage 62d 'in four directions is formed on the lower surface of the upper valve body 47', and the oil passage 62d 'is provided at the center thereof at the shift-up side oil passage 62c. 'The upper end is formed in the shape of a plane H with an opening, and the oil passage lengths reaching the respective upshift-side oil chambers 49 are made uniform. On the other hand, on the lower surface of the middle-stage valve body 37 'in FIG. 7, the common shift-down-side oil passage 63b' branches in four directions to form a planar H-shaped branched shift-down-side oil passage 63c '.
In the upper valve body 47 ′, the branch oil passage 63c ′
Are formed at positions equidistant from the corresponding piston working chamber 47a.

Therefore, in this embodiment, the common upshift-side oil passage 62c 'has a long oil passage length formed up to the upper mating surface of the lower surface of the upper valve body 48'. ... can be maintained substantially equally to each other. Moreover, the upper valve body 47
′, The branch shift-up side oil passage 62d ′ is formed in an H shape so that the oil passage length to each of the piston working chambers 47a is equal, so that each shift is performed while ensuring a short oil passage length. Equalization of the hydraulic pressure of the up-side oil chambers 49 can be further enhanced.

[Brief description of the drawings]

FIG. 1 is a sectional view of a toroidal type continuously variable transmission as viewed from a side.

FIG. 2 is a sectional view taken along line AA of FIG.

FIG. 3 is a bottom view of the middle valve body.

FIG. 4 is a bottom view of the upper valve body.

FIG. 5 shows a diagram of an upshift-side oil passage to an upshift-side oil chamber.
It is sectional drawing which shows arrangement | positioning .

FIG. 6 shows a shift-down-side oil passage to a shift-down-side oil chamber;
It is sectional drawing which shows arrangement | positioning .

FIG. 7 is a bottom view of the middle valve body showing the embodiment of the third aspect of the present invention.

FIG. 8 is a bottom view of the upper valve body showing the embodiment.

[Explanation of symbols]

 2,3 Toroidal-type continuously variable transmission unit 5,9 Input disk 6,10 Output disk 7,11 Power roller (roller) 35 Hydraulic adjustment mechanism 37 Lower valve body 38 Middle valve body 45 Hydraulic cylinder 47 Upper valve body 48 Piston 49 Shift Up-side oil chamber 50 Shift-down side oil chamber 62 Shift-up side oil path 63 Shift-down side oil path 65 Hydraulic control valve 103 Measurement opening (opening)

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F16H 15/38 F16H 61/00

Claims (3)

(57) [Claims] In a toroidal-type continuously variable transmission including an input disk, an output disk, and a roller that is disposed between the two disks and that can freely tilt, a hydraulic adjustment mechanism that adjusts the angle of inclination of the roller is a hydraulic pressure adjusting mechanism. A control valve, a plurality of pistons to which a control oil pressure of the hydraulic control valve is supplied, a shift-up side oil chamber and a shift-down side oil chamber for moving each piston for each piston, and the hydraulic adjustment mechanism. A lower valve body provided with the hydraulic control valve, an upper valve body provided with the plurality of pistons and a plurality of shift-up side oil chambers and a shift-down side oil chamber, The hydraulic control valve and a plurality of shift-up side oil chambers are connected to the valve body of the hydraulic adjustment mechanism. A downshift-side oil passage that connects the hydraulic control valve and the plurality of downshift-side oil chambers is formed, and the upshift-side oil passage includes a lower valve body and a middle valve body. And one of the mating surfaces of the middle valve body and the upper valve body is branched so as to be distributed to each shift-up side oil chamber, and the shift-down side oil passage is connected to the other mating surface. A toroidal type continuously variable transmission characterized by branching so as to be distributed to each downshift side oil chamber. 2. In a toroidal type continuously variable transmission in which a predetermined opening obstructing formation of an oil passage is formed in an upper valve body, an upshift-side oil passage is provided between the lower valve body and the middle valve body. The toroidal-type continuously variable transmission according to claim 1, wherein the transmission branches at a mating surface, and the downshift-side oil passage branches at a mating surface between the middle valve body and the upper valve body. 3. The shift-up side oil passage branches at a mating surface between the middle valve body and the upper valve body, and the shift-down side oil passage branches at a mating surface between the lower valve body and the middle valve body. The toroidal-type continuously variable transmission according to claim 1, wherein: