JP3555458B2 - Lubrication structure of toroidal type continuously variable transmission - Google Patents

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a toroidal-type continuously variable transmission in which a friction roller is arranged between an input disk and an output disk, and a transmission ratio between input and output can be changed by changing a tilting state of the friction roller. It is about.
[0002]
[Prior art]
As a conventional toroidal-type continuously variable transmission, for example, there is one described in Japanese Patent Application Laid-Open No. Hei 10-26201 previously proposed by the present applicant. This toroidal-type continuously variable transmission comprises two input disks rotatable integrally with a torque transmitting rotary shaft and two rotatable output disks disposed coaxially around the torque transmitting rotary shaft. Two friction rollers called power rollers are respectively disposed in the toroidal grooves formed between the facing surfaces of the input disk and the output disk so as to form a pair. Each is tiltably supported by a support mechanism called a trunnion. On the other hand, each of these support mechanisms is driven by a fluid pressure cylinder, for example, in a direction perpendicular to the axial direction of the friction roller and perpendicular to the axial direction of the input / output disk. Here, for example, if the axis of the friction roller and the axis of the input / output disk are displaced, a deviation occurs between the rotation direction of the friction roller and the input direction from the input disk, and the component of the deviation causes the friction roller to tilt. As a result, the contact radius between the friction roller that is in frictional contact with both disks and the input disk and the contact radius with the output disk change, so that the gear ratio between input and output changes. The fluid pressure cylinder is provided on a cylinder body that simultaneously supports each support mechanism itself.
[0003]
The four friction rollers rotate in a toroidal groove between the two input / output disks, and in particular, the toroidal groove, that is, a half made up of an arc whose concavity does not reach the diameter (accurately, a conic section curve). In the case of a toroidal-type continuously variable transmission, a force that moves the friction roller away from the center of rotation of the input / output disk, that is, a force that pushes the friction roller outward, acts on the friction roller. Since this force is very large, it is necessary that the supporting portion of the supporting mechanism that rotatably supports the friction roller obtains a sufficient lubricating fluid and is sufficiently lubricated. Therefore, conventionally, in order to directly supply a sufficient lubricating fluid to the supporting portions of the four friction rollers, the lubricating fluid is supplied to each of the lubricating fluid supplying portions on the opposite side of the cylinder body from the friction roller with respect to the cylinder body. And lubricates the support portion of each friction roller through the inside of each support mechanism from there. Four lubricating fluid passages are formed in the lubricating fluid supply part of each of the support mechanisms in a cylinder body that constitutes the fluid pressure cylinder, and the lubricating fluid is supplied therefrom.
[0004]
[Problems to be solved by the invention]
By the way, the supply fluid pressure to the fluid pressure cylinder for driving the support mechanism is preferably as low as possible. In order to increase the supply fluid pressure, a supply source such as a pump becomes large, or a large driving force is required to drive the pump, thereby reducing fuel consumption. There is also a need to improve the sealing performance of the seal portion. In order to reduce the supply fluid pressure, the sectional area of the hydraulic cylinder, that is, the sectional area of the piston, must be increased.
[0005]
However, in the conventional lubricating structure of the toroidal type continuously variable transmission, a fluid passage for the lubricating fluid is formed in the cylinder body of the fluid pressure cylinder, and each of the lubricating fluids of the four support mechanisms is formed through the fluid passage. Since the lubricating fluid is individually supplied to the supply portion, the cross-sectional area of the hydraulic cylinder is limited, and there is a limit in reducing the supply fluid pressure to the hydraulic cylinder. Further, depending on the configuration of the fluid path formed in the cylinder body, that is, so-called routing, there is a problem that the lubricating fluid supply flow rate to each lubricating fluid supply site of each support mechanism, that is, the support site of the friction roller, cannot be made uniform.
[0006]
The present invention has been developed in view of these problems, it is possible to increase the cross-sectional area of the hydraulic cylinder that drives the support mechanism to tilt the friction roller, to reduce the supply fluid pressure, It is another object of the present invention to provide a lubricating structure for a toroidal-type continuously variable transmission that can make the supply flow rate of the lubricating fluid to each lubricating fluid supply site of the four support mechanisms uniform.
[0007]
[Means for Solving the Problems]
In order to solve the above-mentioned problems, a lubricating structure for a toroidal type continuously variable transmission according to claim 1 of the present invention includes a plurality of friction rollers disposed between opposed rotatable input disks and output disks. A plurality of support mechanisms for individually supporting the friction rollers in a tiltable manner, and a plurality of fluid pressure cylinders for individually driving the respective support mechanisms in order to tilt the friction rollers; A structure for supplying a lubricating fluid for lubricating a supporting portion of each of the friction rollers through a mechanism to a predetermined lubricating fluid supply portion on the opposite side of the friction roller with the fluid pressure cylinder interposed therebetween; A common lubricating fluid passage is provided in a cylinder body constituting the cylinder, and the predetermined lubricating fluid supply portion of the support mechanism farthest from the common lubricating fluid passage is set up from the common lubricating fluid passage. A piping structure, the predetermined lubricating fluid supply site other support mechanism, a separate lubricating fluid passage formed in the cylinder body from the common lubricant path to the predetermined lubrication fluid supply portion of each support mechanism It is characterized by the following.
[0009]
【The invention's effect】
Thus, according to the lubricating structure of the toroidal-type continuously variable transmission according to the first aspect of the present invention, the lubricating fluid for lubricating the support portion of each friction roller through the inside of each support mechanism is supplied to the fluid pressure cylinder. When supplying the lubricating fluid to the predetermined lubricating fluid supply site on the opposite side of the friction roller sandwiching the frictional roller, Supplies the lubricating fluid in a piping structure rising from the common lubricating fluid path, and the predetermined lubricating fluid supply section of the other support mechanism is provided with a common lubricating fluid path to the predetermined lubricating fluid supply section of each support mechanism. Since the lubricating fluid is supplied in a separate lubricating fluid passage formed in the cylinder body from the above, the cross-sectional area of the hydraulic cylinder is reduced by the lubricating fluid passage formed in the cylinder body. It is difficult to limit the supply fluid pressure by increasing the cross-sectional area of the fluid pressure cylinder, thereby reducing the supply source such as a pump or reducing the driving force for driving the same. Can be improved. Further, by adjusting the pipe diameter of the piping structure or adjusting the flow resistance in the piping structure, the lubricating fluid is supplied to at least a predetermined lubricating fluid supply portion of the support mechanism farthest from the common lubricating fluid passage. The supply flow rate can be easily secured, and the supply flow rate of the lubricating fluid to the plurality of support mechanisms, that is, the plurality of friction rollers can be made uniform.
[0011]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, an embodiment of a toroidal type continuously variable transmission according to the present invention will be described with reference to the accompanying drawings.
[0012]
First, a schematic configuration of the toroidal-type continuously variable transmission according to the present embodiment will be briefly described in order from the input side to the output side with reference to FIG. The rotational force of an engine (not shown) is input to an input shaft 2 via a torque converter 4 in a transmission case 1. A power transmission shaft 3 is coaxially disposed on the right side of the input shaft 2 in the drawing. An oil pump 5 is mounted on the input shaft 2, and a forward clutch for switching an input rotation direction to the power transmission shaft 3 by switching a fixed element of a planetary gear mechanism 8 on the right side of the oil pump 5 in the drawing. A forward / reverse switching mechanism 9 including a mechanism 6 and a reverse brake mechanism 7 is provided. Further, the power transmission shaft 3 is provided with first and second toroidal transmission mechanisms 10 and 11 constituting two toroidal grooves, which are spaced apart from each other in the axial direction.
[0013]
A sun gear 13 rotatably supported by the input shaft 2 via a needle bearing 12 and constituting the planetary gear mechanism 8 is formed between the input shaft 2 and the power transmission shaft 3, and is formed on the sun gear 13. A loading cam 14 engaged with the claw portion 13a and rotatably supported by the power transmission shaft 3; connected to the loading cam 14 via an engagement roller 15; and connected to the power transmission shaft 3 via a ball spline 16. A supported input disk 17 is interposed. The engaging roller 15 is rotatably held by a holder 41. Therefore, the torque transmitted from the engine to the input shaft 2 is transmitted to the loading cam 14, the engaging roller 15, the input disk 17, and the ball spline 16 from the claw 13a of the sun gear 13 via the forward / reverse switching mechanism 9. The rotation is transmitted to the rotation 13.
[0014]
When the engaging roller 15 moves along the leads on these cam surfaces, a thrust in the axial direction of the power transmission shaft 3 proportional to the input torque, that is, a thrust force is generated. Further, between the loading cam 14 as the input cam and the input disk 17 as the output cam, a disc spring 42 for applying a force in a direction for separating the two and applying a preload is interposed. .
[0015]
The first toroidal transmission mechanism 10 includes an input disk 17 having a toroidal surface 17a formed on a surface away from the engagement roller 15, and a toroidal surface 18a formed on a surface facing the input disk 17; 3, a power roller (friction roller) that tiltably contacts a groove formed by an output disk 18 rotatably supported by the input disk 17 and a toroidal surface 17a of the input disk 17 and a toroidal surface 18a of the output disk 18. 29.
[0016]
The second toroidal transmission mechanism 11 has an input disk 19, an output disk 20, a power roller (friction roller) 30, and a support mechanism as in the first toroidal transmission mechanism 10, but the power transmission shaft 3 has a ball spline. An input disk 19 externally fitted via 21 is arranged on a side far from the first toroidal transmission mechanism 10, and an output disk 20 is arranged on a side near the first toroidal transmission mechanism 10.
[0017]
An output gear 22 is provided between the back surfaces of the output disks 18 and 20 facing each other. A cylindrical shaft portion 18b and 20b protruding in the axial direction from both ends of the central portion of the output gear 22 is provided. It is splined with them inside the output disks 18,20. The output gear 22 is rotatably supported by a gear housing 23 fixed to the inner peripheral wall of the transmission case 1 via a bearing 24. The output gear 22 is meshed with a counter gear 25, and the counter gear 25 is rotatably supported by the gear housing 23 via a bearing 26. One end of a counter shaft 27 is spline-coupled to the center of the counter gear 25, and the other end of the counter shaft 27 is rotatably supported by the transmission case 1 via a bearing 28. Are designed to rotate together. Therefore, the rotational force from the engine transmitted to the power transmission shaft 3 is distributed to the input disks 17, 19 of the first and second toroidal transmission mechanisms 10, 11, and the tilting of the power rollers 29, 30 described above. After being transmitted to the output disks 18 and 20 of each of the toroidal transmission mechanisms 10 and 11 at a predetermined gear ratio by the operation, they are synthesized by the output gear 22 and sequentially pass through the counter gear 25, the counter shaft 27 and the gear train 28. It is transmitted to the output shaft 33. A disc spring 43 is interposed on the rear surface of the input disk 19 of the second toroidal transmission mechanism 11, and by adjusting the tightening torque of the nut 40 screwed to the output side, the disc spring 42 is connected to the disc spring 42. The preload state of the thrust force generated between the two can be adjusted.
[0018]
Next, shift control by each of the toroidal shift mechanisms will be briefly described. FIG. 2 shows a vertical cross section of the center of the first toroidal transmission mechanism 10 facing the rear of the vehicle. Two power rollers 29, 29 facing in the drawing, arranged opposite rotational power to be transmitted between the output disk 18 and the input disk arranged on the axis O ₁ in the figure (not shown) The power rollers 29, 29 are rotatably supported by a right trunnion 46FL and a left trunnion 46FR in the drawing via an eccentric shaft 47, respectively, and the upper ends of the trunnions 46FL, 46FR are spaced apart from each other. The lower ends are connected via a lower link 52 while being connected laterally via an upper link 50.
[0019]
Among trunnion 46FL of the right in the figure, which rotatably supports the power roller 29 from the illustrated neutral position of the power roller rotation axis O ₂ intersect the input and output disks rotation axis O _1, the power roller rotation as an offset in the direction of the oscillation axis O ₃ that is perpendicular to the axis O _2, displaced in the direction of the oscillation axis O _3, and and and can tilt around a swing axis O _3.
[0020]
The upper end of the trunnion shaft 70 is bar-coupled to the lower part of the trunnion 46FL to which the lower link 52 is connected via the pin 56. The piston boss of the piston 78FL of the fluid pressure cylinder 77 is connected to the trunnion shaft 70. The piston 78FL is integrated with the trunnion 76FL via the trunnion shaft 70 by fitting the portion 78a outside and screwing and tightening the nut 82 to the male screw at the lower end. The cylinder body 60 that houses the piston 78FL defines a first fluid chamber 90a closer to the nut 82 than the piston 78FL, and defines a second fluid chamber 90b closer to the trunnion 46FL than the piston 78RL. The working fluid pressure generated by the shift control valve 64 based on the commanded gear ratio is supplied. Then, the piston 78FL is displaced by a predetermined amount in swing axis _{O 3} direction according to the pressure difference of the first and second fluid chambers 90a, 90b, swing the trunnion 76FL against the input and output disks 17 and 18 the axis O ₃ is the direction to the displacement (offset), the tilting angle of Pawarora 29 changes the direction corresponding to the shift command by the offset.
[0021]
The upper end of the trunnion shaft 70 is also bar-coupled to the lower part of the trunnion 46FR on the left side of the figure, which rotatably supports the power roller 29, via a pin 56. The piston 78FR and the precess cam 66 are integrated with the trunnion 46FR via the trunnion shaft 70 by externally fitting the piston boss portion 78a of the piston 78FR and the precess cam 66 and screwing a nut 82 into a male screw at the lower end thereof. Has been The cylinder body 60 that houses the piston 78FR defines a first fluid chamber 92a closer to the trunnion 46FR than the piston 78FR and defines a second fluid chamber 92b closer to the nut 82 than the piston 78FR. The working fluid pressure generated by the shift control valve 64 is supplied. Then, the tilt angle of the power roller 30 is changed in the same manner as in the right trunnion 46FL shown in the figure.
[0022]
Here, the the precess cam 66, guide grooves 66a that are inclined to the swing axis O ₃ direction, are formed, the displacement of the power roller 46FR engages the end of the shift link 68 is in the guide groove 66a (Offset amount and tilt amount) are fed back to the shift control valve.
[0023]
On the other hand, the second toroidal transmission mechanism 11 has the same configuration as that of the first toroidal transmission mechanism, but does not have the precess cam structure described above. In addition, in order to represent a difference from the first toroidal transmission mechanism 10, the piston is represented by reference numerals 78RL and 78RR, and the trunnion is represented by reference numerals 46RL and 46RR.
[0024]
During forward running, the fluid pressure in the first fluid chambers 90a and 92a of each of the fluid pressure cylinders 77 is increased by the supply pressure from the shift control valve, and the fluid pressure in the second fluid chambers 90b and 92b is relatively increased. When generating a differential pressure therebetween to lower the piston 78FR, 78FL (78RR, 78RL) is a stroke in solid arrows _{S U} along the swing axis _{O 3} directions. Thus, the power axis O ₂ of the roller 29 and displaced to the axis O ₁ of the input and output disks, as a result, for example, deviation occurs in the input direction from the rotational direction and the input disk 17 of the power roller 29, this deviation force components the power rollers 29 trunnion 46FL, by tilting around the swivel axis O ₃ of 46FR, thereby the contact radius varies with the power rollers 29 and the input disk 17 and output disk 18, the gear ratio Change to high side and upshift. Conversely, when the fluid pressure in the first fluid chambers 90a and 92a of each of the fluid pressure cylinders 77 is reduced and the fluid pressure in the second fluid chambers 90b and 92b is relatively increased to generate a pressure difference between the two. , The pistons 78FR, 78FL stroke in the direction of the dashed arrow _SD, and as a result, the power roller 29 tilts in the opposite direction to the above, changes to the low side, and downshifts.
[0025]
Incidentally, it is desired that the fluid pressure supplied to each of the fluid pressure cylinders 77 is as low as possible. When decreasing such supply fluid pressure, simultaneously with the fluid pressure cylinder 77, such that the thrust of the oscillation axis O ₃ directions required to obtain, the cross-sectional area, i.e. the piston 78FL~ It becomes necessary to increase the cross-sectional area of 78RR.
[0026]
On the other hand, as described above, the power roller 29, which is sandwiched between the input / output disks 17 and 18 by a thrust force corresponding to the input torque from the loading cam 14, has the right and left sides in FIG. A large force is exerted that pushes out. In order to keep each power roller 29 rotatably supported by this large force, it is necessary to provide sufficient lubrication to the part supporting the power roller 29 on the back surface. For details of the supporting portions that require specific lubrication, refer to, for example, Japanese Patent Application Laid-Open No. 8-291850. In the present embodiment, for example, the power roller 29 shown in FIG. Needle bearing 61 for supporting the power transmission shaft 29, a thrust needle bearing 62 for supporting the thrust load of the power roller 29 (different from the thrust load of the power transmission shaft 3), a ball bearing 63 therebetween, and the eccentric shaft 47 Needle bearing 64 and the like for rotatably supporting 46FL and 46FR.
[0027]
In such a bearing, a system in which a lubricating fluid is applied from the outside thereof cannot provide a sufficient lubricating effect. Therefore, a system in which the lubricating fluid is directly injected to each lubricating portion through, for example, the inside of the trunnions 46FL and 46FR is used. Therefore, in the present embodiment, due to the layout, the boss portions 78a of the pistons 78FL, 78FR of the trunnions 46FL, 46FR constituting the support mechanism, which are opposite to the power roller 29 with the fluid pressure cylinder 77 interposed therebetween, are provided. The formed grooves 71FL and 71FR are used as lubricating fluid supply sites. The lubricating fluid supplied to the grooves 71FL, 71FR flows into the gap 84 between the boss 78a and the trunnion shaft 70 through the fluid hole 83 formed in the grooves 71FL, 71FR. Further, a part of the fluid is supplied from the fluid groove 85 formed on the outer peripheral surface of the trunnion shaft 70 to the needle bearing 64 through the oblique hole 86 and the vertical hole 87 formed in the trunnions 46FL and 46FR. . The remaining part is supplied from the vertical hole 87 of the trunnions 46FL, 46FR to the thrust needle bearing 62 through the horizontal hole 88 communicating therewith. Further, the remainder flows into a fluid hole 89 drilled inside the eccentric shaft 47, and is communicated with the injection hole 93 to the ball bearing 63, and the injection hole 94 to the needle bearing 61. , Distributed and supplied respectively.
[0028]
As described above, since a sufficient flow rate of the lubricating fluid is required at the supporting portion of the power roller 29, when a fluid path for securing the lubricating fluid flow is formed in the cylinder body 60, the pistons 78FL and 78FR are cut off. The layout is mutually restricted depending on the area.
[0029]
Therefore, in this embodiment, as shown in FIG. 3, of the pre-Symbol cylinder body 60, the right and below the fluid pressure cylinder 77 of the right in the figure shown in FIG. 2, the lubricating fluid (in this embodiment , A common lubricating fluid passage 72 for collectively supplying the same fluid as that supplied to each of the fluid pressure cylinders 77 is formed. Reference numeral 25a in the drawing denotes a housing that houses the counter gear 25. Then, the lubricating fluid is supplied only to the groove portion 71RR of the trunnion 46RR farthest from the common lubricating fluid passage 72 by the pipe 48RR rising from the common lubricating fluid passage 72, and to the other trunnions 46FL to 46RL. The lubricating fluid is supplied from the fluid passages 49FL to 49RL formed in the cylinder body 60.
[0030]
By doing so, it is possible to secure the supply flow rate of the lubricating fluid by increasing the inner diameter of the pipe 48RR at least for the trunnion 46RR farthest from the common lubricating fluid path 72. The cross-sectional area of the lubricating fluid supply passages 49FL-49RL to the other trunnions 46FL-46RL is reduced by the amount that the lubricating fluid supply to the trunnion 46RR furthest from the common lubricating fluid passage 72, which is poor in performance, need not be considered. Therefore, the influence on the cross-sectional area of the hydraulic cylinder 77 is reduced by that much, and the cross-sectional area of the hydraulic cylinder 77 can be increased to reduce the supply fluid pressure. This also makes it possible to reduce the size of a drive source such as a pump, or to reduce the driving force to improve fuel efficiency.
[0031]
Conventionally, a lubricating fluid path to each of the trunnions 46FL to 46RR is formed in the cylinder body 60 only to reduce the labor and cost of piping, and therefore the cross-sectional area of each hydraulic cylinder 77 is limited. As a result, there is a limit to lower the supply fluid pressure. Further, even if the lubricating fluid passage is formed in the relatively narrow cylinder body 60, there is a limit for adjusting the flow resistance and the cross-sectional area. Therefore, for example, the trunnion 46RR farthest from the common lubricating fluid passage 72 has the closest trunnion. There is also a problem that the supply flow rate of the lubricating fluid is reduced as compared with 46FL.
[0032]
FIG. 4 shows a reference example of a lubricating structure for a toroidal-type continuously variable transmission according to the present invention. In this example, four pipes 48 are raised from the common lubricating fluid passage 72 and are directly formed at the lower ends of the trunnions 46FL to 46RR so as not to interfere with the counter gear housing 25a. It connects with 71FL-71RR, and both, namely, the common lubrication fluid path 72 and the groove part 71FL-71RR are connected. The inner diameters of the pipes 48FL to 48RR are adjusted such that the inner diameter of the pipe 48RR to the trunnion 46RR farthest from the common lubricating fluid passage 72 is increased and the inner diameter of the pipe 48FL to the nearest trunnion 46FL is reduced. By doing so, for example, when the lubricating fluid pressure in the common lubricating fluid path 72 is equal, the supply flow rate of the lubricating fluid to each of the trunnions 46FL to 46RR, that is, the supporting portion of the power roller 29 is made uniform. did. It should be noted that such adjustment of the supply flow rate of the lubricating fluid can be dealt with by, for example, changing the flow resistance of an orifice provided in the pipe.
By doing so, it is not necessary to form a fluid passage other than the common lubricating fluid passage 72 in the cylinder body 60, so that the cross-sectional area of each of the fluid pressure cylinders 77 can be increased, and as a result, It is also possible to reduce the supply fluid pressure to reduce the size of a drive source such as a pump, or to reduce the drive force to improve fuel efficiency. Further, by adjusting the inner diameters of the pipes 48FL to 48RR or adjusting the flow resistance, the supply flow rate of the lubricating fluid to each of the trunnions 46FL to 46RR, that is, the power roller 29 can be made uniform.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing an example of a toroidal type continuously variable transmission.
FIG. 2 is a longitudinal sectional view showing a first toroidal transmission mechanism of FIG. 1;
3A and 3B show one embodiment of a trunnion lubrication structure used in the toroidal continuously variable transmission shown in FIG. 1, wherein FIG. 3A is a longitudinal sectional view and FIG. 3B is a bottom view.
4A and 4B show a reference example of a trunnion lubrication structure used in the toroidal continuously variable transmission shown in FIG. 1, wherein FIG. 4A is a longitudinal sectional view and FIG. 4B is a bottom view.
[Explanation of symbols]
1 is a transmission case 3 is a power transmission shaft 10 is a first toroidal transmission mechanism 11 is a second toroidal transmission mechanism 17, 19 is an input disk 18, 20 is an output disk 29 is a power roller (friction roller)
30 is a power roller (friction roller)
46FL to 46RR are trunnions (support mechanism)
48FL-48RR is a pipe 49FL-49RR is a fluid path 61 is a needle bearing (supporting portion)
62 is a needle bearing (lubricated part)
63 is a ball bearing (lubricated part)
64 is a needle bearing (lubricated part)
71FL to 71RR are grooves (lubricating fluid supply sites)
72 common lubricant path 77 is a fluid pressure cylinder 78FL~78RR piston O ₁ power roller rotation axis O ₃ rotation axis O ₂ of the input and output discs are swing axis

Claims (2)

A plurality of friction rollers disposed between opposed rotatable input disks and output disks, a plurality of support mechanisms for individually supporting these friction rollers in a tiltable manner, and for tilting the friction rollers. A plurality of fluid pressure cylinders for individually driving each of the support mechanisms; and a lubricating fluid for lubricating a support portion of each of the friction rollers through the inside of each of the support mechanisms, the friction roller being sandwiched between the fluid pressure cylinders. A common lubricating fluid supply portion is provided in a cylinder body constituting the fluid pressure cylinder, and the predetermined lubricating fluid is supplied to a supporting mechanism furthest from the common lubricating fluid passage. The lubricating fluid supply part has a piping structure that rises from the common lubricating fluid passage, and the predetermined lubricating fluid supply part of the other support mechanism has a predetermined lubrication flow of each support mechanism. Lubrication structure of the toroidal type continuously variable transmission, characterized in that up to supply site separate lubricating fluid passage formed in the cylinder body from the common lubricant path. 2. A lubricating fluid passage extending from the common lubricating fluid passage to the farthest support mechanism beyond the counter gear housing, wherein a counter gear housing exists between the plurality of hydraulic cylinders. 3. A lubricating structure for a toroidal-type continuously variable transmission according to claim 1.

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