JP2000055158A - Toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To locate a post member about its rotational position simply and accurately, fix it with standard bolt, and perform lubrication with good efficiency. SOLUTION: This toroidal type continuously variable transmission includes trunnions to support power rollers with possibility of tilting and swinging, a tension member 10 to hold the shanks of the trunnions rotatably and couple them together, and a post member 171 to support the tension member 10 on a transmission housing, whereby the post member is located by knock pins 176a and 176b and fixed to the transmission housing. The supply of a lubricating oil is made through the first oil passages 56a and 56b formed in the housing and the second oil passages 181-185 formed in the post member, and the first passages are tied with the second via communication holes 180a and 180b formed penetrating the knock pins in the axial direction.

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 using a toroidal transmission unit in which a power roller is sandwiched between input / output disks arranged opposite to each other in the axial direction. .

[0002]

2. Description of the Related Art A toroidal using a toroidal transmission unit in which a power roller is sandwiched and arranged in a cavity formed between an input and an output disk disposed opposite to each other and in contact with both disks. Type continuously variable transmissions are already known. Further, two sets of such toroidal transmission units are disposed in parallel in the axial direction, and the input disks of these two sets of toroidal transmission units are both connected to the input member, and the output disks are both connected to the output member. Double-cavity toroidal type continuously variable transmissions are also already known.

In such a toroidal-type continuously variable transmission, the power transmission ratio is changed by tilting and oscillating a power roller disposed in a cavity, thereby performing a gear shift. Therefore, each power roller is swingably supported by the trunnion member. Here, the power roller is sandwiched between the input and output disks at a position symmetrical with respect to the rotation center axis of these disks, and a force that is pressed and clamped by the input and output disks and separates radially outward from each other. Receive. In order to hold the power roller at a predetermined position against such a force, the trunnion shaft portions of the trunnion members supporting the respective power rollers are rotatably held, and the distance between both shaft portions is kept constant. A tension member is used for connecting and supporting.

A configuration using such a tension member is disclosed in, for example, Japanese Patent No. 2697261. This publication discloses a double-cavity toroidal-type continuously variable transmission, in which a pair of power rollers (friction rollers) are provided in both cavities, respectively. The trunnion shaft portion of the freely supported trunnion member is rotatably held by a tension member, and the tension member keeps the center distance of the trunnion shaft portion constant.

Such a tension member is supported by a transmission housing. One example of this support structure is shown in FIG.
Is shown in In this structure, the tension member 90 is provided with a fitting hole into which the first post member 92 is inserted and fitted, and the first post member 92 is inserted into the fitting hole and locked with the tension member 90. Further, the first post member 92 is attached to the housing 91 by bolt connection.

At this time, as shown in FIG.
2 is fitted with a second post member 93, and a stopper member 94 is attached to the second post member 93 with a disc spring 95 interposed therebetween.
2 and the second post member 93 and the housing 91 are fastened together by bolts 96 used for coupling.
Further, a lubricating oil passage 96 for supplying lubricating oil to the contact surface between the disk and the roller is provided in the bolt 96 and the second post member 93.
a, 93a and 93b are formed. The lubricating oil is supplied from the lubricating oil passage 91 a of the housing 91 to the lubricating oil passage 96 a formed in the bolt 96, the second post member 93 and the bolt 9.
6 through a lubricating oil passage 93a formed by a gap between the second post member 93 and a jet hole 93b formed in the second post member 93, and is jetted to a contact portion between the disk and the roller to lubricate this portion. It has become.

[0007]

In such a configuration, it is required that the lubricating oil be accurately sprayed to the contact portion between the disk and the roller for efficient lubrication.
It is necessary to accurately position the position 3b (rotation angle position). However, conventionally, as described above, both post members 92, 92, stopper member 94,
The conical spring 95 and the like are fastened together, and there is a problem in that when this second fastening is performed, the second post member 93 is rotated together with the bolt 96, and the rotational angle position of the ejection hole 93b is shifted, so that accurate positioning is difficult. In order to prevent such a problem, it is conceivable to provide the second post member 93 with a two-sided width shape for rotation prevention. However, such a rotation prevention structure is likely to be complicated, and the manufacturing cost is increased. Furthermore, various secondary problems may arise, such as the need for extra space.

Further, in the above-mentioned conventional construction, since the lubricating oil passage 96a is formed in the bolt 96, standard bolts cannot be used, so that the bolt manufacturing cost is increased. There is a problem that strength is reduced.

The present invention has been made in view of such a problem.
When the post member supporting the tension member is fixed to the housing, the rotation position of the post member can be easily and accurately determined, and the lubrication oil is spouted from the post member in a desired direction to efficiently lubricate. And to provide a toroidal-type continuously variable transmission having a configuration in which the post member can be fixed to the housing with a simple and sufficient strength using standard bolts. .

[0010]

In order to achieve such an object, the present invention provides an input and output disk (first and second input and output disks 110, 120,
210, 220, etc.), a pair of power rollers (the first to fourth power rollers 150, 160, 250,
260 and the like (the first and second toroidal transmission units 10 of the embodiment).
0, 200, etc.), a pair of trunnion members (the trunnion member 1 of the embodiment) for supporting each power roller in a tiltable and swingable manner.
51, 161, 251, 261 etc.) and trunnion shaft portions of these paired trunnion members (left and right trunnion shaft portions 151a, 161a, 251a, 261a etc. of the embodiment).
Tension members that rotatably hold each other and that connect and support the shafts while maintaining a constant inter-axis distance (the first tension member in the embodiment).
Tension member 10) and post members (post members 171 and 271 in the embodiment) locked to the tension member to support the tension member by the transmission housing, and the post member is a pair of positioning knock pins. The first lubricating oil passage formed in the transmission housing is a lubricating oil passage which is positioned by the knock pins 176a, 176b and the like in the embodiment, fixedly held in the transmission housing, and supplies lubricating oil to the toroidal transmission unit. (Lubricating oil passages 55, 56a, 56b, etc. in the embodiment) and second lubricating oil passages formed in the post member (lubricating oil passages 181a, 181b, lubrication holes 182a, 1 in the embodiment).
82b, lubricating oil passage 183, lubricating holes 184a, 184
b, 185a, 185b, etc.)
The lubricating oil passage and the second lubricating oil passage are connected via a third oil passage (communication holes 180a, 180b and the like in the embodiment) formed through the positioning knock pin in the axial direction.

In the case of the toroidal-type continuously variable transmission having such a configuration, the positioning of the post member can be performed by using only the pair of knock pins, and the rotation of the post member can also be prevented. In addition, it is possible to perform mounting under accurate positioning. further,
Since the knock pin is used only for positioning, its strength is not so much required. Therefore, a relatively large through-hole can be formed in the inside and used as a lubricating oil passage (third lubricating oil passage). The path can be formed with a simple configuration.

It is preferable that the post member is connected and fixed to the transmission housing with a fastening bolt between the pair of positioning knock pins. By doing so, it is not necessary to form a lubricating oil passage for the fastening bolt, and it is possible to use a standard bolt, and it is possible to reduce the cost of the bolt while securing the fastening strength.

[0013]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a power transmission path configuration of the toroidal type continuously variable transmission according to the present invention. The continuously variable transmission T includes a torque converter T / C connected to an output shaft of the engine E, and first and second toroidal transmission units 100, which are connected in parallel to a turbine shaft of the torque converter T / C. 200. Here, the first and second toroidal transmission units 100, 2
Since 00 has the same configuration, corresponding components are indicated by the same numbers in the last two digits.

The first toroidal transmission unit 100 has a first input disk 110 having a semi-donut-shaped inner surface 110a having a semi-circular cross section, and an axially opposed and semi-circular cross-section to the inner surface 110a. Output disc 12 having a semi-doughnut shaped inner surface 120a
0, first input and first output disks 110, 120
Cavity 1 surrounded by inner surfaces 110a and 120a of
30 and a pair of first and second power rollers 150 and 160 sandwiched in contact with the inner surfaces 110a and 120a. The power rollers 150 and 160 are connected to both disks 110 and 120.
Are disposed at positions opposing each other with respect to the rotation center axis, that is, positions symmetrical with respect to the rotation center axis.

The first input disk 110 and the first output disk 120 are disposed on the transmission input shaft 1 coaxially with each other and opposed to each other.
10 is connected to the transmission input shaft 1 and rotates integrally therewith. On the other hand, the first output disk 120 is disposed on the transmission input shaft 1 so as to be relatively rotatable, is coupled to the first gear 2, and is relatively rotatable on the input shaft 1 together with the first gear 2.

The second toroidal transmission unit 200 is configured to be axially symmetrical with respect to the first toroidal transmission unit 100, and has a semi-doughnut-shaped inner surface 21.
0a and the inner surface 21
A second output disc 220 having a semi-donut-shaped inner surface 220a that is axially opposed to the inner surface 210a, and a pair of held and disposed in a second cavity 230 surrounded by the inner surfaces 210a and 220a. And the third and fourth power rollers 250 and 260. The two disks 210 and 220 are disposed on the input shaft 1 coaxially opposite each other, and the second input disk 210 is connected to the transmission input shaft 1 and rotates integrally therewith. On the other hand, the second output disk 220 is relatively rotatably disposed on the transmission input shaft 1, is coupled to the first gear 2, and is relatively rotatable on the input shaft 1 together with the first gear 2.

The first gear 2 meshes with a second gear 3a connected to one end of the counter shaft 3, and the second gear 3a is disposed on the output shaft 5 so as to be relatively rotatable. Meshes with A fourth gear 3b is connected to the other end of the counter shaft 3, and rotates together with the second gear 3a. The fourth gear 3b meshes with a fifth gear 4 (reverse idler gear), and the fifth gear 4 meshes with a sixth gear 5b disposed on the output shaft 5 so as to be relatively rotatable. A forward clutch 6a for engaging and disengaging the third gear 5a and the output shaft 5; and a reverse clutch 6b for engaging and disengaging the fifth gear 5b and the output shaft 5. A seventh gear 7a is provided at an end of the output shaft 5. Are connected and arranged. The seventh gear 7a meshes with an eighth gear 7b having a differential mechanism 8.

For this reason, when the forward clutch 6a is engaged, the rotation of the first gear 2 is changed to the second and third gears 3a,
The rotation is transmitted to the output shaft 5 via 5a, and this rotation is transmitted from the seventh and eighth gears 7a, 7b to the left and right axles 9a, 9b via the differential mechanism 8, and the vehicle is driven in the forward direction. On the other hand, when the reverse clutch 6b is engaged, the rotation of the first gear 2 is transmitted to the output shaft 5 via the fourth, fifth, and sixth gears 3b, 4, 5b, and this rotation is transmitted to the seventh and fifth gears. The power is transmitted from the eight gears 7a and 7b to the left and right axles 9a and 9b via the differential mechanism 8, and the vehicle is driven in the reverse direction.

The shifting operation of the transmission having the above-described structure is performed by the first to fourth power rollers 150, 160, 250,
This is performed by tilting and swinging 260 about the respective tilting and swinging axes O as indicated by an arrow φ. The structure is shown in FIG.
The first toroidal transmission unit 100 will be described as an example with reference to FIG. 2 which is a cross-sectional view along the arrow II-II. Note that the second toroidal transmission unit 200 has basically the same configuration, and a description thereof will be omitted. .

The first toroidal transmission unit 100 has a first
And the second power rollers 150 and 160. The power rollers 150 and 160 are connected to the rotation center axis of the input shaft 1 (the first input and first output disks 110 and 120).
(Which is also the center axis of rotation). First and second power rollers 150, 16
0 is the first and second tension members 10 and 20 slidable in the left-right direction (y direction) in FIG.
The tension member 10 has trunnion members 151 and 161 supported by the tension member of the claims. The trunnion members 151, 161 are provided on bearings 152a, 152b, and 16 at left and right trunnion shaft portions 151a, 151b and 161a, 161b, respectively.
It is supported by both tension members 10 and 20 via 2a and 162b, and can tilt and swing (rotational movement in the φ direction) about the tilt and swing axis O. Therefore, the trunnion members 151 and 161 can move in the y direction and can tilt and swing in the φ direction.

Each of the trunnion members 151 and 161 has a shaft member 154 having an axis orthogonal to the tilt and swing axis O.
The shaft members 154 and 164 are attached.
4, cone members 153 and 163 are rotatably mounted. The cone members 153 and 163 are rotatably supported by the trunnion members 151 and 161 via bearings.
163 is pressed against the inner surfaces 110a, 120a of the input and output disks 110, 120 and held in a state of being abutted and sandwiched.

Here, the shaft members 154 and 164 integrally have eccentric shaft portions 154a and 164a eccentric from the rotation center of the cone members 153 and 163, and the eccentric shaft portions 154a and 164a
1,161. As a result, the trunnion members 151 and 161 can be automatically aligned, and the cone members 153 and 163 and the input / output disks 110 and 12 can be aligned.
Automatic centering is performed so that the rotational speed directions of the two at the point of contact with zero always coincide.

On the other hand, the trunnion members 151 and 161 are
When the cone members 153 and 163 are moved in the directions, a difference occurs in the rotational speed directions of the cone members 153 and 163 and the input / output disks 110 and 120 at the contact points. Occurs and the trunnion member 15
1, 161 is tilted and rocked in the φ direction about the tilt and rocking axis O. As a result, the cone members 153 and 163 are tilted and rocked along the inner surfaces 110a and 120a while being held between the input and output disks 110 and 120, that is, the tilted rocking axis O is set in the plane of FIG. The gear is tilted and rocked as a center, and a shift is performed. As you can see from this,
Shift control can be performed by pressing the trunnion members 151 and 161 in the y direction. Hydraulic actuators 145 and 146 are provided to apply a force to press the trunnion members 151 and 161 in the y direction as described above.

Here, as can be seen from FIG. 1, the first and second power rollers 150, 160 are provided on the semi-donut-shaped inner surfaces 110a, 1 of the first input / output disks 110, 120.
20a, the two disks 11
When a pinching force from 0, 120 is received, a force is pushed outward in the radial direction. First and second tension members 10, 20 are provided to hold the power rollers 150, 160 at predetermined positions against such a force.

The first tension member 10 will be described with reference to FIGS. FIG. 3 shows the first tension member 1.
The members around the zero direction are taken out and shown, and they are shown in cross section along the arrows III-III in FIG. In FIG. 3, the first tension member 10 is provided so as to enter the first cavity 130 and the second cavity 230. On the other hand, FIG. 4 shows the first tension member 10 and the power rollers 150, 160, 250, and 260 supported by the first tension member 10, which are viewed from the direction of arrow IV in FIG. . Although the second tension member 20 is not shown, the first tension member 1 is provided below the first cavity 130 and the second cavity 230 in FIG.
0, and is located on the near side in FIG. 4 and overlaps the first tension member 10.

As is clear from FIG. 3, the first tension member 1
0 is the first and second toroidal transmission units 100,
200 power rollers 150, 160, 250, 260
Left trunnion shaft portions 151a, 161a, 251a, 2
Support holes 11a, 11b, 2 rotatably supporting 61a.
1a, 21b (note that 21a, 21b are not shown), and bearings 152a, 162a, 252a, 262a are formed by these support holes 11a, 11b, 21a, 21b.
(Bearings 252a and 262a are not shown) through left trunnion shaft portions 151a, 161a, 251a and 26.
1a is rotatably supported. Similarly, the second tension member 20 also includes the right trunnion shaft portions 151b, 161b, 251b, and 26.
1b so as to be rotatable so that the power roller 1
50, 160, 250 and 260 are supported so as to be able to swing and tilt (φ direction).

The first tension member 10 is supported by the transmission housing 50 at two locations (two locations corresponding to the first and second toroidal transmission units 100 and 200). One of the support structures is shown in an enlarged scale in FIG. 5, and as shown in FIGS. 3 to 5, the first tension member 10 is attached to the transmission housing 50 by the post members 171 and 271. Since these two support structures have the same structure, one of the support structures (the support structure shown in FIG. 5) will be described below as an example.

The post member 171 (271) is fastened to the tip of the convex portion 51 of the housing 50 by fastening bolts 172. The post member 171 has a spherical outer peripheral fitting portion 171a. The outer peripheral fitting portion 171a fits into the fitting hole 12 of the first tension member 10 and
0 is locked to the post member 171, so that the first tension member 10 is attached to the housing 50.

At the tip end of the post member 171, the cylindrical portion 1
71b, and a disc spring 174 and a swing stopper 173 are attached to the cylindrical portion 171b.
It is held down by 5 and attached. In this state, the disc spring 174 is in a compressed state, and the swing stopper 173 is fixed and held by the frictional force.

As described above, since the swing stopper 173 is structured to be independently attached to the post member 171 by the circlip 175, the swing stopper 173 is attached to the post member 171 with the disc spring 174 sandwiched by the circlip 175. Thus, the post member 171 in the sub-assembly state can be fixed to the convex portion 51 of the housing 50 by the fastening bolt 172 as shown in FIG. As a result, the post member 171 holding and retaining the first tension member 10 is assembled, and the disc spring 174 is mounted.
And the swing stopper 173, which is fixed by receiving the pressing force, can be separately assembled, and these assemblings are easy. The compression load of the disc spring 174 is equal to the circlip 1.
75, and does not act on the fastening bolt 172, so that the problem of loosening of the fastening bolt 172 does not occur.

The post member 171 is formed with a bolt insertion hole 171c penetrating the center thereof in the axial direction. A fastening bolt 172 is inserted into the bolt insertion hole 171c to be screwed and fastened to the housing 50. At this time, the bolt insertion hole 171c is larger than the outer diameter of the fastening bolt 172, and a lubricating oil passage 183 is formed therebetween.

A pair of left and right knock pin insertion holes 171d and 171e are formed on the end surface of the post member 171 which is in contact with the convex portion 51 of the housing with the bolt insertion hole 171c interposed therebetween. On the other hand, a pair of left and right knock pin insertion holes 51a and 51b corresponding to these are formed in the convex portion 51. Then, as shown in FIG. 5, a pair of left and right hollow knock pins 176a, 176b are fitted into these knock pin insertion holes 51a, 51b and 171d, 171e, and the post member 171 is mounted and positioned.

Incidentally, as shown in FIG.
Is formed with a lubricating oil passage 55 to which a predetermined lubricating oil is supplied as shown by an arrow L, and a lubricating oil passage 56 branched therefrom.
a, 56b (57a, 57b) are knock pin insertion holes 51;
a, 51b. In addition, knock pin 176
Reference numerals a and 176b are hollow, and communication holes 180a and 180b serving as lubricating oil passages are formed therein. On the other hand, the post member 171 has knock pin insertion holes 171d and 171d.
e form the lubricating oil passages 181a and 181b.
Lubrication holes 182a, 182b, 184a, 184b are formed to reach the knock pin insertion holes 171d, 171e through c. Further, these lubrication holes 184a, 184b
Lubrication holes 185a and 185b are formed in a plane perpendicular to the above and penetrate in the radial direction of the cylindrical portion 171b.

A predetermined lubricating oil is supplied to the lubricating oil passage 55 of the housing 50 as shown by an arrow L. The lubricating oil is supplied from the lubricating oil passages 56a and 56b to the knock pins 176a and 176b. Communication holes 180a, 180b
Through the lubricating oil passages 181a and 181b, and through the lubricating holes 182a and 182b to the lubricating oil passage 183. Thereafter, the lubricant is ejected from the lubrication holes 184a, 184b or the lubrication holes 185a, 185b to perform lubrication in the first cavity 130, particularly lubrication of the contact portions between the power rollers 150, 160 and the input / output disks 110, 120 and the like. .

The post member 171 is provided as described above.
The operation of the swing stopper 173 (273) attached to the device will be described with reference to FIG. FIG. 4 shows a state in which the power rollers 150 and 160 are tilted and swung about the tilt and swing axis O by the trunnion members 151 and 161 as described above, and are in contact with the swing stopper 173. At this time, the stopper surfaces 173a, 173 of the swing stopper 173
3c, stopper surfaces 15 of both power rollers 150, 160
0a and 160a come into contact with each other and do not swing any more.

In the state shown in FIG. 4, the first power roller 150 tilts and swings clockwise and the second power roller 1
The case where the swing limit when the tilting and swinging movement of the shaft 60 is set in the counterclockwise direction is set by the swing stopper 173 is shown. On the other hand, when the first power roller 150 tilts and swings counterclockwise and the second power roller 160 tilts and swings clockwise, the swing limit is the stopper surface 173b of the swing stopper 173. , 173d with both power rollers 150, 160
Are set in contact with the stopper surfaces 150b and 160b.

As described above, the swing stopper 173 for setting the swing limit is attached to the post member 171 by receiving the frictional force associated with the pressing force of the disc spring 174 as described above. Even if the mounting angle positions are slightly shifted, the two power rollers 150, 16
0 swings to the swing limit, and as shown in FIG. 4, resists the above frictional force to a position where the stopper surfaces 150a, 160a of both power rollers 150, 160 abut against the stopper surfaces 173a, 173c of the swing stopper 173. Rotated and positioned in the correct position.

[0038]

As described above, according to the present invention,
The post member is positioned by a pair of positioning knock pins and fixedly held in the transmission housing, and the post member can be positioned and also prevented from rotating by only the pair of knock pins, thereby simplifying the mounting structure of the post member. , And can be mounted under accurate positioning. Further, a lubricating oil passage for supplying lubricating oil to the toroidal transmission unit is constituted by a first lubricating oil passage formed in the transmission housing and a second lubricating oil passage formed in the post member. The lubricating oil passage and the second lubricating oil passage are connected via a third oil passage formed by penetrating the positioning knock pin in the axial direction, but the role of the knock pin is positioning, and the strength of the lubricating oil itself is very low. Therefore, a relatively large through hole can be formed inside the knock pin and used as a lubricating oil passage (third lubricating oil passage), and the lubricating oil passage can be formed with a simple configuration.

It is preferable that the post member is connected and fixed to the transmission housing by a fastening bolt between the pair of positioning knock pins. By doing so, it is not necessary to form a lubricating oil passage for the fastening bolt, and it is possible to use a standard bolt, and it is possible to reduce the cost of the bolt while securing the fastening strength.

[Brief description of the drawings]

FIG. 1 is a schematic diagram showing a power transmission path of a toroidal type continuously variable transmission according to the present invention.

FIG. 2 shows a toroidal transmission mechanism of the transmission with an arrow in FIG.
It is an expanded sectional view shown along II-II.

FIG. 3 is an enlarged sectional view showing a part of the transmission along an arrow III-III in FIG. 2;

FIG. 4 is an arrow IV of FIG. 3 around a first tension member of the transmission.
It is a figure seen from a direction.

FIG. 5 is a sectional view showing a support structure of a first tension member in the transmission.

FIG. 6 is a cross-sectional view showing a support structure of a tension member in a conventional toroidal type continuously variable transmission.

[Explanation of symbols]

T Toroidal-type continuously variable transmission 10 First tension member 20 Second tension member 55, 56a, 56b Lubricating oil passage (first lubricating oil passage) 100, 200 Toroidal transmission unit 110, 210 Input disk 120, 220 Output disk 150, 160, 250, 260 Power rollers 151, 161, 251, 261 Trunnion members 151a, 151b, 161a, 161b, 251a,
251b, 261a, 161b Trunnion shaft part 171,271 Post member 172 Fastening bolt 176a, 176b Dowel pin 180a, 180b Communication hole (third lubricating oil passage) 181a, 181b, 182a, 182b, 183,1
84a, 184b, 185a, 185b Lubricating oil passage, lubricating oil passage, and lubricating hole (second lubricating oil passage)

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J051 AA03 AA08 BA03 BB02 BD02 BE09 CA05 CB07 EC10 ED08 FA01 3J063 AA01 AB33 BA20 CA01 CB36 CD53 XD03 XD23 XD42 XD72 XE14

Claims (1)

[Claims] 1. A toroidal transmission unit comprising a pair of power rollers disposed between input and output disks disposed opposite to each other at positions symmetrical with respect to a rotation center axis of these disks. A toroidal type continuously variable transmission, comprising: a pair of trunnion members for supporting the respective power rollers in a tiltable and oscillating manner; A tension member for connecting and supporting a fixed distance, and a post member locked to the tension member to support the tension member by the transmission housing, wherein the post member is formed by a pair of positioning knock pins. A lubricating oil passage positioned and fixedly held in the transmission housing, for supplying lubricating oil to the toroidal transmission unit; A first lubricating oil passage formed in the transmission housing and a second lubricating oil passage formed in the post member, wherein the first lubricating oil passage and the second lubricating oil passage are the positioning knock pins. The third formed through the
A toroidal-type continuously variable transmission characterized by being connected via an oil passage.