JP3456300B2 - Toroidal type continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [0001] BACKGROUND OF THE INVENTION 1. Field of the Invention
The transmission can be used, for example, as a transmission for automobiles or in various industries.
Used as a transmission for industrial machinery. [0002] 2. Description of the Related Art As a transmission for an automobile,10 to 11To
The use of a toroidal-type continuously variable transmission as outlined
Is being studied. This toroidal type continuously variable transmission is, for example,
As disclosed in Japanese Utility Model Publication No. 62-71465,
Input side disk (first disk) 2 concentric with input shaft 1
Of the output shaft 3 concentrically arranged with the input shaft 1.
Fix the output disk (second disk) 4 to the end
I have. Inside the casing containing the toroidal type continuously variable transmission
Side, there is a twist position with respect to the input shaft 1 and the output shaft 3.
Trunnion swinging about pivots 5 and 5
6, 6 are provided. [0003] Each trunnion 6, 6 is placed on the outer surface of both ends.
The pivots 5, 5 are provided. In addition, each trunnion 6, 6
The center part supports the base ends of the displacement shafts 7, 7,
Swing each trunnion 6, 6 around 5, 5
Allows the inclination angle of each displacement shaft 7, 7 to be adjusted freely.
I have. Of the displacement shafts 7, 7 supported by the respective trunnions 6, 6
Power rollers 8 and 8 are rotatably supported around the
I have Then, each of the power rollers 8, 8 is
It is sandwiched between the force side and output side disks 2 and 4. The input and output disks 2, 4 are mutually
The opposing inner surfaces 2a, 4a each have a cross section
Form a concave surface obtained by rotating an arc around axis 5
ing. And each power roller formed on the spherical convex surface
The peripheral surfaces 8a, 8a of the 8, 8 correspond to the inner side surfaces 2a, 4a.
In contact. [0005] Between the input shaft 1 and the input side disk 2
Is provided with a loading device 9 of a loading cam type.
The input side disk 2 is connected to the output side disk by the device 9.
, And can be elastically pressed toward the hook 4. This pressing device
The device 9 includes a cam plate 10 that rotates with the input shaft 1 and a retainer.
11 (for example, four) rollers 1 held by
2 and 12. One side of the cam plate 10
surface(10 to 11On the left side of the circle)
A cam surface 13 is formed on the input side disk 2.
Outer side (10 to 11The same cam surface 1
4 are formed. And the plurality of rollers 12,
12 with the axis radial to the center of the input shaft 1
It is rotatably supported as a center. [0006] The toroidal type steplessly constructed as described above.
When the high speed gear is used, the cam plate 10 rotates with the rotation of the input shaft 1.
When rotated, a plurality of rollers 12, 1,
2 is pressed against the cam surface 14 on the outer surface of the input side disc 2.
You. As a result, the input side disk 2 is
At the same time as being pressed by the power rollers 8, 8.
Between the roller surfaces 13 and 14 and the rollers 12 and 12
The input side disk 2 rotates based on the interference.
Then, the rotation of the input side disk 2 corresponds to the plurality of paths.
Transmitted to the output side disk 4 through the word rollers 8, 8.
The fixed output shaft 3 rotates on the output disk 4.
You. The rotation speed ratio (speed change) between the input shaft 1 and the output shaft 3
Ratio), first, between the input shaft 1 and the output shaft 3
When decelerating, each of the trucks should be
Swing the nonions 6, 6, the peripheral surface of each power roller 8, 8
8a, 8aFIG.As shown in FIG.
The center portion of the side surface 2a and the inner side surface 4 of the output side disk 4
each displacement axis so as to abut against the outer peripheral portion of a.
Tilt 7,7. On the other hand, when increasing the speed, the pivot
Each of the trunnions 6, 6 is swung about 5, 5,
And the peripheral surfaces 8a, 8a of the power rollers 8, 8FIG.To
As shown, a portion near the outer periphery of the inner side surface 2a of the input side disk 2
And the central portion of the inner surface 4a of the output side disk 4
And the displacement shafts 7, 7 are tilted so that they come into contact with each other.
You. The inclination angle of each displacement axis 7, 7FIG.WhenFIG.In and
If it is in the middle, an intermediate shift between the input shaft 1 and the output shaft 3
Ratio can be obtained. Further,Figures 12-13Is the actual application 63-69
293 (Japanese Utility Model No. 1-173552)
A more embodied toroidal stepless, described in Lumm
4 shows a transmission. Input disk 2 and output disk
4 is a needle around the input shaft 15
It is rotatably supported via the bearings 16 and 16.
In addition, the cam plate 10 is connected to the end of the input shaft 15 (FIG.Left end of
Part) Spline engagement with the outer peripheral surface
Movement in the direction away from the input side disk 2 is prevented.
I have. Then, the cam plate 10 and the rollers 12, 12
Thus, based on the rotation of the input shaft 15, the input side
The disk 2 is rotated while being pressed against the output side disk 4.
And a loading device 9 of the loading cam type.
The output disk 18 is provided with an output gear 18, a key 19,
19, the output disk 4 and the output gear
18 are rotated in synchronization with each other. [0010] Both ends of the pair of trunnions 6, 6 are paired.
The supporting plate 20 is provided with a swing and an axial direction (FIG.Front and back
direction,FIG.(Left and right directions).
You. And, it is formed in the middle part of each trunnion 6
The displacement shafts 7, 7 are supported in the circular holes 23, 23.
You. Each displacement shaft 7, 7 is parallel and eccentric support
The shaft portions 21 and 21 and the pivot shaft portions 22 and 22 are respectively provided.
I do. Each of the support shaft portions 21 is inserted into each of the circular holes 2.
Radial needle bearings 24, 24 inside 3, 23
It is rotatably supported via the In addition, each pivot shaft
Power rollers 8, 8 around the circumference of the
Are rotatably supported via idle bearings 25, 25.
You. The pair of displacement shafts 7, 7 are connected to the input shaft.
It is provided at a position opposite to the shaft 15 by 180 degrees. or,
Each of the pivot shaft portions 22, 22 of each of these displacement shafts 7, 7 is supported by
The direction eccentric with respect to the shaft portions 21
The same direction with respect to the rotation direction of both the output side discs 2 and 4
(FIG.In opposite directions). The eccentric direction is
A direction substantially perpendicular to the direction in which the input shaft 15 is disposed
ing. Therefore, each of the power rollers 8 and 8
It is supported so as to be slightly displaceable in the direction in which the shaft 15 is disposed.
As a result, due to dimensional accuracy and elastic deformation of each component,
The respective power rollers 8, 8 are arranged in the axial direction of the input shaft 15.
Direction (FIG.Left and right direction,FIG.Displaced in the direction of the front and back)
Apply excessive force to each component even if it becomes a trend
This displacement can be absorbed without any problem. Further, the outer surface of each of the power rollers 8, 8 and
A path between the trunnions 6 and 6 and the inner side
In order from the outer surface side of the power rollers 8,
Thrust for supporting the thrust load applied to the roller 8
Thrust ball bearings 26, 26 which are rolling bearings
To support the thrust load applied to the outer races 30
Needle bearings 27, 27 as thrust bearings
Are provided. Of these, thrust ball bearings 26, 26
Is the thrust direction applied to the power rollers 8
While supporting the load, the rotation of each of these power rollers 8
Is allowed. Such a thrust ball bearing 26,
26 is a plurality of balls 29, 29, and each ball 2
Circular retainers 28, 2 that hold rolling rolls 9, 29 freely
8 and an annular outer ring 30, which is a thrust bearing ring.
(Power roller thrust bearing outer ring)
You. The inner raceway of each thrust ball bearing 26, 26
The outer raceway on the outer surface of each of the outer races 3
It is formed on the inner surface of 0 and 30, respectively. The thrust needle bearings 27, 27
Are the race 31, the cage 32, the needles 33, 33
It is composed of Of these, race 31 and cage 32
Are slightly displaceable in the direction of rotation.
You. Such a thrust needle bearing 27, 27
The races 31, 31 are placed on the inner surfaces of the trunnions 6, 6, respectively.
In a state where the outer ring 30 and the outer ring 30 are in contact with each other,
It is sandwiched between the outer side. Thrust need like this
The bearings 27, 27 are located above the power rollers 8, 8.
The thrust load applied to each outer ring 30, 30 is supported.
The pivot shafts 22, 22 and the outer races 30, 30
Swinging around the support shafts 21, 21 is allowed
You. Further, one end of each of the trunnions 6, 6
(FIG.Drive rods 36, 36 at the left end of the
Are connected to the outer peripheral surface of the intermediate portion of each drive rod 36, 36.
The moving pistons 37, 37 are fixed. And these
Each drive piston 37 is connected to a drive cylinder 3
8 and 38 are fitted in an oil-tight manner. The toroidal type steplessly constructed as described above
In the case of a high-speed machine, the rotation of the input shaft 15 is
To the input side disk 2. And this input side
The rotation of the disk 2 is performed via a pair of power rollers 8
To the output side disk 4 and further to this output side disk.
The rotation of the gear 4 is taken out from the output gear 18. Rotational speed between input shaft 15 and output gear 18
When changing the power ratio, the pair of drive pistons 37,
37 are displaced in opposite directions. Each of these drive fix
The pair of trunnions 6 according to the displacement of the
6 are displaced in opposite directions, for example,FIG.Under
The power roller 8 is located on the right side of FIG.
The roller 8 is displaced to the left in FIG. As a result,
The peripheral surfaces 8a, 8a of these power rollers 8, 8 are
Inner surfaces 2a, 4a of the power side disk 2 and the output side disk 4
The direction of the tangential force acting on the abutment with a changes
You. Then, with the change in the direction of this force,
The pivot 6, which is pivotally supported by the support plates 20, 20,
5 oscillate in mutually opposite directions. As a result,
The aforementioned10 to 11As shown in the above, each of the above power rollers
8, 8 and the inner surfaces 2a, 4a
The contact position changes, and the input shaft 15 and the output gear 18
The rotation speed ratio between the two changes. The toroidal type constructed and operated as described above
In the case of a continuously variable transmission, the power rollers 8
Lubricate the radial needle bearing 25 and thrust ball bearing 26
Lubricating oil needs to be sent. What is toroidal type
During operation of the continuously variable transmission, the power rollers 8 are large.
It rotates at high speed under heavy load. Therefore, the above radial
Ensure the durability of the needle bearing 25 and thrust ball bearing 26
In order to maintain the lubrication, a sufficient amount of lubrication
Need to pump oil. For this reason, conventionally, for example, Japanese Utility Model Laid-Open No. 62-1
Lubricating oil supply device as described in 56658
It has been known. This conventionally known lubricating oil supply device
IsFIG.It is configured as shown in FIG. This lubrication oil supply
The device is provided inside the trunnion 6 with a feed-side oil supply passage 39.
And an outer ring constituting the thrust ball bearing 26
30 is formed with oil supply holes 40, 40, and this thrust ball shaft
The lubricating oil can be sent into the receiver 26 freely. In addition,
The first half of the displacement shaft 7 is formed in the dial needle bearing 25.
Receiving-side refueling passage 4 provided inside the pivot shaft portion 22
Lubricant is fed through 1. This recipient
The upstream end of the oil supply passage 41 is connected to the base end face 3 of the pivot shaft portion 22.
5 has an opening at a portion deviated from the support shaft portion 21.
You. During operation of the toroidal type continuously variable transmission,
By the action of a pump (not shown)
The lubricating oil is fed into the feed-side oil supply passage 39.
You. First, this lubricating oil flows downstream of the feed-side oil supply passage 39.
The outer ring 3 constituting the thrust ball bearing 26 from the end opening
In the gap space between the outer surface of the trunnion 6 and the outer surface of the trunnion 6
Leaked to Further, the lubricating oil is supplied to the oil supply holes 40, 40
Through the thrust ball bearing 26 through the receiving side lubrication system.
Through the path 41 to the radial needle bearing 25
Respectively, and lubricates these two bearings 26, 25. [0020] However, as described above,
In the case of the conventional structure, the lubrication holes 40, 40 and the receiving side
Sent to the radial needle bearing 25 through the oil passage 41
It was difficult to secure a sufficient amount of lubricating oil. this
Are a retaining ring 42 and a spacer, which are locked to the distal end of the pivot shaft portion 22.
43 is the resistance to the flow of the lubricating oil, and
Le NeedlebearingOf the lubricating oil into the space provided with
Due to hindrance. The toroidal type continuously variable transmission of the present invention
Invented to eliminate poor lubrication due to such causes
Things. [0021] SUMMARY OF THE INVENTION The toroidal type of the present invention
The step transmission is the same as the conventional toroidal-type continuously variable transmission described above.
As described above, with the inner surfaces facing each other,
First and second discs rotatably supported in the heart
And the twist of the center axis of these first and second discs.
A trunnion that oscillates about a pivot point
Eccentric support shaft and pivot shaft.
Is supported rotatably on the trunnion,
Displacement shaft whose shaft protrudes from the inner surface of the trunnion
And a radial needle bearing around the pivot shaft
And the first and second data
Sandwiched between disksWith a through hole in the centerPower
Roller andUse this power roller at the tip of the pivot shaft.
Is fitted to the part protruding from the inner end face of the
The spacer was designed to keep the tip of thepower
Attached to the outer end surface of the roller and added to this power roller
Thrust rolling bearings that support thrust loads
With the outer surface of the thrust bearing ring that constitutes the last rolling bearing
Provided between the inner surface of the trunnion and the power
The thrust direction applied to the thrust race from the roller
This thrust to the trunnion while supporting the load
A separate thrust bearing to allow
An oil supply passage provided inside the support shaft. In particular, the toroidal type continuously variable transmission of the present invention
At the end of the oil supply passageThe branch oil supply passage above
By forming it perpendicular to the axial direction of the trunnion
The downstream end of the refueling passage,Partial outer peripheral surface of the pivot shaft
soA part farther from the distal end face of this pivot than the spacer
AndNear the tip of the above radial needle bearing
Exists, out of the load zone of this radial needle bearing
To opening. [0023] According to the present invention, there is provided a toroidal type antenna having the above-described structure.
The step transmission is the same as the conventional toroidal-type continuously variable transmission described above.
Based on the same action, the first disk and the second disk
Transmission of rotational force between the trunnion and the
By changing the angle, the rotation speed ratio of these two disks can be changed.
I can. In particular, the toroidal type continuously variable transmission of the present invention
In this case, the end of the oil supply passage provided inside the pivot shaft
The lubricating oil that has flowed out of the
Flows in the radial needle bearing towards the side. Follow
Supply a sufficient amount of lubricating oil to this radial needle bearing.
it can. Also, in this way, the radial needle bearing
The lubricating oil flowing from the distal end toward the proximal end
Flows through the strike rolling bearing and lubricates this thrust rolling bearing
I do. These allow the radial needle bearing and the
A sufficient amount of lubricating oil can be supplied to both the
Wear.Furthermore, connect the downstream end of the oil supply passage with the radial needle
Because it is opened at a position outside the bearing load zone,
Even after extended use, the pivot shaft may be damaged.
Peg. [0025] FIG. 1 shows a first embodiment of the present invention.
Note that the feature of the present invention is that the pivot shaft 22
Through the receiving side oil supply passage 41, which is an oil supply passage provided inside
The lubricating oil that is sent to the power roller 8
It is in the structure of the part to be fed into the al-needle bearing 25. So
Regarding the structure and operation of the other parts,
Is the same as that of
Hereinafter, description will be made focusing on characteristic portions of the present invention. The displacement shaft 7 for pivotally supporting the power roller 8
The inside of the pivot shaft portion 22 constituting the first half portion is
Receiving-side oil supply passage 41 corresponding to the oil supply passage described in the range
Is provided. The upstream end of the receiving side refueling passage 41 is
A part of the base end face 35 of the pivot shaft portion 22 extends from the support shaft portion 21.
It is open to the off part. Provided in the trunnion 6
Lubricating oil fed through the feeding side oil supply passage 39
From the upstream end of the receiving side oil supply passage 41
It flows into the oil passage 41. Intermediate portion and tip of the receiving side oil supply passage 41
From the part together with the receiving side oil supply passage 41
The first and second components constituting the oil supply passage described in the range of
The branch oil supply passages 44 and 45 are branched. And this
The downstream ends of the first branch refueling passages 44, 44
On the outer peripheral surface of the intermediate portion of the pivot shaft portion 22, the thrust ball bearing 26
An opening is provided at a portion facing the inner diameter side. Further, the second branch oil supply passages 45, 45
Of the pivot shaft 22 at the outer peripheral surface thereof.
An opening is formed in the vicinity of the tip of the Al-needle bearing 25.
In the illustrated embodiment, each of these second branch refueling passages 4
5, 45 constitute the radial needle bearing 25 described above.
The distal end surfaces of the needles 46, 46 (the lower end surface in FIG. 1) and the above
Spacer locked to the tip of pivot shaft portion 22 by retaining ring 42
43. The toroidal of the present invention configured as described above
In the case of a type of continuously variable transmission, the feed-side oil supply passage 39 is used.
Into the receiving side oil supply passage 41 in the pivot shaft portion 22 from
The lubricating oil passes through the first and second branch oil supply passages 44 and 45.
Then, it flows outward in the diameter direction of the pivot shaft portion 22. So
And the openings of the second branch oil supply passages 45, 45
The lubricating oil that has flowed out from the end is located on the tip side of the pivot shaft portion 22.
From the bottom to the proximal end (from bottom to top in FIG. 1)
Flow through the needle bearing 25. Therefore, this radial
A sufficient amount of lubricating oil can be supplied to the needle bearing 25. In addition, the radial needle bearing 2
5 flowing from its distal end toward its proximal end
Flow from the open ends of the first branch refueling passages 44, 44
Merges with the lubricating oil that has come out, and
Then, the thrust ball bearing 26 is lubricated. By these
The radial needle bearing 25 and the thrust ball bearing 2
6 can be supplied with a sufficient amount of lubricating oil. In addition, above
The inner diameter of the first and second branch oil supply passages 44 and 45 (cross section)
Product) is smaller than the inner diameter (cross-sectional area) of the receiving side oil supply passage 41.
Small (narrow) in minutes. Therefore, in the receiving side refueling passage 41,
Most of the lubricating oil fed into the first branch oil supply passage 44,
It does not flow out of 44. In other words, the second branch
A sufficient amount of lubricating oil flows out from the oil supply passages 45, 45
Therefore, the lubricating oil supplied to the radial needle bearing 25
A sufficient amount can be secured. [0031]Further, this embodimentIn Case of,The first, second
Of the two branch refueling passages 44 and 45,First branch refueling
Road 44,44 toFormed in the axial direction of the trunnion 6, the second
The branch refueling passage 45 is connected directly to the axial direction of the trunnion 6.
Corner direction (FIG.(Front and back directions). Also, the receiving side
The refueling passage 41I mentioned earlierLike the central axis of the pivot shaft 22
It is formed at a position slightly off from it. Therefore, the second
The branch lubrication passage 45 is arranged with respect to the central axis of the pivot shaft portion 22.
It is formed in a twisted positional relationship. In this direction, the second branch oil supply passage 45 is
FormationExampleIn the case of the second branch refueling
By devising the formation position of the passage 45, this second branch refueling
The passages 45, 45 are removed from the load zone of the pivot shaft portion 22.
You. That is, according to the experiment of the present inventors, toroidal
During operation of the type continuously variable transmission, power is applied to the pivot shaft portion 22.
From the roller 8 via the radial needle bearing 25,FIG.
A large load is applied to the area (load zone) indicated by the diagonal grid
I understand. The part where such a large load is applied
Forming the branch refueling passages 45, 45 of the displacement shaft 7
It is not preferable because it causes deterioration of durability. So book
In the case of the embodiment, these second branch refueling passages 45, 4
5 is formed at the above-mentioned position to remove it from the load zone. The load zone isFIG.At the position indicated by the diagonal grid
The present inventor considered the reason for the appearance, and found that
It is thought like. First, operation of the toroidal type continuously variable transmission
Sometimes the power roller 8 isFIG.Input side
Between the disc 2 and the output side disc 4. This
As a result, the center hole of the power row 8 isFIG.Exaggerate to
As shown, it is elastically deformed into an elliptical shape, and the pivot shaft portion 22 is inserted.
Strong in the arrangement direction of both the power side and output side disks 2, 4
Press. On the other hand, the power roller 8 is connected to the input side disc.
When strongly clamped between the disk 2 and the output side disk 4,
LaInput side,Output sideInner surfaces 2a, 4a of both disks 2, 4
And the peripheral surface 8 a of the power roller 8.
Warlor 8 aboveInput side,Output sideOf both discs 2, 4
A large force is applied that pushes diametrically outward. And this
Supports the power roller 8 on its inner surface based on the force
Trunnion 6FIG.From the state shown in (A)
It elastically deforms to the state shown in FIG. Support of displacement shaft 7
The shaft portion 21 is located at a position slightly shifted from the center of the trunnion 6.
Because the trunnion 6 is elastically deformed,
Accordingly, the displacement shaft 7 is inclined. And based on this slope
And the radially outer surface of the pivot shaft portion 22 of the displacement shaft 7
The needles 46, 46 constituting the needle bearing 25 are
Win. More specifically,FIG.The part indicated by the oblique lattice
The rolling surfaces of the needles 46, 46 and the pivot shaft
22 comes into strong contact with the outer peripheral surface. The elastic deformation of these power rollers 8
And the one contact based on the inclination of the displacement shaft 7.
The joints are combined and the pivot shaft 22 isFIG.As shown
It is thought that a large load zone appears. In the case of this embodiment
InFIG.As is clear from FIG.
Use for a long period of time because 5, 45 are out of the load zone
The presence of these second branch refueling passages 45
Based on the location, the pivot shaft portion 22 is less likely to be damaged. Next,Figures 7-8Of the present inventionsecondExample
are doing. In addition, this embodiment and a later-described embodiment.FIG.Pointing out toungueThird
In the embodiment, the feed-side lubrication provided inside the trunnion 6 is described.
The lubricating oil discharged from the passage 39 is supplied to the inside of the pivot shaft portion 22.
Specially designed for efficient guiding to the receiving side oil supply passage 41
There is a sign. Radial needle bearing which is a feature of the present invention
25 second branch lubrication passage for supplying sufficient lubricating oil to 25
45 is described above.firstThis is the same as the embodiment. One end of the feed oil supply passage 39 (FIG.of
The left end) moves the trunnion 6 in the axial direction (FIG.Left and right
Supply rod provided inside the drive rod 36 for displacing
Through the oil passage 34,
And lubricating oil is fed into the feed-side oil supply passage 39.
I am here. Also, the other end of the feed-side oil supply passage 39
(FIG.The right end of the opening is closed by a plug 47.
Furthermore, the inner surface of the trunnion 6 (FIG.Bottom) 2 places
In the middle of the feed-side oil supply passage 39
From the downstream end of the main branch refueling passage 48 and the sub-branch supply
The downstream end of the oil passage 49 is opened. Lord of these
The downstream end opening of the branch refueling passage 48 constitutes the displacement shaft 7.
A part of the base end surface 35 of the pivot shaft portion 22, which extends from the support shaft portion 21.
It is opposed to the off part. Also, the sub-branch lubrication passage
The downstream end of 49 corresponds to a part of thrust needle bearing 27.
Facing. On the other hand, the receiving
Side refueling passage 41 is provided, and upstream of the receiving side refueling passage 41
The end is supported by a part of the base end surface 35 of the pivot shaft portion 22.
An opening is provided at a portion off the shaft portion 21. The inner surface of the trunnion 6 and the thrust
Between the outer surface of the outer ring 30 constituting the needle bearing 27
In the gap space 50,FIG.Closed in an elliptical arc shape as shown in
An annular seal member 51 is provided. This sealing material 51
Are elastic materials such as rubber and vinyl, nylon, polyacetator
, Slippery synthetic resin such as polytetrafluoroethylene, copper,
Self-lubricating metals such as silver and oil-impregnated metals, and boron nitride
Made of a sintering material of lubricating material.
And the inner surface of the trunnion 6 and the thrust bearing ring.
Any one of the outer surfaces of the outer ring 30 is in contact with the outer surface.
It is fixed in place by welding, welding, etc.
You. And the upstream end opening of the receiving side oil supply passage 41 and
The main opening which is an opening at the downstream end of the feed-side oil supply passage 39
The downstream end opening of the branch refueling passage 48 is
It is located inside. The configuration is as described above.secondExample Trojan
In the case of the dull type continuously variable transmission, the transmission is provided on the trunnion 6 side.
A main branch refueling passage at the downstream end of the feed-side refueling passage 39
Lubricating oil discharged from 48 to the inside of the sealing material 51
However, it is not blocked by this sealing material 51 and will not flow to the surroundings.
And the receiving side refueling passage 41
It is fed from the upstream end opening of the road 41. This receiving side refueling
The lubricating oil fed into the passage 41 is supplied to the first and second branch feeds.
Through the oil passages 44 and 45, the thrust ball bearing 26 and
It is sent to the dial needle bearing 25. Therefore, the above feed
Out of the lubricating oil sent through the
Most of the parts (the knee that constitutes the thrust needle bearing 27)
Do not be washed away by passing between dollars 33, 33
C) sent to the dual bearings 25 and 26,
Lubrication of 5, 26 can be performed sufficiently. The lubrication in the feed-side oil supply passage 39 is described.
A part of the oil passes through the sub-branch oil supply passage 49 and
This is sent to the st needle bearing 27,
The cross-sectional area of the passage 49 is small,
The amount of lubricant flowing is small. Therefore, this sub-branch refueling
Due to the presence of the passage 49, it is sent to the two bearings 25 and 26.
There is no shortage of lubricating oil. Also, the above thrust need
The bearing 27 serves to reciprocate the swing between the trunnion 6 and the outer ring 30.
This is provided to allow for the
The frequency depends on the rotation speed and the number of rotations of the power roller 8.
It is much smaller than that. Therefore, the thrust needle shaft
Even if the amount of lubricating oil sent to the receiver 27 is small,
There is no problem with the durability of the last needle bearing 27
Absent. Next,FIG.Of the present inventionThirdExample
I have. In the case of this embodiment, the outer periphery of the inner surface of the trunnion 6
A part surrounding the entire circumference of the thrust needle bearing 27
In this state, a closed annular groove 52 is formed.
The annular sealing member 51a is fitted and supported. And this
Of the trunnion 6 by the sealing material 51a
Outside of outer ring 30 constituting thrust needle bearing 27
The outer peripheral opening of the gap space 50 between the first and second surfaces is closed. still,
The shape of the concave groove 52 and the sealing material 51a is
To surround the entire circumference of the toe needle bearing 27, for example,
Or oval. In the case of this embodiment, the main branch oil supply passage
The opening 48 does not necessarily correspond to the proximal end face 35 of the pivot support 22.
You don't have to. In the case of the present embodiment,secondExample
Is not provided. the above
The thrust needle bearing 27 is lubricated in the main branch oil supply passage 4.
8 through the lubricating oil flowing into the inside of the sealing material 51a.
Do Other configurations and operations are described above.secondReal
This is similar to the case of the embodiment. Incidentally, as described above.secondExamples and aboveThird
The sealing materials 51 and 51a used in the embodiment
The lubricating oil sent inside is effective in the receiving side oil supply passage 41.
It is enough to guide efficiently. Necessarily sent inside
It is not necessary to completely prevent the lubricant from spilling out.
No. Therefore, the sealing materials 51 and 51a of each embodiment are
Direction (7 and 9One side is glued to the opposite side
Or inside the recess formed on the opposite surface.
The fittings 51 and 51a are fixed by fitting or the like.
Lubricating oil between the other end in the direction
There is a small gap that has a sufficiently large resistance to the flow of
Being there is no problem in practical use. TheseSecond-thirdIn the case of the embodiment,
By providing the lubricating members 51 and 51a, the main branch lubrication passage 48
The lubricating oil efficiently into the receiving side oil supply passage 41
I am doing it. In contrast,First embodimentLike
The inner surface of the trunnion 6 and the thrust needle bearing 27
Of the clearance space 50 between the outer ring 30 and the outer surface of the outer ring 30
If the end opening is narrowed, the sealing materials 51 and 51a can be omitted.
Also from the main branch refueling passage 48 to the receiving side refueling passage 41
Lubricating oil can be sent efficiently. That is,First implementation
An exampleIn the case of the radial needle bearing 24,
One axial edge of the ring 53 (Of FIG.Thrust ball axis at the lower edge)
The outer ring 30 constituting the receiver 26 is brought close to the outer surface of
The area of the inner end opening of the interspace 50 is reduced. [0046] The toroidal type continuously variable transmission according to the present invention has the following features.
Because it is constructed and operates as described above,
Radial need to support high-speed rotating power rollers
Lubricating oil in the bearing, The pivot shaft is hard to be damaged
While doingIt becomes possible to send. As a result,
This contributes to the improvement of the durability and reliability of the oil-type continuously variable transmission.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view of a main part showing a first embodiment of the present invention. FIG. 2 is a view for showing a load range of a pivot shaft constituting a pivot.
FIG. FIG. 3 shows a power low during operation of the toroidal type continuously variable transmission.
FIG. 4 is a partial cross-sectional view for explaining a load applied to the la. FIG. 4 is a sectional view taken along line AA of FIG . 3; FIG. 5 shows a tiger during operation of a toroidal type continuously variable transmission.
Sectional drawing which shows the deformation | transformation state of a nonion . FIG. 6 shows the load range of the pivot shaft based on the inclination of the pivot.
FIG. FIG. 7 is a sectional view of a main part showing a second embodiment of the present invention. FIG. 8 shows that the sealing material used in the second embodiment is
The view seen from. FIG. 9 is a sectional view of a main part showing a third embodiment of the present invention. FIG. 10 shows a conventional toroidal type continuously variable transmission.
FIG. 3 is a side view showing a basic configuration in a state of maximum deceleration. FIG. 11 is a side view showing a state at the time of maximum speed increase. FIG. 12 is a sectional view showing an example of a conventional specific structure. FIG. 13 is a sectional view taken along line BB of FIG . 12; FIG. 14 is a sectional view of a main part showing a conventional structure having an oil supply passage .
FIG. [Description of Signs] 1 Input shaft 2 Input side disk (first disk) 2a Inner surface 3 Output shaft 4 Output side disk (second disk) 4a Inner surface 5 Pivot 6 Trunnion 7 Displacement shaft 8 Power roller 8a Peripheral surface Reference Signs List 9 pressing device 10 cam plate 11 retainer 12 rollers 13 and 14 cam surface 15 input shaft 16 needle bearing 17 flange 18 output gear 19 key 20 support plate 21 support shaft 22 pivot shaft 23 circular hole 24, 25 radial needle Bearing 26 Thrust ball bearing 27 Thrust needle bearing 28 Cage 29 Ball 30 Outer ring 31 Race 32 Cage 33 Needle 34 Oil supply passage 35 Base end surface 36 Drive rod 37 Drive piston 38 Drive cylinder 39 Feed-side oil supply passage 40 Oil supply hole 41 Receiving-side oil supply Passage 42 retaining ring 43 spacer 44 first branch refueling passage 45 second branch refueling passage 46 d Dollar 47 plug 48 main branch oil supply passage 49 by-branch oil supply passage 50 clearance space 51,51a sealant 52 groove 53 outer ring

──────────────────────────────────────────────────続 き Continued from the front page (56) References JP-A-61-59055 (JP, A) JP-A-8-35552 (JP, A) JP-A-2-47458 (JP, U) JP-A-2-47458 135760 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16H 15/00-15/56 F16H 57/00-57/12 F16C 19/00-19/56 F16C 33/30 -33/66

Claims (1)

(57) [Claims 1] With the inner surfaces facing each other,
First and second discs concentrically and rotatably supported, a trunnion swinging about a pivot axis which is twisted with respect to a center axis of the first and second discs, and eccentric with each other; Consisting of a supporting shaft portion and a pivot shaft portion,
Of these, the support shaft is rotatably supported by the trunnion, and the pivot shaft is protruded from the inner surface of the trunnion, and the displacement shaft is rotatable around the pivot shaft via a radial needle bearing. With a through hole in the center , sandwiched between the first and second disks while being supported by
And power rollers that, the power at the tip of the pivot shaft portion
Externally fitted to the part protruding from the inner end surface of the roller,
A spacer which is prevented from coming off from the front end portion, and a thrust rolling bearing which is attached to an outer end surface of the power roller and supports a thrust load applied to the power roller,
This thrust bearing is provided between an outer surface of a thrust bearing ring constituting the thrust rolling bearing and an inner surface of the trunnion and supports a load in a thrust direction applied to the thrust bearing ring from the power roller. Another thrust bearing that allows the raceway displacement,
In the toroidal type continuously variable transmission that includes a fuel supply path provided inside said pivot shaft portion, the end of the oil supply passage
Make the branch lubrication passage perpendicular to the axial direction of the trunnion.
The lower end of the oil supply passage is formed on the outer peripheral surface of the pivot shaft portion more partially than the spacer.
This radial needle is located at a portion away from the distal end surface and near the distal end of the radial needle bearing.
A toroidal-type continuously variable transmission characterized in that it is opened at a portion of the bearing outside the load zone .