JP2000145919A - Continuously variable transmission of infinite transmission gear ratio - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance productivity by simplifying a structure for supplying hydraulic pressure to the clutch of a unit output shaft. SOLUTION: This continuously variable transmission of infinite transmission gear ratio is provided with a continuously variable transmission 2 and a constant transmission 3 connected to unit input shafts respectively, a planetary gear mechanism, a power circulation mode clutch 9, a direct connection mode clutch 10, a chain 40 for transmitting driving force to the sun gear 5a of the planetary gear mechanism from the continuously variable transmission 2 and a casing 14 for journalling the unit input shafts 1a, 1b and a unit output shaft 6. An oil distributing wall 30 for supplying hydraulic pressure to the power circulation mode clutch 9 is intervened between the power circulation mode clutch 9 of the unit output shaft 6 and the gear 3b of the constant transmission 3.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an infinitely variable transmission with an infinite transmission ratio used in vehicles and the like.

[0002]

2. Description of the Related Art A belt-type or toroidal-type continuously variable transmission is conventionally known as a vehicle transmission. In order to further expand the shift range of such a continuously variable transmission, a continuously variable transmission is known. There is known a continuously variable transmission with an infinitely variable transmission ratio in which the transmission ratio can be controlled to infinity by combining a constant transmission and a planetary gear mechanism, for example, Japanese Patent Application No. 9-29080 proposed by the present applicant. and so on.

[0003] This is a planetary gear mechanism in which a continuously variable transmission and a constant transmission (reduction gear) are connected in parallel to a unit input shaft connected to an engine, and their outputs are arranged on a unit output shaft. The output side of the continuously variable transmission is connected to the sun gear of the planetary gear mechanism via the continuously variable transmission output gear train, and the output shaft of the constant transmission is connected to the carrier of the planetary gear mechanism via the power circulation mode clutch. Respectively.

[0004] The continuously variable transmission output shaft connected to the sun gear
While being connected to the unit output shaft, which is the output shaft of the infinitely variable speed ratio transmission, via the direct connection mode clutch, the ring gear of the planetary gear mechanism is also connected to the unit output shaft.

As shown in FIG. 7, a case 113 is disposed on the unit output shaft 6 between the constant transmission output gear 103b and the transmission output gear 7.

[0006] Inside the case 113 (left side in the figure), bearings 132a, 1a of the constant transmission output gear 103b are provided.
32b is formed, and an oil passage 113 for supplying hydraulic pressure to the power circulation mode clutch 109 is provided inside the bearing support portion 113b.
c is formed, and the oil passage 15 formed inside the case 113 is formed.
The power circulation mode clutch 109 is driven by the hydraulic pressure supplied from zero.

[0007]

However, in the above-mentioned conventional continuously variable transmission with an infinite transmission ratio, the constant transmission output gear 103b is attached to the bearing support portion 113b of the case 113 in an assembling process or the like. Bearing support 11
3b is engaged with the inner circumference of the clutch drum 109a while the constant transmission output gear 103b and the clutch drum 1 are engaged.
09a must be spline-connected, and case 11
3, a plurality of positioning operations are performed at the same time, and there is a problem that the workability of the assembling process is reduced.

The present invention has been made in view of the above problems, and has as its object to improve the productivity by simplifying the structure for supplying hydraulic pressure to the clutch of the unit output shaft.

[0009]

According to a first aspect of the present invention, there is provided a continuously variable transmission and a fixed transmission which are respectively connected to a unit input shaft and a unit output shaft which is provided on an output shaft of the continuously variable transmission. A connected sun gear, a carrier connected to the output shaft of the fixed transmission, and a ring gear connected to the unit output shaft.
A power transmission mode clutch interposed in the middle of a transmission path to an output shaft and a carrier of the constant transmission, and a sun gear and a carrier of the planetary gear mechanism.
A direct-coupled mode clutch interposed between two elements of the ring gear, a chain for transmitting a driving force from the continuously variable transmission to the sun gear, and mounted in parallel with the unit input shaft and the unit output shaft In addition, in the continuously variable transmission having an infinitely variable gear ratio, comprising a casing that supports the unit input shaft and the unit output shaft, the constant transmission includes gears provided on the unit input shaft and the unit output shaft, respectively. And an output shaft arranged coaxially with the unit output shaft and coupled to a gear. Between the gear on the unit output shaft side and the power circulation mode clutch, an oil chamber of the power circulation mode clutch is provided. An oil distribution wall having a communicating oil passage formed therein is interposed.

In a second aspect based on the first aspect, the oil distribution wall is fastened to the casing via fastening means.

[0011] The third invention is the first or the second invention.
In the invention, the oil distribution wall communicates with an oil chamber of the power circulation mode clutch via an oil passage provided in a drum support constituting an inner peripheral side of the power circulation mode clutch.

In a fourth aspect based on the third aspect, the oil distribution wall is in sliding contact with the outer periphery of the drum support, and the oil passage of the drum support is formed in an annular shape formed on the inner periphery of the oil distribution wall. Communicate with oilway.

In a fifth aspect based on the second aspect, the oil distribution wall is fastened to the casing via a plurality of projections projecting from the outer periphery.

[0014]

According to a first aspect of the present invention, when assembling a continuously variable transmission with an infinite transmission ratio, the output shaft of the constant transmission, the oil distribution wall, and the power circulation before the unit output shaft is inserted into the casing. Mode clutch, planetary gear mechanism, continuously variable transmission output shaft,
Insert the direct-coupled mode clutch in this order and assemble it as a sub-assembly. Then, insert the unit output shaft, which has been made into the sub-assembly, from the bearing to the inner periphery of the casing,
After the chain is inserted around the end portion and wound around the sun gear side, the oil distribution wall is connected to the inner periphery of the casing or the like, and then the gear is fastened to the output shaft of the fixed transmission. Next, the chain is wound around the continuously variable transmission and assembled to the casing. Accordingly, since the oil distribution wall is disposed between the gear of the fixed transmission and the power circulation mode clutch, it is possible to sequentially assemble each part, and as in the above-described conventional example, a plurality of parts are provided on the inner periphery of the casing. It is not necessary to perform the positioning work at the same time, and the workability in the assembling process is greatly improved, and the productivity can be improved.

In the second invention, the oil distribution wall is connected to the inner periphery of the casing by the fastening means. Therefore, after the unit output shaft is positioned on the inner periphery of the casing, the connection between the oil distribution wall and the casing is made. Can be performed, and the assembling work can be facilitated.

According to a third aspect of the present invention, since the supply of the hydraulic pressure from the oil distribution wall to the power circulation mode clutch is performed through an oil passage provided in the drum support, the output coupled with the gear of the constant transmission is provided. It is not necessary to form an oil passage in a shaft or the like, and the strength of the power transmission path from the constant transmission to the power circulation mode clutch can be easily secured.

According to a fourth aspect of the present invention, the inner periphery of the oil distribution wall is slid in contact with the outer periphery of the drum support, and the oil passage of the drum support receives the supply of hydraulic pressure from the annular oil passage slid in contact with the outer periphery. In addition, the oil distribution wall can be arranged while suppressing an increase in the axial dimension, and the reduction in size and weight can be promoted.

In the fifth invention, the oil distribution wall is fastened to the casing via a plurality of projections projecting from the outer periphery.
While preventing the unit output shaft from interfering with other components such as the continuously variable transmission due to the gap between the convex portions, the mounting strength can be secured, and the oil distribution wall is formed by forming an oil passage in each convex portion. It is possible to easily secure the total area of the flow path.

[0019]

An embodiment of the present invention will be described below with reference to the accompanying drawings.

FIGS. 1 to 4 show an example in which the present invention is applied to an infinitely variable speed ratio continuously variable transmission using a toroidal type continuously variable transmission.

As shown in FIGS. 1 and 2, the infinitely variable transmission has a unit input connected to a crankshaft (not shown) of an engine via a flywheel and a damper (both not shown). A continuously variable transmission 2 whose gear ratio can be continuously changed and a constant transmission 3 (reduction gear) composed of gears 3a and 3b are connected in parallel to the shafts 1a and 1b, and their outputs are connected. The shafts 4 and 3c are coaxially arranged on the unit output shaft 6 and connected by a planetary gear mechanism 5. The output shaft 4 of the continuously variable transmission 2 is connected to the sun gear 5a of the planetary gear mechanism 5 and the fixed transmission 3 The output shaft 3c is connected to the carrier 5b of the planetary gear mechanism 5 via the power circulation mode clutch 9.

The continuously variable transmission output shaft 4 connected to the sun gear 5a receives the driving force of the continuously variable transmission 2 from the sprocket 4a and the chain 40 and receives the driving force of the infinitely variable transmission through the direct connection mode clutch 10. The ring gear 5 c is also connected to the unit output shaft 6 while being connected to the unit output shaft 6 which is the output shaft.

A transmission output gear 7 is provided on the right side of the unit output shaft 6 in the drawing, and the transmission output gear 7 meshes with the final gear 12 of the differential gear 8 and is connected to the drive shaft 11 a connected to the differential gear 8. , 11b
The driving force is transmitted at a predetermined total reduction ratio.

As shown in FIG. 1, the continuously variable transmission 2 is a double-cavity half-toroidal type that sandwiches and presses the power rollers 20, 20 with two sets of input disks 21 and output disks 22, respectively. The output sprocket 2a interposed between the pair of output discs 22 is formed on the continuously variable transmission output shaft 4 of the unit output shaft 6 arranged in parallel with the unit input shafts 1a and 1b via the chain 40. Connects to sprocket 4a.

As shown in FIG. 2, the unit input shafts 1a and 1b are arranged coaxially and connected in the rotational direction via a loading cam device 23 of the continuously variable transmission 2. , The unit input shaft 1a is a flywheel,
The unit input shaft 1b is connected to a crankshaft of the engine via a damper, and forms a gear 3a of the constant transmission 3. The unit input shaft 1b is connected to two sets of input disks 21 and 21 to receive an input from the unit input shaft 1a. The power rollers 20, 20 shown in FIG. 1 are nipped and pressed between the input and output disks by the axial pressing force generated by the loading cam device 23 according to the torque.

In this continuously variable transmission with an infinite transmission ratio, the power circulation mode clutch 9 is disengaged while the direct connection mode clutch 10 is engaged to transmit the driving force in accordance with the speed ratio of the continuously variable transmission 2. By disengaging the direct-coupled mode clutch 10 while engaging the power circulation mode clutch 9, the continuously variable transmission 2 has an infinite transmission ratio according to the difference in transmission ratio between the continuously variable transmission 2 and the fixed transmission 3. And a power circulation mode in which the unit speed ratio (speed ratio between the unit input shaft 1a and the unit output shaft 6) is controlled almost continuously from a negative value to a positive value including infinity. Can be.

The unit input shafts 1a and 1b, the unit output shaft 6 and the drive shafts 11a and 11b are arranged in parallel on the inner periphery of the casing 14, and as shown in FIGS. The output gear 7 and the final gear 12 and the gear 3a and the gear 3b of the fixed transmission 3 are arranged so as to be shifted in the axial direction, and the outer periphery of the large-diameter gear 3b is close to the differential gear 8.

Next, the gear 3b of the fixed transmission 3 is formed in an annular shape, and the inner periphery of the gear 3b is formed to have an inner diameter through which the unit output shaft 6 and the transmission output gear 7 can be inserted. 3b is a flange portion 3 of the output shaft 3c via a bolt.
d.

As shown in FIG. 2, an oil retainer 60, a direct mode clutch 10, a sprocket 4a, a planetary gear mechanism 5, a power circulation mode clutch 9, The oil wall 30, the output shaft 3c and the gear 3b of the fixed transmission 3, and the transmission output gear 7 are sequentially arranged.

An oil passage 61 for supplying oil pressure to the direct connection mode clutch 10 is formed inside the oil retainer 60, and communicates with an oil passage 13 formed inside the casing 14 so as to communicate with a hydraulic pressure from a hydraulic supply source (not shown). To the direct connection mode clutch 10.

On the other hand, the supply of oil pressure to the power circulation mode clutch 9 is performed via an annular oil distribution wall 30 interposed between the gear 3b of the fixed transmission 3 and the power circulation mode clutch 9.

First, as shown in FIG. 3, the connection between the gear 3b of the fixed transmission 3 and the power circulating mode clutch 9 is performed via an output shaft 3c arranged coaxially with the unit output shaft 6. The output shaft 3c has a flange 3d formed on the transmission output gear 7 side, and the gear 3b is fastened to the end face of the flange 3d, while the other end is engaged with the inner periphery of the power circulation mode clutch 9. A cylindrical portion 3e is formed, and a drum support 94 for supporting the clutch drum 90 on the inner periphery is connected to the cylindrical portion 3e via a spline 51.

The output shaft 3c has a bearing 18 interposed between the inner periphery of the flange portion 3d and the outer periphery of the unit output shaft 6.
And a roller bearing 50 interposed between the inner periphery of the drum support 94 and the outer periphery of the unit output shaft 6 so as to be rotatably supported relative to the unit output shaft 6.

The clutch drum 90 of the power circulation mode clutch 9 is formed of a cylindrical member having an inverted L-shaped cross section. The base end having a small inner diameter is connected to the outer periphery of the drum support 94, and the other end having a larger inner diameter is The inner 96 connected to the carrier 5b of the planetary gear mechanism 5 is inserted.

The clutch disc 93 provided on the outer circumference of the inner 96 and the clutch plate 92 provided on the inner circumference of the clutch drum 90 are arranged so that the piston 91 slides on the inner circumference of the clutch drum 90 and the outer circumference of the drum support 94 in the axial direction. By engaging and disengaging according to the displacement, the engagement and release of the power circulation mode clutch 9 are performed.

The flange 3 to which the gear 3b is fastened
As shown in FIG. 4, an oil distribution wall 30 in which an annular oil passage 34 is formed is interposed on the outer periphery of the drum support 94 between d and the base end of the clutch drum 90.

The oil distribution wall 30 is formed of an annular member that slides on the outer periphery of the drum support 94, and as shown in FIG.
The annular oil passage 34 opens toward the outer periphery of the drum support 94.

As shown in FIG. 3, one end of an oil passage 95 having a substantially L-shaped cross section is opened at a predetermined position on the outer periphery of the drum support 94, and communicates with the annular oil passage 34. On the other hand, the other end of the oil passage 95 opens on the side surface of the drum support 94 facing the piston 91. An oil chamber 97 is defined by the inner circumferences of the drum support 94 and the clutch drum 90 and the end face of the piston 91, and the piston 91 rotates in accordance with the oil pressure applied to the oil chamber 997 from the annular oil passage 34 via the oil passage 95. In this direction, the power circulation mode clutch 9 is engaged and released.

The oil distribution wall 30 provided with the annular oil passage 34 is shown in FIG.
As shown in the figure, a plurality of protrusions 31 are provided on the outer periphery to connect with a predetermined inner circumference of the casing 14, and through holes 33 are formed in the protrusions 31 so that positioning is performed. A pin 36 projects in the axial direction and engages with a bracket (not shown) formed on the inner periphery of the casing 14,
The oil distribution wall 30 is positioned in the circumferential direction by the positioning pins 36, and the oil distribution wall 30 is connected to the inner periphery of the casing 14 by bolts (not shown) inserted into the through holes 33. In FIG. 2, the oil distribution wall 30 is inserted from the right side in the drawing, and the side surface of the projection 31 is engaged with a bracket (not shown).

Further, an annular oil passage 34 is provided inside the convex portion 31.
And an oil passage 32 extending in the radial direction is formed. The oil passage 32 opens as a communication passage 35 at a predetermined position on the side surface of the convex portion 31 and opens to a bracket of the casing 14 (not shown). In communication with the oil passage, the oil pressure from the oil pressure supply source is supplied to the annular oil passage 34.

The operation will be described next.

When assembling the transmission, first, the bearing 18, the output shaft 3 c of the fixed transmission 3,
The power circulation mode clutch 9, the planetary gear mechanism 5, the sprocket 4a, the direct connection mode clutch 10, the oil retainer 6, in which the oil distribution wall 30 is pre-assembled on the outer periphery of the drum support 94.
After inserting in the order of 0, the lock nut 39 is fastened to the end 6A, and the unit output shaft 6 is assembled as a sub-assembly.

At this time, since the annular oil passage 34 is opened facing the inner periphery of the oil distribution wall 30, it is not necessary to position the drum support 94 in the oil passage 95 in the circumferential direction, and it is easily assembled. be able to.

Then, the lock nut 39 is connected to the output shaft 3c.
The unit output shaft 6 assembled as a sub-assembly is inserted from the end 6A side to the inner periphery from the casing 14 from the right side shown in FIG.

While the unit output shaft 6 is inserted in the axial direction, the chain 40 is wound around the sprocket 4a, and the oil retainer 60 is brought into contact with the inner periphery of the casing 14 and fastened.

At this time, since the convex portion 31 protruding from the outer periphery of the oil distribution wall 30 also engages with the bracket on the inner periphery of the casing 14, after positioning in the circumferential direction by the positioning pin 36, it is inserted into the through hole 33. Fasten with bolts. Due to the connection between the oil distribution wall 30 and the inner circumference of the casing 14, the oil passage on the casing 14 side is connected via the oil passage 32 provided inside the oil distribution wall 30, the annular oil passage 34, and the oil passage 95 provided on the drum support 94. Oil chamber 9 of power circulation mode clutch 9
Connect to 7.

Next, a chain 4 is attached to the output sprocket 2a.
The continuously variable transmission 2 around which 0 is wound is assembled into the casing 14.

Finally, the gear 3b of the fixed transmission 3 is connected to the unit output shaft 6 assembled to the casing 14 by the output shaft 3.
c, the final gear 12 is fastened to the differential gear 8 while meshing with the transmission output gear 7, and the unit input shaft 1 of the continuously variable transmission 2 is engaged.
2a, the unit input shaft 1b is engaged in the rotation direction via the loading cam device 23, and the gear 3a of the fixed transmission 3 is meshed with the gear 3a, and then the right casing 14 in FIG. Then the assembly is completed.

As described above, since the oil distribution wall 30 for supplying oil pressure to the power circulation mode clutch 9 is disposed on the drum support 94 between the gear 3b of the fixed transmission 3 and the clutch drum 90, the components are sequentially assembled. This eliminates the need to simultaneously perform a plurality of positioning operations on the inner periphery of the casing 14 as in the above-described conventional example, greatly improving workability in the assembling process and improving productivity. It becomes possible.

Since the oil passage communicating from the oil distribution wall 30 to the oil chamber 97 is formed inside the drum support 94, the oil passage is formed on the output shaft 3c and the like connected to the gear 3b of the fixed transmission 3. Therefore, the strength of the power transmission path from the fixed transmission 3 to the power circulation mode clutch 9 can be easily ensured, and the oil passage 95 inside the drum support 94 is substantially in the oil chamber from the axial direction. Since the oil pressure is supplied to the oil passage 97 while being supplied from the annular oil passage 34 slidably contacting at the outer periphery, the oil distribution wall 30 can be arranged while suppressing an increase in the axial dimension, and it is small and lightweight. Can be promoted.

Further, the connection between the oil distribution wall 30 and the inner periphery of the casing 14 is performed by a plurality of protrusions 31 protruding from the outer periphery of the oil distribution wall 30, so that the gap between the protrusions 31 allows the stepless connection. The mounting strength can be ensured while avoiding interference with other components such as the transmission 2, and the oil passage 32 is formed in each convex portion 31 to easily secure the total flow passage area inside the oil distribution wall 30. It is possible to do.

FIGS. 5 and 6 show a second embodiment, in which the oil distribution wall 30 of the first embodiment is replaced by an oil distribution wall 130, and other configurations are the same as those of the first embodiment. It is.

The oil distribution wall 130 is provided between the disk portion 13 held between the flange portion 3d of the output shaft 3c and the drum support 94.
0a, the cylindrical portion 3e of the output shaft 3c and the drum support 94.
An oil passage 134 is formed in the cylindrical portion 130b in the axial direction, and the oil passage 134 is formed at a predetermined position in the cylindrical portion 130b.
A communication passage 137 that opens in the outer periphery of is formed in the radial direction,
The communication passage 137 is formed to penetrate in the radial direction from the inner periphery of the drum support 94 and communicates with an oil passage 98 communicating with the oil chamber 97. Note that bearings 53 and 54 are interposed between the disk portion 130a, the flange portion 3d, and the drum support 94, respectively.

FIG. 6 shows the outer periphery of the disk portion 130a.
As shown in FIG. 5, in order to connect the oil distribution wall 130 to a predetermined inner periphery of the casing 14, a plurality of convex portions 131 are protrudingly provided on the outer periphery, and a through hole 133 is formed through the convex portion 131. At the same time, a positioning pin 136 protrudes in the axial direction, and engages with a bracket (not shown) formed on the inner periphery of the casing 14 to position the oil distribution wall 130 in the circumferential direction by the positioning pin 136. Done, through-hole 13
The oil distribution wall 13 is provided by bolts (not shown)
0 is connected to the inner periphery of the casing 14. In addition, the oil distribution wall 130 is inserted from the right side in FIG.
The side surface of 31 is engaged with a bracket (not shown).

Further, an oil passage 132 is formed inside the protruding portion 131 and communicates at one end with the oil passage 134 and extends substantially in the radial direction.
Is opened as a communication passage 135 at a predetermined position on a side surface of the casing 14, communicates with an oil passage (not shown) opened in a bracket of the casing 14, and supplies a hydraulic pressure from a hydraulic supply source to an axial oil passage 134 via an oil passage 132. I do.

In this case, when assembling the unit output shaft 6 as a sub-assembly, the cylindrical portion 1e of the oil distribution wall 130 is transferred to the cylindrical portion 3e of the output shaft 3c constituting the fixed transmission 3.
The inner periphery of the disc 30b is engaged from the left side of FIG.
Oil distribution wall 1 on output shaft 3c until abuts against flange 3d.
Insert 30.

Then, while the drum support 94 is engaged with the spline 51, the inner periphery of the drum support 94 is engaged with the outer periphery of the cylindrical portion 130b of the oil distribution wall 130, and in FIG. It may be inserted until the bearing 52 is sandwiched between the oil distribution wall 130 and the disk portion 130a.

At this position, the cylindrical portion 130 of the oil distribution wall 130
b and the power circulation mode clutch 9
The oil passages 98 are set so as to communicate with each other, so that positioning can be easily performed and productivity can be improved.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram of a continuously variable transmission with an infinite gear ratio showing an embodiment of the present invention.

FIG. 2 is a sectional view of a main part of the continuously variable transmission with an infinite speed ratio.

FIG. 3 is a sectional view of a main part of an output shaft of the power circulation mode clutch and the constant transmission.

FIG. 4 is a schematic side view of the continuously variable transmission with an infinite speed ratio.

FIG. 5 is a sectional view of a main part of a power circulation mode clutch and an output shaft of a constant transmission, showing a second embodiment.

FIG. 6 is a schematic side view of the continuously variable transmission with infinite transmission ratio.

FIG. 7 is a sectional view of a main part of a power circulation mode clutch and an output shaft of a constant transmission, showing a conventional example.

[Explanation of symbols]

 1a, 1b Unit input shaft 2 Continuously variable transmission 3 Constant transmission 5 Planetary gear mechanism 6 Unit output shaft 9 Power circulation mode clutch 10 Direct connection mode clutch 14 Casing 30 Oil distribution wall 31 Convex portion 32 Oil passage 33 Through hole 34 Ring oil Path 35 Communication path 36 Positioning pin 90 Clutch drum 91 Piston 92 Clutch plate 93 Clutch disk 94 Drum support 95 Oil path 97 Oil chamber 98 Oil path 130 Oil distribution wall 130a Disk part 130b Cylindrical part 131 Convex part 132 Oil path 133 Through hole 134 Oil passage 135 Communication passage 136 Positioning pin 137 Communication passage

 ──────────────────────────────────────────────────続 き Continued on the front page F-term (reference) 3J028 EA07 EA08 EA09 EB10 EB16 EB35 EB37 EB42 EB50 EB66 FA06 FA51 FA57 FB06 FC13 FC23 FC63 GA01 HA14 HA16 HA32 3J051 AA03 BA03 BB01 BD02 BE09 CB04 AB01 AC01 AB01 BB46 CA10 CC16 CD25 XA03 XA08

Claims (5)

[Claims] 1. A continuously variable transmission and a constant transmission respectively connected to a unit input shaft, a sun gear disposed on a unit output shaft and connected to an output shaft of the continuously variable transmission, and an output of the constant transmission. A planetary gear mechanism including a carrier connected to a shaft and a ring gear connected to a unit output shaft; a power circulation mode clutch interposed in a transmission path to the output shaft and the carrier of the constant transmission; A direct-coupled mode clutch interposed between two elements of a sun gear, a carrier, and a ring gear of the planetary gear mechanism; a chain for transmitting a driving force from the continuously variable transmission to the sun gear; And a casing in which the unit input shaft and the unit output shaft are supported in parallel with the unit output shaft and the casing is supported. The constant transmission is constituted by a gear provided on the unit input shaft and the unit output shaft, and an output shaft provided coaxially with the unit output shaft and connected to the gear. An infinite transmission ratio transmission having an oil distribution wall formed therein and an oil passage communicating with an oil chamber of the power circulation mode clutch interposed between the power circulation mode clutch and the power circulation mode clutch. 2. The continuously variable transmission according to claim 1, wherein the oil distribution wall is fastened to the casing via fastening means. 3. The power distribution mode clutch according to claim 1, wherein the oil distribution wall communicates with an oil chamber of the power circulation mode clutch via an oil passage provided in a drum support constituting an inner peripheral side of the power circulation mode clutch. Or a continuously variable transmission with an infinite transmission ratio according to claim 2. 4. The oil distribution wall is in sliding contact with an outer periphery of a drum support, and an oil passage of the drum support communicates with an annular oil passage formed on an inner periphery of the oil distribution wall. The infinitely variable transmission according to any one of the preceding claims. 5. The continuously variable transmission according to claim 2, wherein the oil distribution wall is fastened to the casing via a plurality of projections projecting from an outer periphery.