JP3473061B2 - 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 a toroidal type continuously variable transmission.

[0002]

2. Description of the Related Art Recently, it has been attempted to employ a toroidal type continuously variable transmission as disclosed in Japanese Unexamined Patent Publication No. 1-206149 as a continuously variable transmission for automobiles. In this toroidal type continuously variable transmission, an input disk having a curved conical friction surface and an output disk are coaxially arranged with the friction surfaces facing each other, and between the input disk and the output disk. , A toroidal type stepless device provided with a power roller in contact with each of these friction surfaces at the same time, and transmitting power from the input disk side to the output disk side at a gear ratio corresponding to the tilt angle of the power roller. It is configured to include a speed change mechanism. The gear ratio is determined by moving a roller support member supporting the power roller up and down by a hydraulic actuator to change the tilt angle of the power roller. In that case, it is also disclosed in the above-mentioned known examples. As described above, it is customary to arrange the hydraulic actuator below the toroidal type continuously variable transmission in view of layout or a demand for compactness.
A valve body incorporating a valve mechanism for controlling the operation of the hydraulic actuator is also arranged below the toroidal type continuously variable transmission mechanism.

[0003]

By the way, since the toroidal type continuously variable transmission mechanism uses the oil shearing force at the contact portion between the friction surface of each disk and the power roller to transmit torque, a relatively large amount is required. Lubrication oil is required, and this oil is returned to the oil pan side after lubricating the toroidal type continuously variable transmission part or various gear meshing parts, and is supplied again to the lubricated part by the oil pump. However, in this case, since the valve body is arranged at an intermediate position between the toroidal type continuously variable transmission mechanism and the oil pan, and the amount of oil itself is large as described above, the return oil is present on the upper surface side of the valve body. It becomes easy to collect.

However, when the return oil collects on the upper surface side of the valve body in this way, each disk, especially the maximum diameter part thereof, is immersed in the return oil, and the power loss increases due to oil agitation resistance, and the power of the toroidal type continuously variable transmission mechanism increases. This will significantly reduce the transmission efficiency.

As a countermeasure against such a case, for example, it is conceivable to penetrate the space between the lower position of the toroidal type continuously variable transmission mechanism and the oil pan with a large area. When the vehicle starts / stops or climbs a hill, the oil level in the oil pan temporarily tilts greatly, which may cause the disc to soak in the oil on the oil level rising side and increase stirring resistance. On the side where the surface is lowered, the oil strainer tends to come out on the oil surface and trap air, which may lead to poor control of the hydraulic system or damage to the sliding part due to lack of lubricating oil. The optimal method is hard to say.

Therefore, the present invention has its main purpose to surely prevent a decrease in power transmission efficiency due to immersion of a disk of a toroidal type continuously variable transmission mechanism in return oil.

[0007]

As a concrete means for solving the above problems in the present invention, in the invention according to claim 1, the input disk and the output disk having the curved conical friction surfaces are provided with the friction surfaces. Power rollers which are arranged coaxially with each other facing each other, and which simultaneously contact the friction surfaces of the respective discs between the input disc and the output disc to transmit power from the input disc to the output disc side. was placed through a roller support member, a hydraulic actuator to the roller supporting member - the motor of the power roller gyration
A toroidal-type continuously variable transmission mechanism is provided in which the gear ratio is variable by moving the tilt angle of the power roller in the vertical direction, which is the axial direction, and at the lower position of the toroidal-type continuously variable transmission mechanism. A valve body with a built-in control valve mechanism that controls the operation of the actuator
In a toroidal type continuously variable transmission in which the toroidal type continuously variable transmission mechanism and an oil pan are arranged so as to be vertically separated from each other, a toroidal type continuously variable transmission is provided at a position corresponding to a maximum diameter portion of each disk of the valve body. An oil return hole for the oil that flows back from the continuously variable transmission side to the oil pan side is formed.

According to a second aspect of the present invention, in the toroidal type continuously variable transmission according to the first aspect, the valve body is composed of a plurality of body members that are vertically stacked, and the oil return hole is provided. It is characterized in that the portions corresponding to the respective body members are sequentially offset in the lateral direction.

According to the invention of claim 3, claim 1 or 2
In the toroidal type continuously variable transmission described above, a plurality of the toroidal type continuously variable transmission mechanisms are arranged side by side in the axial direction and the roller supporting members are connected to each other by a connecting member, and the discs of the connecting member are connected to each other. It is characterized in that the cross-sectional shape of the corresponding portion is an inclined surface that can guide the scattered oil scattered by the rotation of each disk in the direction away from each disk.

[0010]

With each of the inventions of the present application, the following effects can be obtained by adopting such a configuration.

According to the first aspect of the invention, the oil return hole is formed in the valve body at a position corresponding to the maximum diameter portion closest to the valve body in each disk of the toroidal type continuously variable transmission mechanism. Even if a large amount of return oil collects on the upper surface side of the valve body, the oil return hole portion, that is, the portion corresponding to the maximum diameter portion of the disc, is affected by the oil flowing down from the oil return hole. Since the height of the oil surface is low, the maximum diameter portion of the disk is not immersed in the return oil.

Further, since it is sufficient to reduce the stirring resistance as long as it is possible to secure the return oil dischargeability at the position corresponding to the maximum diameter portion of the disk, the oil return hole corresponds to the maximum diameter portion of the disk. As long as it is a size that can cover only a limited range,
Therefore, it is possible to reduce the area of the oil return hole.

According to the second aspect of the invention, in addition to the effect of the first aspect, the oil return hole is laterally offset for each of the plurality of body members that are vertically stacked. Therefore, for example, compared with the case where the oil return hole penetrates straight in the vertical direction, the flow resistance at the time of oil reverse flow from the oil pan side to the toroidal type continuously variable transmission side is large, and that much The oil level inclination and the oil level fall in the oil pan during sudden acceleration / deceleration of the vehicle are suppressed.

According to the third aspect of the present invention, in addition to the effect of the first or second aspect, the scattered oil scattered around the rotational direction by the rotation of each disk is caused by the inclined surface of the connecting member. Since the scattered oil is guided in the direction away from the disk, it is possible to suppress the splashed oil from colliding with the inner wall of the casing, rebounding, and contacting the disk again.

[0015]

Therefore, according to the toroidal type continuously variable transmission of each invention of the present application, the following effects can be obtained.

(A) The toroidal type continuously variable transmission according to claim 1 has a simple structure in which the oil return hole is locally provided at a position corresponding to the maximum diameter portion of the disc of the valve body. By lowering the oil level of the part corresponding to the maximum diameter part of the disc to prevent the maximum diameter part of the disc from being immersed in the return oil, it is possible to reduce the power loss of the toroidal type continuously variable transmission mechanism due to stirring resistance. It can be reduced to a high power transmission efficiency,
By reducing the area of the oil return hole, it is possible to effectively prevent the occurrence of problems such as insufficient lubrication due to air spillage in the oil by suppressing the oil surface inclination during sudden acceleration / deceleration. It is what is done.

(B) According to the toroidal type continuously variable transmission of the second aspect, in addition to the effect of the above-mentioned (a), the oil return holes are laterally arranged for each of a plurality of vertically stacked body members. By offsetting in the direction, it is possible to suppress the oil level tilt and oil level drop in the oil pan during sudden acceleration / deceleration of the vehicle, etc., which may result from poor control of the hydraulic system due to air intake into the oil or lack of lubricating oil. The sliding portion can be reliably prevented from being damaged, and the operational reliability can be further enhanced.

(C) According to the toroidal type continuously variable transmission of the third aspect, in addition to the effect of the above (a) or (b),
By guiding the scattered oil scattered around the rotation direction by the rotation of each disk in the direction away from each disk by the inclined surface of the connecting member, the re-contact of the scattered oil with the disk is suppressed, so that the speed of An increase in stirring resistance of the disc due to the slow re-contact oil is prevented as much as possible, and the power transmission efficiency is further enhanced due to the reduction in power loss in the disc.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be specifically described below with reference to the accompanying drawings. FIGS. 1 and 2 show a toroidal type continuously variable transmission Z according to an embodiment of the present invention. This toroidal type continuously variable transmission Z includes a first toroidal type continuously variable transmission mechanism 4 and a second toroidal type transmission 4 which will be described later on the output shaft 3 which is arranged so as to penetrate through the front and rear end walls 1a and 1b of the casing 1. The continuously variable transmission mechanism 5 is arranged. In the drawings, reference numeral 2 is an oil pan.

Here, since each of the toroidal type continuously variable transmission mechanisms 4 and 5 has a conventionally known basic structure,
The specific structure thereof will be briefly described, and the first toroidal type continuously variable transmission mechanism 4 and the second toroidal type continuously variable transmission mechanism 5 have exactly the same configuration. The 1 toroidal type continuously variable transmission mechanism 4 will be described as an example, and this will be referred to as the description of the second toroidal type continuously variable transmission mechanism 5. However, for the sake of convenience of the following description, the reference numerals assigned to the respective constituent members of the first toroidal type continuously variable transmission mechanism 4 and the second toroidal type continuously variable transmission mechanism 5 are different from each other only for the input disc and the output disc described later. However, the other members are denoted by the same reference numerals.

The first toroidal type continuously variable transmission mechanism 4 has an input disk 11 having a curved conical friction surface loosely fitted to the output shaft 3 and a curved conical friction surface similar to the input disk 11. The output disc 12 spline-coupled to the output shaft 5 and the friction faces of these two discs 11 and 12 simultaneously contact and rotate to rotate the input disc 11.
Is provided with a pair of left and right power rollers 13, 13 for transmitting the torque to the output disk 12 side.

The input disk 11 has a cam roller 24.
The input cam 25 having the driven gear 23 is engaged via the input cam 25, and the larger the input torque to the input disc 11, the more strongly the input cam 25 is pressed against the input disc 11 side to transmit a larger torque. You can do it.

The gear ratio of the first toroidal type continuously variable transmission mechanism 4 can be adjusted by increasing or decreasing by changing the tilt angle of the power rollers 13, 13. Hereinafter, a specific description for changing the tilt angle of each of the power rollers 13, 13 will be described with reference to FIGS. 1 and 2.

As shown in FIG. 2, in the first toroidal type continuously variable transmission mechanism 4, a pair of left and right power rollers 13 and 13 are arranged opposite to each other with the output shaft 3 sandwiched in the radial direction.
A pair of left and right roller support members 15 and 15 which will be described later and are rotatably supported via eccentric shafts 14 and 14 , respectively.
The casing 1 is provided on both side walls 1c, 1d so as to be vertically adjacent to each other. Further, rod members 16 extending in a direction orthogonal to the output shaft 3 are respectively provided at lower end portions 15b of the roller support members 15, 15.

The roller supporting members 15 and 15 provided with the rod member 16 are connected and supported at their upper ends 15a and 15a by an upper connecting member 71 which is provided above the output shaft 3 in a horizontal direction. Also, its lower end 15b, 1
5b, a valve body 3 to be described later, which is attached to the lower end of the output shaft 3 and the lower end of the casing 1.
5 is connected and supported by a lower connecting member 72 which is laterally arranged at a position immediately above 5. Therefore, by moving the roller support members 15 and 15 in the vertical direction to change the tilting force acting between the power rollers 13 and 13 and the input disk 11, the tilting of the power rollers 13 and 13 is performed. The turning angle changes, and thereby the gear ratio is adjusted to be increased or decreased.

A hydraulic actuator 34, which will be described later, is attached to the valve body 35 in order to move the roller support members 15 and 15 in the vertical direction to increase or decrease the gear ratio.
Hydraulic valve for controlling the operation of the hydraulic actuator 34
(Not shown) and are incorporated.

As shown in FIGS. 1 and 2, the valve body 35 includes a thick plate-shaped upper body 36 that is abutted and fixed to the lower end surface of the casing 1, and the upper body 3.
A thick plate-shaped center body 3 fixed to the lower surface of 6
7 and a thick plate-like lower body 38 that is abutted and fixed to the lower surface side of the center body 37, and has the three-layer structure, and the hydraulic actuator 34 is provided on the upper body 36.
Further, a control valve (not shown) is built in the center body 37 and the lower body 38. The valve body 35 is provided with oil return holes 41 to 43 which are the subject matter of the present invention, which will be described in detail later.

As shown in FIG. 5, the hydraulic actuator 34 is fitted on both upper and lower sides of a cylinder 19 formed on the upper body 36 and a partition wall 20 extending at an axially intermediate position of the cylinder 19. First piston 1 inserted and arranged
7 and a second piston 18, and the first piston 1
7, a first oil chamber 27 formed between the partition wall 20 and the partition wall 20,
By supplying and discharging the hydraulic pressure to and from the second oil chamber 28 formed between the second piston 18 and the partition wall 20, the roller support member 15 can be moved in the vertical direction to increase or decrease the gear ratio. Has become.

The above is the first toroidal type continuously variable transmission mechanism 4.
This is the main configuration of the second toroidal type continuously variable transmission mechanism 5.

By the way, this toroidal type continuously variable transmission Z
In the above, since each of the toroidal type continuously variable transmission mechanisms 4 and 5 transmits power by utilizing the shearing force of the oil, a relatively large amount of lubricating oil is used for each of the toroidal type continuously variable transmissions. It is supplied to the mechanisms 4, 5 and the gears.
Therefore, a relatively large amount of oil is always stored in the oil pan 2 and is circulated and supplied by an oil pump (not shown) via the oil strainer 33. In this case, since the valve body 35 is laterally installed at the lower end of the casing 1, the valve body 3 is
5, the return oil after lubricating the toroidal type continuously variable transmissions 4, 5 and the like arranged above the oil pan 2
When returning to the side, a large amount is accumulated on the upper surface side of the valve body 35, and the toroidal type continuously variable transmission mechanisms 4,5
As described above, when the input disks 11 and 21 and the output disks 12 and 22 are soaked, oil agitation resistance increases, power loss increases correspondingly, and power transmission efficiency as the toroidal continuously variable transmission Z decreases. On the street.

Further, as described above, a relatively large amount of oil is supplied to each of the input disks 11 and 21 and the output disks 12 and 22, and this supply oil is supplied to each of these disks 11, 12, 21, and. After adhering to 22, it is gradually moved to the outer peripheral side by the centrifugal force accompanying these rotations and finally scattered around, but in this case, after the scattered oil hits the inner wall of the casing 1 and the speed decreases. , And when the disks 11, 12, 21, 22 are turned over again and contacted again, the re-contact oil and the disks 11, 12,
Due to the speed difference between the disks 11 and 21,
As described above, the oil agitation resistance is generated in 2, 21, and 22 and this contributes to the reduction of the power transmission efficiency.

Further, when the vehicle is suddenly started / stopped, suddenly turned, etc., the oil stored in the oil pan 2 is biased due to the lateral G (lateral acceleration) at that time and the oil level is Although it inclines, in this case, on the oil level rising side, the disks 11, 12, 21, 22 are immersed in the oil to reduce the power transmission efficiency, and on the oil level lowering side, the immersion amount of the oil strainer 33 is increased. As described above, there is a possibility that the amount of oil will decrease, and in some cases air will leak into the oil, resulting in poor control of the hydraulic system.

In view of the above problems, the present invention adopts various new configurations as described later to deal with them. Hereinafter, these new configurations will be sequentially described. First, by improving the return property of the oil to the oil pan 2 side, the above-mentioned disks 11, 12
The power transmission efficiency of the toroidal type continuously variable transmission Z is improved by preventing the submergence of 21 and 22.

That is, in the valve body 35 disposed laterally between the lower end of the casing 1 and the upper end of the oil pan 2, an oil serving as a return oil passage from the casing 1 side to the oil pan 2 side is provided. A return hole is provided. In this case, however, in this embodiment, the invention described in claims 1 and 2 of the present application is applied when forming the oil return hole. Specifically, as shown in FIGS. 1, 3 and 4, when the three oil return holes 41 to 43 are formed by vertically penetrating the valve body 35, each of the oil return holes 41 to 43 is formed. Of the first
The oil return hole 41 is at a position corresponding to the maximum diameter portion 12a of the output disk 12 of the first toroidal type continuously variable transmission mechanism 4, and the second oil return hole 42 is at the input disk of the first toroidal type continuously variable transmission mechanism 4. Maximum diameter part 11
a and the input disk 2 of the second toroidal type continuously variable transmission 5
The third oil return hole 43 is provided at a position corresponding to the maximum diameter portion 21a of the first toroidal type continuously variable transmission mechanism 5 described above.
Are formed at positions corresponding to the maximum diameter portion 22a of the output disk 22 of FIG.

Each of the disks 11, 11 has such a structure.
In 12, 21, and 22, the oil is most easily immersed in the oil because the largest diameter portions 11a, 12a, 21a, and 22a located at the lowest position. That is, each disk 11, 12, 21, 2
If the oil return holes 41 to 43 are formed corresponding to the maximum diameter portions 11a, 12a, 21a, 22a of No. 2, even if a large amount of return oil is accumulated on the upper surface side of the valve body 35, at least the above each Oil return hole 4
In the portions 1 to 43, the oil flows down from here toward the oil pan 2 side, so that the oil level is naturally kept lower than the other portions. Therefore, the maximum diameter portions 11a, 12 of the respective disks 11, 12, 21, 22 are previously prepared.
Even if the space between the a, 21a, 22a and the valve body 35 is not wide, the maximum diameter portions 11a, 12a, 21a, 22a of the respective disks are formed.
A sufficient distance between the oil surface and the oil surface of the return oil is secured, and the maximum diameter portions 11a, 12a, 21a, 22a are immersed in the return oil, and the power transmission efficiency is lowered due to the stirring resistance. And it is certainly prevented.

Further, in this case, as described above, the disks 11, 12, 2 are placed at the portions where the oil level is lowered by the oil flowing down.
By arranging the maximum diameter portions 11a, 12a, 21a, 22a of 1, 22 respectively, oil immersion of the respective disks 11, 12, 21, 22 can be prevented, and even if the oil return performance of other portions is enhanced, the respective disk 11 It has little meaning in terms of preventing oil immersion of 12, 12, 21 and 22. This is
The oil return holes 41 to 43 are used for the discs 11,
This means that it is sufficient to cover only the maximum diameter portions 11a, 12a, 21a, 22a of 12, 21, 22 and, therefore,
It is possible to reduce the opening area of each of the oil return holes 41 to 43. When the opening areas of the oil return holes 41 to 43 are suppressed to be small in this way, for example, backflow of oil from the oil pan 2 side to the casing 1 side is prevented when the vehicle makes a sharp turn, and the oil pan 2 is also prevented. The oil surface inclination of the oil inside is also suppressed, and as a result, each disk 11, 12, 2 to the backflow oil is suppressed.
Problems such as a reduction in power transmission efficiency due to the immersion of Nos. 1 and 22 or poor control of the hydraulic system due to air spillage from the oil strainer 33, or insufficient lubricating oil can be reliably prevented.

Further, in this embodiment, in order to further enhance the function and effect by reducing the opening area of each of the oil return holes 41 to 43, FIG. 1 and FIG.
As shown in FIG. 4, the oil return holes 4 are formed by vertically penetrating the upper body 36, the center body 37, and the lower body 38 that form the valve body 35.
1 to 43 are not straight passages having a conventional general structure, but are bent passages in which the oil return holes 41 to 43 are laterally offset for each of the bodies 36 to 38. With such a configuration, particularly when the vehicle is turning suddenly, the oil in the oil pan 2 is abruptly biased and flows back to the casing 1 side through the oil return holes 41 to 43. In this case, the flow resistance of the oil return holes 41 to 43 is larger than that in the case where the oil return holes 41 to 43 are linear passages, and it is possible to suppress the oil backflow as much as possible, and eventually to the backflow oil. It is possible to more effectively prevent the immersion of the discs 11, 12, 21, 22 or the entrapment of air in the oil strainer 33.

Secondly, each of the disks 11, 12, 21,
By adjusting the scattered state of the splashed oil from 22, the re-contact of the splashed oil with the disks 11, 12, 21, 22 is prevented and a high power transmission efficiency is achieved.

That is, as shown in FIGS. 1 and 3, first of all, on the casing 1 side, the disks 11, 12, 21, 2 are arranged.
2 (note that FIG. 3 shows the portion of the input disc 21 of the second toroidal type continuously variable transmission mechanism 5, but the same applies to the other disc portions) and the first side between the side wall 1c. Second side space 5 between the partial space 51 and the other side wall 1d
3 and the upper space 52 between the upper wall 1e and the upper space 52 are locally enlarged (see the concavo-convex state of the upper wall 1e in FIG. 1), and especially on the other side wall 1d side. It is inclined and continuous with the curved upper surface wall 1e.

The disks 11, 12, 21, 22 are located near the upper ends of the disks 11, 12, 21, 22.
In the upper connecting member 71 having the opening 80 facing in the protruding state, the disks 11, 12, 21, 22 are
71a, 71c facing each other (that is, the inner peripheral wall of the opening)
Are inclined surfaces substantially along the outer circumferences of the disks 11, 12, 21, 22 and the surface 71b facing the one side wall 1c approaches the output shaft 3 as it goes downward. The surface 71c facing the other side wall 1d is an inclined surface that approaches the side wall 1d as it goes downward.

Further, each disk 11, 12, 21, 22
Located near the lower end of each of the disks 11, 12, 21,
In the lower connecting member 72 having the opening 79 facing the disk 22, the surfaces 72a, 72b of the inner wall surface of the opening 79 facing the disks 11, 12, 21, 22 are respectively connected to the disk 11, It is an inclined surface along the outer circumference of 12, 21, 22. Further, a shielding plate 40 is provided upright at a position near the other side wall 1d of the lower connecting member 72.

With this structure, re-contact of the scattered oil from the disks 11, 12, 21, 22 with the disks 11, 12, 21, 22 is prevented as much as possible. . That is, as shown by the arrow a in FIG. 3, the splashed oil horizontally scattered from the lower ends of the disks 11, 12, 21, 22 is guided to the inclined surface 72a of the lower connecting member 72 and is then transferred to the disks 11, 12. Since it scatters in the direction away from (i.e., one side wall 1c side), it does not come into contact with the disks 11, 12, 21, 22 again.

As shown by the arrow b, the disks 11, 12,
The splashed oil scattered from 21, 22 toward the upper part of the one side wall 1c reverses and falls downward after hitting the side wall 1c, but in this case, the first side space 51 is localized. Since it is a large space that has been enlarged, it does not come into contact with the disks 11, 12, 21, 22 during its fall.

As shown by the arrow c, the disks 11, 12,
21 and 22 to one side wall 1c of the casing 1 and the top wall 1
The splashed oil splashing toward the corners of e is collided and reversed, and is guided by the inclined surface 71b of the upper coupling member 71 and drops downward. Therefore, the disks 11, 12, 21, 2
No re-contact with 2.

As shown by the arrow d, the disks 11, 12,
The scattered oil scattered from the portions of the upper connecting member 71 corresponding to the opening 80 of the upper connecting member 71 is guided by the inclined surface 71a of the upper connecting member 71 and scattered to the side wall 1d of the other side. , The disks 11, 12, 21, 22 and the upper wall 1e are spaced apart from each other, and the upper wall 1e
Since it has a curved shape, after it collides with the upper surface wall 1e, it is guided by the upper surface wall 1e while moving away from the discs 11, 12, 21, 22 and moves smoothly. Is guided diagonally downward (that is, in the direction away from the disks 11, 12, 21, 22),
Since it drops to the oil pan 2 side as it is, it rarely comes into contact with the disks 11, 12, 21, 22 again.

As indicated by arrows e and f, the splashed oil scattered from the portion of the upper connecting member 71 corresponding to the inclined surface 71c is guided by the inclined surface 71c and is guided to the other side wall 1d side (that is, the disk). Scatter in the direction away from 11, 12, 21, 22), part of it drops after being reversed (see arrow f), and the other part is reversed to make disks 11, 12, 2
Although it approaches the 1, 22 side, it collides with the shield plate 40 and is scattered again in a direction away from the disks 11, 12, 21, 22. Therefore, in any case, re-contact of the splashed oil with the disks 11, 12, 21, 22 is prevented.

As indicated by the arrow g, the disks 11, 12,
The scattered oil that is scattered downward from the portions of the members 21 and 22 that face the shield plate 40 is the lower connecting member 72.
Since it is guided by the inclined surface 72b and scattered to the valve body 35 side, it does not come into contact with the disks 11, 12, 21, 22 again.

As described above, with the configuration of this embodiment, it is possible that the splashed oil from the disks 11, 12, 21, 22 re-contacts with the disks 11, 12, 21, 22. As a result, it is possible to prevent the power loss of the disks 11, 12, 21, 22 from increasing due to the increase of the stirring resistance due to the contact with the spattering oil having a slow speed. The transmission efficiency is achieved.

Further, in this embodiment, since the hydraulic actuator 34 is located in the return path of the lubricating oil, foreign matter such as metal powder mixed in the return oil is generated in the hydraulic actuator. In order to prevent the sliding portion of the switch 34 from entering and damaging this portion, some new structures are adopted. That is, one of them is, as shown in FIG. 5, that the lower connecting member 72 exists just above the hydraulic actuator 34. The inflow of return oil to the actuator 34 side is suppressed. Specifically, as shown in FIG. 6, the lower connecting member 72 has bearing holes 74, 74 ,.
, Which is formed by a rectangular plate material, but in that case, the parts corresponding to the hydraulic actuator 34, that is, the bearing holes 74, 74, ... The extension portion 75 and the inner extension portion 76 are formed.
Then, as shown in FIG. 5, in the assembled state, the upper position of the hydraulic actuator 34 is covered by the outer extending portion 75 and the inner extending portion 76 of the lower connecting member 72. Return oil is hydraulic actuator
The outer extending portion 75 and the inner extending portion 76 prevent the inflow from flowing into the switch 34.

As for the other one, as shown in FIG. 7, a bearing race 78 above the thrust bearing 77 mounted between the hydraulic actuator 34 and the lower connecting member 72 is enlarged in the radial direction. It is formed so as to be extended, and the extended portion suppresses the inflow of the return oil into the hydraulic actuator 34.

In either of the above two methods, the inflow of the return oil into the hydraulic actuator 34 is suppressed, so that the oil mixture is prevented from invading the sliding portion of the hydraulic actuator 34. Therefore, the durability of the hydraulic actuator 34 is improved.

[Brief description of drawings]

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

FIG. 2 is a vertical sectional view taken along the line II-II in FIG.

3 is a vertical cross-sectional view taken along the line III-III in FIG.

FIG. 4 is a view taken along the line IV-IV in FIG.

FIG. 5 is an enlarged view of a V portion of FIG.

FIG. 6 is a plan view of the lower connecting member shown in FIG.

7 is a cross-sectional view showing a modified example of the cylinder portion shown in FIG.

[Explanation of symbols]

1 is a casing, 2 is an oil pan, 3 is an output shaft, 4 is a first toroidal type continuously variable transmission mechanism, 5 is a second toroidal type continuously variable transmission mechanism, 11 is an input disc, 12 is an output disc, and 13 is a power roller. , 14 is an eccentric shaft, 15 is a roller support member, 16 is a rod member, 17 is a first piston, 1
8 is a second piston, 19 is a cylinder, 20 is a partition wall, 21
Is an input disc, 22 is an output disc, 23 is a driven gear, 24 is a cam roller, 25 is an input cam, 27 is a first oil chamber, 28 is a second oil chamber, 31 is a bearing, 32 is a bearing,
33 is an oil strainer, 34 is a hydraulic actuator,
35 is a valve body, 36 is an upper body, 37 is a center body, 38 is a lower body, 40 is a shielding plate, 4
1 is a first oil return hole, 42 is a second oil return hole, 43 is a third oil return hole, 51 is a first side space, 52 is an upper space, 53 is a second side space, and 71 is an upper connecting member. , 72 is a lower connecting member, 73 is a main body portion, 74 is a bearing hole, 75 is an outer extending portion, 76 is an inner extending portion, 77 is a thrust bearing, 78 is bearing racing, 7
Reference numeral 9 is an opening, 80 is an opening, and Z is a toroidal type continuously variable transmission.

─────────────────────────────────────────────────── ─── Continuation of the front page (56) Reference JP 4-29659 (JP, A) JP 59-9361 (JP, A) JP 61-13063 (JP, A) JP 4- 69445 (JP, A) Actual development Sho 63-92859 (JP, U) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16H 15/38 F16H 57/00-57/12

Claims (3)

(57) [Claims] 1. An input disk and an output disk having a curved conical friction surface are coaxially arranged with the friction surfaces facing each other, and between the input disk and the output disk. A power roller for simultaneously contacting the friction surface of the disk and transmitting power from the input disk to the output disk side is arranged via a roller supporting member, and the roller supporting member is operated by a hydraulic actuator to operate the power roller.
Of the toroidal type continuously variable transmission mechanism in which the transmission ratio is made variable by moving the tilting angle of the power roller by moving it up and down, which is the direction of the tilt axis of the toroidal type continuously variable transmission mechanism. A toroidal type continuously variable transmission in which a valve body having a control valve mechanism for controlling the operation of the actuator at a position is arranged so as to separate the toroidal type continuously variable transmission mechanism and the oil pan in the vertical direction. And an oil return hole for returning the oil from the toroidal type continuously variable transmission side to the oil pan side is formed at a position corresponding to the maximum diameter portion of each of the discs of the valve body. A toroidal type continuously variable transmission. 2. The valve body according to claim 1, wherein the valve body is composed of a plurality of body members that are vertically stacked, and the oil return holes are laterally sequentially arranged in portions corresponding to the body members. Toroidal type continuously variable transmission characterized by being offset. 3. The toroidal type continuously variable transmission mechanism according to claim 1 or 2, wherein a plurality of the toroidal type continuously variable transmission mechanisms are arranged side by side in the axial direction, and the roller supporting members are connected to each other by a connecting member, A toroidal type continuously variable transmission characterized in that a cross-sectional shape of a portion corresponding to each disk is an inclined surface that can guide scattered oil scattered by the rotation of each disk in a direction away from each disk. .