JP3496513B2 - Toroidal type continuously variable transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement of a toroidal type continuously variable transmission adopted in vehicles and the like.

[0002]

2. Description of the Related Art Conventionally, as a continuously variable transmission for a vehicle, a power roller in which an input disk and an output disk whose opposite surfaces are formed in a toroidal shape are coaxially arranged, and which is sandwiched and pressed by the input / output disk. There is known a toroidal type continuously variable transmission capable of continuously setting an arbitrary gear ratio by changing the tilt angle (tilt angle) of the toroidal type.
56, JP 6-280960 A, JP 8
Those disclosed in JP-A-355552, JP-A-8-291850 and the like are known.

As shown in FIG. 12, these form rotating shaft portions 3a and 3b on the upper and lower end portions of a trunnion 3 which pivotally supports a power roller 1 via a pivot shaft 2, respectively, while rotating them. Between the shaft portions 3a and 3b,
The power roller 1 has a concave inner periphery for accommodating the power roller 1, and is provided with an offset portion 3c protruding in the outer peripheral direction of the input / output disk (left side in the drawing).

Then, inside the shaft portion 6b and the trunnion 3 connected to the lower rotating shaft portion 3b in the drawing, the inside of the pivot shaft 2 is provided via oil passages 11 and 12 communicating with a hydraulic power source (not shown). From the formed oil passage 15 to the supply holes 16, 1
7 (first lubrication means) to supply pressure oil to the power roller 1
Is provided between the power roller 1 and the outer ring 7 for supporting the thrust roller in the radial direction, and the ball bearing 8 for supporting the thrust load applied to the power roller 1 is supplied with oil for lubrication and cooling. It is carried out.

Since the power roller 1 is sandwiched and pressed by a large force by an input / output disk (not shown), a large thrust force is applied to the power roller 1 toward the outer peripheral direction of the input / output disk, that is, toward the offset portion 3c. Try to displace.

Therefore, the trunnions 3 and 3 facing each other are connected to a swingable link via the needle bearing 21 and the spherical bearing 20 and are moved to the left side in the figure against the thrust force applied to the power roller 1. The displacement of the trunnion 3 is allowed while the displacement is restricted.

[0007]

However, in the above conventional toroidal type continuously variable transmission, the trunnion 3 is used.
At a linking position of a link (not shown), the trunnion 3 rotates with a shift while supporting the thrust force applied to the power roller 1, so that the needle bearing 21 inside the spherical bearing 20 supports a large load. Although it will roll, the lubrication of the needle bearing 21 is as shown in FIG.
As shown by the broken line, among the oil scattered on the inner circumference of the casing 10, the oil that has penetrated into the needle bearing 21 through the gap of the spherical bearing 20 and the oil that has penetrated into the needle bearing 21 along the rotary shaft portions 3a and 3b. Since it is carried out only by itself, the amount of lubricating oil may be insufficient, wear tends to progress due to insufficient lubrication and cooling,
The peeling life of the rolling surface tends to be shortened.To avoid this, if the bearing capacity is increased to ensure wear resistance and fatigue strength, the size of the bearing will increase and the manufacturing cost will increase. There was a problem of doing.

Therefore, the present invention has been made in view of the above problems, and an object thereof is to improve durability while preventing an increase in the size of the bearing interposed in the connecting portion of the trunnion and the link.

[0009]

According to a first aspect of the present invention, a pair of trunnions that are arranged so as to face each other and are displaceable in the axial direction and about the axis are sandwiched between the facing surfaces of an input / output disk, and a base end of the trunnion is provided. A power roller rotatably supported by a pivot shaft oscillatably connected to the opposing trunnion, an oscillating link, and a trunnion and a link interposed at the link connecting position. In a toroidal type continuously variable transmission including a trunnion and a bearing member that allows relative rotation and swing of a link, a lubricating means for supplying lubricating oil to the bearing member is formed inside the trunnion.

According to a second aspect of the present invention, in the first aspect, the bearing member includes a spherical bearing which allows relative swing of the trunnion and the link, and an inner circumference of the spherical bearing and an outer circumference of the trunnion. The lubricating means supplies the lubricating oil to the inner circumference of the roller bearing.

In a third aspect based on the second aspect, the lubricating means guides the lubricating oil scattered from the power roller or the bearing of the power roller to the bearing member.

A fourth invention is the first or second invention.
In the invention described above, the lubricating means communicates with a hydraulic pressure supply source.

In a fifth aspect based on the third aspect, the lubricating means has a hole formed in a trunnion facing the bearing of the power roller, and the hole faces the roller bearing. And a lubrication hole communicating with the outer periphery of the trunnion.

In a sixth aspect based on the fifth aspect, the lubricating hole inclines in the direction of gravity from the hole toward the outer periphery of the trunnion.

Further, in a seventh aspect based on the fifth aspect, the lubricating hole opens on the outer periphery of the trunnion, which is separated from the load point of the link and the trunnion by a predetermined angle in the circumferential direction.

In addition, in an eighth aspect based on the fifth aspect, the lubrication hole is opened on the outer periphery of the trunnion at a predetermined angle in the circumferential direction from the load point of the link and the trunnion, and the lubrication hole is opened. The ratio of the area or inner diameter to the length of the roller is set to a predetermined value or less that does not hinder the rotation of the roller bearing . A ninth invention is the fifth invention.
At, the lubrication hole is the load point of the link and trunnion.
Open on the outer circumference of the trunnion at a specified angle in the circumferential direction from
With the opening area or inner diameter of the lubrication hole,
The roller length ratio is the contact pressure of the roller bearing at the maximum of the load point.
It is set below a predetermined value that does not exceed the large surface pressure.

In a tenth aspect based on the fifth aspect, the link connects the upper ends of the trunnions facing each other, while the holes extend in the axial direction of the trunnion at the upper ends of the trunnions. The stepped portion is formed so as to penetrate therethrough, and the inner diameter of the stepped portion below the connection position with the lubricating hole is reduced.

An eleventh aspect of the present invention is the same as the fifth aspect, wherein the link connects the upper end portions of the trunnions facing each other, while the hole extends in the axial direction of the trunnion at the upper end portion of the trunnion. The ring-shaped member is formed so as to penetrate therethrough and is provided at a connection position with the lubrication hole.

A twelfth aspect of the present invention is the fuel cell system according to the second aspect, wherein the spherical bearing has an oil groove formed on a surface facing the roller bearing.

[0020]

Therefore, according to the first aspect of the present invention, the power roller rotates in accordance with the rotation of the input / output disk to transmit the power, and the trunnion supports the thrust force of the power roller due to the pinching and pressing of the input / output disk. . The link connecting the trunnions facing each other supports this thrust force that acts in the pulling direction, and allows the rotation and axial displacement of the trunnion during shifting while maintaining the positional relationship of the trunnion by the bearing member. Since the lubricating means formed inside the trunnion directly lubricates the bearing member, it is possible to positively perform lubrication and cooling as compared with the conventional example,
The wear resistance and the fatigue strength can be significantly increased without increasing the capacity of the bearing member that supports the thrust force, and the durability and reliability of the toroidal type continuously variable transmission can be improved.

According to a second aspect of the present invention, the bearing member is a spherical bearing that allows relative swinging of the trunnion and the link, and is inserted between the inner circumference of the spherical bearing and the outer circumference of the trunnion to link with the trunnion. Of the roller bearing that allows the relative rotation and swing of the trunnion and the link while supporting the thrust force applied to the power roller while allowing the relative rotation and swing of the trunnion and the link. By supplying lubricating oil to the inner circumference, the wear resistance and fatigue strength are significantly increased without increasing the capacity of the roller bearing of the bearing member that supports the thrust force, and the peeling life of the rolling surface of the roller bearing is increased. Can be extended, and the durability and reliability of the toroidal type continuously variable transmission can be improved.

According to a third aspect of the invention, the lubricating means guides the bearing of the power roller or the lubricating oil scattered from the power roller to the bearing member, thereby reducing the amount of lubricating oil for lubricating other mechanisms. Moreover, the durability of the bearing member can be improved while utilizing the lubricating oil supplied to the trunnion without waste.

According to a fourth aspect of the present invention, the lubrication means receives the supply of pressure oil directly from the hydraulic pressure supply source and positively lubricates and cools. The performance can be improved, and the wear resistance and fatigue strength are significantly increased without increasing the capacity of the bearing member that supports the thrust force, and the durability and reliability of the toroidal type continuously variable transmission are improved. be able to.

Further, in the fifth aspect of the invention, the rotation of the power roller and the bearing of the power roller accompanying the operation of the continuously variable transmission causes the oil that lubricates and cools the power roller or the bearing of the power roller to be scattered to the inner circumference of the trunnion. However, the oil collected in the hole formed in the trunnion facing the bearing of the power roller flows through the lubrication hole from the hole to the outer circumference of the trunnion facing the roller bearing, and the roller forming the bearing member. It is possible to reliably lubricate and cool the bearings,
It is possible to improve the durability of the bearing member while utilizing it efficiently without increasing the discharge flow rate from the hydraulic pressure supply source supplied to the trunnion.

According to a sixth aspect of the present invention, the lubricating hole of the lubricating means is inclined in the direction of gravity from the hole toward the outer circumference of the trunnion, so that the lubricating oil collected on the inner circumference of the hole flows into the lubricating hole. It is possible to reliably flow to the outer periphery of the trunnion facing the roller bearing, and to reliably lubricate and cool the roller bearing that constitutes the bearing member.

According to a seventh aspect of the invention, the lubrication hole of the lubrication means is opened on the outer periphery of the trunnion, which is separated from the load point of the link and the trunnion by a predetermined angle in the circumferential direction, so that the surface of the roller bearing contacting the trunnion is exposed. It is possible to prevent the pressure from becoming excessive and to significantly increase the wear resistance and the fatigue strength.

In the eighth or ninth aspect of the invention, the lubrication hole of the lubrication means is opened on the outer periphery of the trunnion at a predetermined angle in the circumferential direction from the load point of the link and the trunnion, and the opening area of the lubrication hole or By setting the ratio of the inner diameter to the length of the roller to a predetermined value or less, it is possible to prevent the surface pressure of the roller bearing that comes into contact with the trunnion from becoming excessive and to significantly increase wear resistance and fatigue strength. it can.

[0028] In a tenth aspect based on the fifth aspect, the trunnions facing each other are linked at their upper ends by a link through a bearing member, and the hole of the lubricating means is a trunnion at the upper end of the trunnion. Since it has a stepped portion that is formed so as to penetrate through in the axial direction of and the inner diameter below the connection position with the lubricating hole is reduced,
Since the oil is once supplied to the roller bearing from the lubrication hole after being accumulated in the stepped portion, more of the lubricating oil scattered from the power roller can be supplied to the roller bearing, and the lubricating performance can be further improved.

According to the eleventh aspect of the invention, the trunnions facing each other are linked at their upper ends by links via bearing members, and the hole of the lubricating means is formed so as to penetrate through the upper ends of the trunnions in the axial direction of the trunnions. In addition, since the annular member is provided at the connection position with the lubrication hole, the lubricating oil collected in the inner circumference of the hole is temporarily accumulated in the annular member and then supplied from the lubrication hole to the roller bearing. A larger amount of the lubricating oil scattered from the roller bearing can be supplied to the roller bearing, and the lubricating performance can be further improved.

In the twelfth invention, an oil groove is formed on the inner surface of the spherical bearing on the surface facing the roller bearing, and the lubricating oil supplied from the lubricating means is guided to the entire circumference of the roller bearing. Lubrication performance can be improved.

[0031]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 and FIG. 2 show an example in which the present invention is applied to a toroidal type continuously variable transmission similar to the above-mentioned conventional example. The trunnions 3 and 3 facing each other have rotary shafts on the upper and lower end sides. While forming the portions 3a and 3b respectively, an inner periphery is formed between these rotary shaft portions 3a and 3b so as to accommodate the power roller 1, and an offset portion protruding in the outer peripheral direction of the input / output disk. 3c is formed.

The power roller 1 is axially supported by a pivot shaft 2 which is eccentric by a predetermined amount, and the pivot shaft 2 has a base end at an offset portion 3c of a trunnion 3.
On the other hand, the power roller 1 supported in the radial direction by a needle bearing 9 on the tip end side is rotatably supported by the pivot shaft 2.

The power roller 1 has the offset portion 3c.
The thrust load is supported by a ball bearing 8 and an outer ring 7 between the power roller 1 and the outer ring 7, and the power roller 1 uses the needle bearing 9 on the tip end side of the pivot shaft 2 and the ball bearing 8 in the radial direction and the thrust direction. Is supported by the offset portion 3c of the trunnion 3.

A rod 6b is connected to the lower end of the trunnion 3 (on the side of the rotating shaft 3b), and a hydraulic servo cylinder 6 connected to this rod 6b causes the trunnion 3 to move in the axial direction (vertical direction in FIGS. 1 and 2). Driven to rotate the power roller 1 around the rotation shaft portions 3a and 3b of the trunnion 3 (hereinafter, referred to as tilting) and change the contact radius between the input disc and the output disc to continuously change the gear ratio. Change to.

The trunnions 3 and 3, which are arranged to face each other with the input / output shaft C ₀ interposed therebetween, have their upper end side rotating shaft parts 3a swingably supported by a link 4 so that their lower end side rotating shaft parts are supported. Links 3b are swingably supported to each other, and are connected to each other, and maintain a constant distance between the trunnions 3 and 3 against the thrust force applied to the power rollers 1 and 1.

Rotating shaft portion 3 of links 4 and 5 and trunnion 3
At the connecting positions of a and 3b, similarly to the above-mentioned conventional example, the spherical bearings 20 provided on the rotary shaft portions 3a and 3b are engaged with the through holes provided on both end sides of the links 4 and 5, respectively, and swing. The trunnion 3 moves with respect to the links 4 and 5 by the needle bearing 21 (roller bearing, bearing member) which is moved between the inner circumference of the spherical bearing 20 and the outer circumference of the rotary shaft portions 3a and 3b. The relative rotation becomes possible and the hydraulic servo cylinders 6, 6 are driven in mutually opposite directions, whereby the power rollers 1, 1 supported by the trunnions 3, 3 tilt and change the gear ratio, and the trunnion 3 is rotated. The links 4 and 5 for connecting 3 are oscillated around the center of FIG.

The needle bearing 21 rolls with the rotating shafts 3a and 3b as the inner ring and the inner circumference of the spherical bearing 20 as the outer ring.

On the other hand, the lubrication of the connecting portion of the power roller 1, the trunnion 3 and the links 4 and 5 is performed as follows.

An oil passage 11 formed inside the shaft portion 6b connected to the rotating shaft portion 3b communicates with a hydraulic pressure supply source (not shown), and from this oil passage 11 an oil passage 12 formed inside the trunnion 3 is formed. Via the oil passage 15 formed inside the pivot shaft 2 to the supply holes 16 and 17,
Oil is supplied to a needle bearing 9 that axially supports the power roller 1 in a radial direction and a ball bearing 8 that supports a thrust load applied to the power roller 1 to perform lubrication and cooling.

Further, as shown in FIG. 2, the oil which collects the oil scattered from the ball bearing 8, the needle bearing 9 or the power roller 1 is provided on the inner circumference of the rotary shaft portions 3a and 3b facing the ball bearing 8. Collection hole 3
0 and 32 (lubrication means) are opened.

In the rotating shaft portion 3a on the upper end side of the trunnion 3, an oil collecting hole 30 is opened in the inner periphery facing the ball bearing 8 and is extended upward in FIG. The lubrication hole 31 penetrating in the horizontal direction is opened on the outer periphery of the rotary shaft portion 3 a facing the needle bearing 21, and the ball bearing 8 and the needle bearing 9 are formed.
Alternatively, the oil scattered from the power roller 1 passes through the oil collecting hole 30 and the lubricating hole 31 and then the needle bearing 21
Guided to the inner circumference. Although the oil collecting hole 30 is formed so as to penetrate the rotary shaft portion 3a in the vertical direction, it may have a depth up to the branch position with the lubricating hole 31.

Similarly, in the rotating shaft portion 3b on the lower end portion side of the trunnion 3, an oil collecting hole 32 is opened in the inner periphery facing the ball bearing 8 and is extended downward in FIG.
Lubrication hole 3 formed from the bottom part thereof in a substantially diagonally downward direction
3 is a rotating shaft portion 3b facing the needle bearing 21.
The oil splashed from the ball bearing 8, the needle bearing 9 or the power roller 1 is guided to the inner circumference of the needle bearing 21 through the oil collecting hole 32 and the lubricating hole 33.

With the above arrangement, the operation will be described.

When the operation of the continuously variable transmission is started, pressure oil is supplied from the inside of the trunnion 3 to the oil passage 15 formed inside the pivot shaft 2 via the oil passages 11 and 12 from a hydraulic pressure supply source (not shown). Supplied.

The oil passages 15 are respectively connected to the pivot shaft 2
The oil is supplied to the needle bearing 9 from the supply hole 16, while the oil is supplied to the ball bearing 8 from the supply hole 17.

Then, the oil supplied to the ball bearing 8 lubricates and cools the power roller 1 and the rolling surface of the outer ring 7 and the ball bearing 8, and then the centrifugal force corresponding to the rotation of the power roller 1 It scatters toward the inner circumference of the rotating shaft portions 3a, 3b of the trunnion 3. In addition, the oil supplied to the needle bearing 9 is the power roller 1
After lubricating and cooling the rolling surfaces of the pivot shaft 2 and the needle bearing 9, the rotating shaft portion 3a of the trunnion 3 is rotated by the centrifugal force according to the rotation of the power roller 1.
Scatter toward the inner circumference of 3b.

The oil scattered toward the inner circumference of the rotating shaft portion 3a of the trunnion 3 penetrates into the oil collecting hole 30 and adheres to the inner circumference thereof, and then a part of the oil passes through the lubrication hole 31 to rotate the rotating shaft portion. It is supplied to a needle bearing 21 arranged on the outer periphery of 3a.

On the other hand, the oil scattered toward the inner circumference of the rotating shaft portion 3b of the trunnion 3 enters the oil collecting hole 32, and then passes through the lubrication hole 33, and the needle disposed on the outer circumference of the rotating shaft portion 3b. It is supplied to the bearing 21.

In this way, the oil scattered from the ball bearing 8, the needle bearing 9 or the power roller 1 is applied to the needle bearings 21 and 21 which connect the rotating shafts 3a and 3b at the upper and lower ends of the trunnion 3 to the links 4 and 5, respectively. When supplied, it can be more actively lubricated and cooled compared to the conventional example, and the wear resistance and fatigue strength are greatly increased without increasing the bearing capacity, and the peeling life of the rolling surface is increased. Can be extended, and the durability and reliability of the toroidal type continuously variable transmission can be improved.

As the oil for lubricating the needle bearings 21 and 21, the oil scattered from the ball bearing 8 or the needle bearing 9 or the power roller 1 is used, so that the ball bearing 8 or the needle bearing 9 of the pivot shaft 2 is lubricated. The oil amount does not decrease, and it can be used without waste without changing the discharge flow rate from the hydraulic pressure supply source supplied to the trunnion 3.

It should be noted that the lubricating holes 31,
An example in which one 33 is provided is shown, but by providing a plurality of lubricating holes 31 and 33 in the circumferential direction, the lubricating performance and the cooling performance can be further improved.

FIGS. 3 to 6 show the second embodiment, in which the positions of the lubricating holes 31 and 33 of the first embodiment are set within a predetermined angle range with respect to the load points of the links 4 and 5. The other configurations are the same as those in the first embodiment.

In FIG. 3 (A), two lubricating holes 31, 31 are formed in the rotating shaft portion 3a which is the upper end portion side of the trunnion 3.
Is a predetermined angle θ from the load point P in the circumferential direction of the rotary shaft portion 3a.
Open at the position.

Here, the load point P is, as shown in FIG.
When the operation of the continuously variable transmission is started, the power roller 1 is sandwiched and pressed by the input / output disk, and the power roller 1 receives the force of the load W in the thrust direction.

This thrust load W is transmitted to the trunnion 3 via the ball bearing 8, the outer ring 7, and the needle bearing 13, and the trunnion 3 tends to be displaced toward the inner circumference of the casing 10 in FIG. By the links 4 and 5 connected to the rotating shafts 3a and 3b of
This displacement is regulated. Therefore, the links 4, 5 have a load w / 2 in the pulling direction between the connecting positions with the trunnion 3.
Accordingly, this position becomes the load point P.

Then, the rotating shaft portion 3 by this load w / 2
The surface pressure distributions in the circumferential directions of a and 3b are determined by the lubricating holes 31, 3 on the outer circumference.
When 3 is not formed, it becomes as shown by the broken line in FIG. 6, and as it goes away from the load point P, that is, the angle θ in the circumferential direction.
, The surface pressure gradually decreases, and θ = 90 °
At a position of up to 180 °, the no-load zone where the surface pressure is 0 is obtained.

The opening positions of the lubricating holes 31 and 33 are closer to the position of θ = 0 which is the maximum surface pressure in the load zone of FIG.
Although the needle bearing 21 can be reliably lubricated, the rotation shaft portion 3a,
Since the contact area between 3b and the needle bearing 21 decreases, if the load point P gets too close, the surface pressure exceeds the maximum surface pressure of θ = 0, the load on the needle bearing 21 and the like increases, and the durability decreases. Will be invited.

When the opening area of the lubrication holes 31, 33, that is, the inner diameter is increased, the contact area between the rotating shaft portions 3a, 3b and the needle bearing 21 is decreased and the surface pressure is increased. Since the rotation of 21 is hindered, as shown in FIG.
Assuming that the effective length of the roller of the needle bearing 21 is leff, first, in order not to hinder the rotation of the needle bearing 21, it is necessary to set d / leff ≦ 0.5 (1).

Next, in order to bring the opening position of the lubricating hole 31 close to θ = 0 ° without the surface pressure exceeding the maximum surface pressure at the load point P, θ ≧ 45 ° ... (2) d / leff The inventor of the present application has confirmed through experiments and the like that it may be set to ≦ 1/70 (θ−25) (3).

Therefore, from the above equations (1) to (3),
The relationship between d / leff and θ is as shown in FIG. 5, and in the region where the angle θ in the circumferential direction from the load point P is 45 ° or more, lubrication is performed so as to satisfy the above formulas (1) and (3). Inner diameter d of hole 31
For example, as shown in FIGS. 3A and 3B, by setting the opening positions of the two lubrication holes 31, 31 to θ = 90 ° and setting the inner diameter d as described above, While preventing the needle bearing 21 from rotating poorly and surely preventing the surface pressure applied to the needle bearing 21 from becoming excessive, the lubricating performance can be further improved, and the needle bearing 2 that connects the link 4 and the trunnion 3 can be obtained.
It is possible to further improve the abrasion resistance and the peeling life of No. 1 described above.

Although the rotating shaft portion 3a at the upper end has been described, two lubricating holes 33, 33 may be similarly provided in the rotating shaft portion 3b at the lower end although not shown.

FIGS. 7A and 7B show a third embodiment, in which an oil groove 20A is provided on the inner circumference of the spherical bearing 20 of the first or second embodiment, and other constructions are provided. Is the same as above.

By forming the oil groove 20A over the entire inner circumference of the spherical bearing 20, the oil supplied from the lubrication holes 31 and 33 to the needle bearing 21 is supplied almost along the entire circumference along the oil groove 20A. In particular, it becomes possible to reliably supply the oil to the vicinity of the load point P where the lubrication holes 31 and 33 cannot be formed, and further improve the lubrication performance of the connecting position of the links 4 and 5 and the trunnion 3 to improve the needle bearing 21. It is possible to significantly improve the abrasion resistance and the peeling life of the.

In the inner circumference of the spherical bearing 20, the oil groove 20A is formed.
Although the surface pressure increases due to the formation of the above-mentioned embodiment, the tilting of the trunnion 3 causes the maximum load point of the spherical bearing 20 to move, and the needle bearing 2
Since the contact surface pressure is lower than that of the rotating shaft portions 3a and 3b which are the inner rings of No. 1, the needle bearing 21 as a whole is improved in lubrication performance at the maximum load point P on the rotating shaft portions 3a and 3b, thereby improving wear resistance. Property and peeling life are improved.

FIG. 8 shows a fourth embodiment, in which the first
The lubrication holes 31 and 33 of the embodiment are provided with a predetermined inclination, and other configurations are the same as the above.

In FIG. 8, a lubricating hole 31 'connected to the oil collecting hole 30 formed in the upper rotary shaft portion 3a is provided with an inclination of a predetermined angle α with respect to the rotary shaft 3z of the trunnion 3. The angle α is set to 90 ° or less.

The lubricating hole 33 'connected to the oil collecting hole 32 formed in the lower rotating shaft portion 3b is provided with an inclination of a predetermined angle α with respect to the axis parallel to the rotating shaft 3z of the trunnion 3. The angle α is set to 90 ° or less.

That is, the lubrication holes 31 'and 33' are located at the opening positions of the rotary shafts 3a and 3b at the oil collecting holes 30 and 32, respectively.
Set below the connection position with the oil collecting hole 30,
The oil flowing from 32 to the lubrication holes 31 'and 33' is smoothly guided to the needle bearing 21 by gravity, and the amount of lubricating oil to the needle bearing 21 is increased to further improve the lubricating performance. Is.

FIG. 9 shows a fifth embodiment, in which the first
Or, the step portion 30A is formed in the oil collecting hole 30 of the fourth embodiment, and other configurations are similar to the above.

The oil collecting hole 30 penetratingly formed in the upper rotary shaft portion 3a is formed such that the inner diameter thereof increases above the position where it is connected to the lubricating hole 31 ', and the oil collecting hole 30 is formed at the connecting position of the lubricating hole 31'. Has a step portion 30A.

A part of the oil that lubricates the ball bearing 8 and the quadruple bearing 9 as the power roller 1 rotates adheres to the inner circumference of the oil collecting hole 30 and then flows downward due to gravity. At this time, the oil attached above the step portion 30A formed in the oil collecting hole 30 is
Since the oil is accumulated in A and guided to the lubrication hole 31 ', the amount of oil supplied to the lubrication hole 31' can be increased and the lubrication performance can be further improved.

FIG. 10 shows a sixth embodiment, in which an annular member 34 is fixedly provided on the inner circumference of the oil collecting hole 30 of the first to fourth embodiments, and other configurations are the same as the above. Is.

On the inner circumference of the oil collecting hole 30 formed through the upper rotating shaft portion 3a, an annular member 34 penetrating the central portion is fixedly provided at a position connected to the lubricating hole 31 '.

The annular member 34 inclines downward from the inner circumference toward the outer circumference, and the outer circumference of the annular member 34 has the lubrication hole 3
It is fixed near the opening below 1 '.

A part of the oil that lubricates the ball bearing 8 and the two-dollar bearing 9 as the power roller 1 rotates passes through the inner circumference of the annular member 34 and adheres to the upper inner circumference of the oil collecting hole 30. After that, it flows downward due to gravity, and is accumulated in the annular member 34 inclined downward toward the outer periphery and then guided to the lubricating hole 31 '. Therefore, the amount of oil supplied to the lubricating hole 31' is increased, The lubrication performance can be further improved.

FIG. 10 shows a seventh embodiment, in which the first
The oil collecting holes 30 and 32 of the embodiment are eliminated and the oil is directly supplied from the oil passage 12 to the lubricating holes 31 and 33. Other configurations are the same as those of the first embodiment.

Oil passage 12 formed inside trunnion 3
After branching the oil pumped from the oil passage 11 in the shaft portion 6b to the lubricating oil passage 36 opened in the rotating shaft portion 3b facing the needle bearing 21, in the offset portion 3c,
The oil passage 15 inside the pivot shaft 2 and the needle bearing 21 are branched to a lubricating oil passage 35 which is opened in the rotating shaft portion 3 a facing the needle bearing 21.

Therefore, the oil pressure-fed to the trunnion 3 from the hydraulic pressure supply source (not shown) is provided inside the trunnion 3 with the lubricating oil passages 35 and 36 and the oil passage 1 of the pivot shaft 2.
5, the lubricating oil passages 35 and 36 are pumped to the needle bearing 2 of the rotary shafts 3a and 3b by the oil fed.
The oil that directly lubricates Nos. 1 and 21 and is supplied to the oil passage 15 passes through the supply holes 16 and 17 to the needle bearing 9 and the ball bearing 8 that pivotally support the power roller 1 as in the first embodiment. Lubricate.

The needle bearings 21 and 21 of the rotating shafts 3a and 3b are positively lubricated by the lubricating oil passages 35 and 36, so that the lubricating performance can be dramatically improved as compared with the conventional example. is there. In this case, it is necessary to increase the discharge flow rate of the hydraulic pressure supply source to secure the lubricating oil amount of the pivot shaft 2.

In the above embodiment, the lubrication holes 31 and 33 or the lubrication oil passages 35 and 36 for supplying oil to the needle bearing 21 are provided in the upper and lower rotary shaft portions 3a and 3b, respectively. The lubricating hole 31 or the lubricating oil passage 35 may be provided only in the shaft portion 3a, while the lubricating hole or the lubricating oil passage in the lower rotating shaft portion 3b may be omitted.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a toroidal type continuously variable transmission showing an embodiment of the present invention.

FIG. 2 is likewise an enlarged sectional view of the trunnion.

3A and 3B show a second embodiment, FIG. 3A is a horizontal sectional view of a rotary shaft portion, and FIG. 3B is a vertical sectional view of the rotary shaft portion.

FIG. 4 is an enlarged cross-sectional view of the trunnion showing the force applied to the link.

FIG. 5 is a graph showing the relationship between the inner diameter d / leff and the angle θ.

FIG. 6 is a graph showing the relationship between angle θ and surface pressure.

7A and 7B show a third embodiment, FIG. 7A is a horizontal sectional view of a rotary shaft portion, and FIG. 7B is a vertical sectional view of the rotary shaft portion.

FIG. 8 is an enlarged cross-sectional view of the trunnion according to the fourth embodiment.

FIG. 9 is a vertical cross-sectional view of a rotating shaft portion according to the fifth embodiment.

FIG. 10 shows a sixth embodiment and is a vertical cross-sectional view of a rotary shaft portion.

FIG. 11 is an enlarged cross-sectional view of the trunnion according to the seventh embodiment.

FIG. 12 is an enlarged sectional view of a trunnion showing a conventional example.

[Explanation of symbols]

1 power roller 2 pivot shaft 3 trunnions 3a, 3b Rotating shaft part 3c offset part 3z rotation axis 4,5 links 6 Hydraulic servo cylinder 6b rod 7 outer ring 8 ball bearings 9 Needle bearing 10 casing 11, 12 oil passage 13 Needle bearing 15 oil passage 16, 17 Supply hole 20 Spherical bearing 20A oil groove 21 needle bearing 30, 32 Oil collection hole 30A step 31, 33 Lubrication hole 34 ring member 35, 36 Lubricating oil passage

─────────────────────────────────────────────────── --Continued from the front page (56) References JP 62-283256 (JP, A) JP 8-291850 (JP, A) JP 10-205601 (JP, A) JP 10- 205599 (JP, A) JP 10-220544 (JP, A) JP 11-247954 (JP, A) JP 11-257451 (JP, A) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16H 15/38 F16H 57/04

Claims (12)

(57) [Claims] 1. A pair of trunnions, which are arranged opposite to each other and are displaceable in the axial direction and about an axis, and a pivot shaft which is sandwiched between the facing surfaces of an input / output disk and whose base end is swingably supported by the trunnion. A power roller rotatably supported by the power roller and the opposite trunnion, and a swingable link; and a relative rotation of the trunnion and the link, which is interposed at the linking position of the trunnion and the link. A toroidal type continuously variable transmission including a bearing member that allows rocking, wherein a lubrication means for supplying lubricating oil to the bearing member is formed inside the trunnion. 2. The bearing member is formed of a spherical bearing which allows relative swinging of the trunnion and the link, and a roller bearing which is interposed between an inner circumference of the spherical bearing and an outer circumference of the trunnion. The toroidal type continuously variable transmission according to claim 1, wherein the means supplies lubricating oil to the inner circumference of the roller bearing. 3. The toroidal type continuously variable transmission according to claim 2, wherein the lubricating means guides the lubricating oil scattered from the power roller or the bearing of the power roller to the bearing member. 4. The toroidal type continuously variable transmission according to claim 1, wherein the lubrication means communicates with a hydraulic pressure supply source. 5. The lubricating means includes a hole formed in a trunnion facing the bearing of the power roller, and a lubricating hole communicating from the hole with an outer periphery of the trunnion facing the roller bearing. The toroidal type continuously variable transmission according to claim 3. 6. The toroidal type continuously variable transmission according to claim 5, wherein the lubricating hole is inclined in the direction of gravity from the hole toward the outer periphery of the trunnion. 7. The toroidal type continuously variable transmission according to claim 5, wherein the lubrication hole is opened on the outer periphery of the trunnion which is separated from the load point of the link and the trunnion by a predetermined angle in the circumferential direction. 8. The lubricating hole opens on the outer periphery of the trunnion, which is separated from the load point of the link and the trunnion by a predetermined angle in the circumferential direction, and the ratio of the opening area or inner diameter of the lubricating hole to the length of the roller is The toroidal type continuously variable transmission according to claim 5, wherein the toroidal type continuously variable transmission is set to a value equal to or less than a predetermined value that does not hinder the rotation of the roller bearing . 9. The lubrication hole is a load of a link and a trunnion.
On the outer circumference of the trunnion, which is a predetermined angle away from the point in the circumferential direction
When opening, the opening area or inner diameter of the lubrication hole
The ratio of the roller length is the surface pressure of the roller bearing at the load point.
Characterized by being set below a predetermined value that does not exceed the maximum surface pressure
The toroidal type continuously variable transmission according to claim 5 . 10. The link connects the upper end sides of the trunnions facing each other, while the hole is formed at the upper end of the trunnion in the axial direction of the trunnion so as to extend from the connection position with the lubricating hole. Is equipped with a stepped part that reduces the inner diameter
Toroidal type continuously variable transmission according to claim 5, characterized in that there was e. 11. A trunnion in which the links face each other.
While connecting the upper end side of the, the hole portion of the trunnion
It is formed by penetrating in the axial direction of the trunnion at the upper end,
An annular member is provided at a connection position with the slide hole.
The toroidal type continuously variable transmission according to claim 5 . 12. The spherical bearing is provided on a surface facing a roller bearing.
The toro according to claim 2, wherein an oil groove is formed.
Idal type continuously variable transmission.