JP2003207011A - Toroidal type continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a toroidal type continuously variable transmission which downsizes an oil pump without a thermal problem or a drive loss problem by preventing undesired excessive lubricating oil from being suppied. <P>SOLUTION: The toroidal type continuously variable transmission comprises a power roller lubricating oil passage 5 for lubricating a bearing part of a power roller 3 via a trunnion 4, and a rolling surface lubricating oil passage 6 for lubricating rolling surfaces 1a and 2b of an input disk 1 and an output disk 2 via a post base 7. The rolling surface lubricating oil passage 6 has two systems of a lubricating oil passage 6a on the input disk side and a lubricating oil passage 6b on the output disk side for independently supplying lubricating oil to the input disk 1 side and the output disk 2 side. The rolling surface lubricating oil passage 6 having two systems is provided with a solenoid spool valve 8 for adjusting a lubricating oil amount to the rolling surface 1a of the input disk 1 and a lubricating oil amount to the rolling surface 2a of the output disk 2 in response to a power roller tilting angle. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the field of lubrication technology for a toroidal transmission unit in a toroidal type continuously variable transmission.

[0002]

2. Description of the Related Art Conventionally, as a toroidal type continuously variable transmission, for example, one described in JP-A-11-210855 is known.

In this prior art publication, an oil passage provided in the post base of the upper link is branched and opened on the outer surface of the post so that the lubricating oil (traction oil) can be sufficiently supplied to the toroidal transmission. A configuration for supplying lubricating oil to the power roller rolling surface of the output disk is described.

[0004]

However, in the conventional toroidal type continuously variable transmission, the amount of oil supplied to both the input and output disks is evenly provided, resulting in inefficient cooling. .

This point will be described in detail. The main heat sources of the toroidal type continuously variable transmission are the input / output disk, the rolling portion of the power roller, and the bearing portion of the power roller. In particular, in the case of a half toroidal type continuously variable transmission such as the conventional example, a very large thrust force for generating a traction force acts on the power roller bearing part, and for the power roller inner ring, the rolling part. It has a heat source on both sides of the bearing and it is in a very thermally severe environment.

Therefore, in addition to the lubricating oil path for supplying the input / output disk and the rolling surface of the power roller via the post base of the upper link, the power roller bearing is supplied to the inside of the power roller via the trunnion. Etc. there is a lubricating oil route. Then, the lubricating oil from either path finally reaches the rolling surface of the input / output disk.

Of these, the oil that has passed through the trunnion passes through the inside of the power roller and is therefore at a high temperature when it reaches the rolling surface. Therefore, the oil that passes through the post base is required to have the action of cooling the oil that has reached this high temperature.

However, since the oil passing through the trunnion is ejected from between the outer ring and the inner ring of the power roller, when the power roller tilt angle is at the maximum gear ratio position (LOW position), the oil shown in FIG. ), It is not ejected on the rolling surface of the output disc. On the other hand, when the power roller tilt angle is at the minimum gear ratio position (HIGH position), it is not ejected onto the rolling surface of the input disc as shown in FIG.

Therefore, it is useless to supply the oil from the post base to the output disc when the power roller tilt angle is at the maximum gear ratio position. Further, it is useless to supply the oil from the post base to the input disk when the tilt angle of the power roller is at the minimum gear ratio position.

Therefore, in the prior art in which the amount of oil for cooling the high temperature oil is always applied to the rolling surface of the input / output disk evenly, a wasteful amount of oil is consumed and the oil is unnecessarily used. This leads to an increase in the size of the pump.

The present invention has been made in view of the above problems, and its purpose is to prevent excessive supply of lubricating oil that is not necessary, thereby causing problems of thermal problems and drive losses. An object of the present invention is to provide a toroidal-type continuously variable transmission that can achieve miniaturization of an oil pump without causing any problems.

[0012]

In order to achieve the above object, according to the present invention, a first lubricating oil passage for lubricating a bearing portion of a power roller via a trunnion and an input disk via a post base are provided. In a toroidal type continuously variable transmission having a second lubricating oil passage for lubricating the rolling surface of the output disc, the second lubricating oil passage is provided for the input disc side and the output disc side independently of each other. An oil passage having two input-disk-side lubrication oil passages and an output-disc-side lubrication oil passage to be supplied, and a second lubrication oil passage having these two passages is provided on the input disc rolling surface according to the tilt angle of the power roller. A lubricating oil amount control means for adjusting the amount of lubricating oil to the output disk and the amount of lubricating oil to the output disk rolling surface is provided.

[0013]

As described above, according to the present invention, the amount of lubricating oil applied to the input disk rolling surface and the amount of lubricating oil applied to the output disk rolling surface are changed according to the power roller tilt angle (= gear ratio). home,
By ensuring that one has a sufficient amount of oil for cooling and the other has an amount of oil that decreases (including zero oil),
The oil pump can be miniaturized by preventing unnecessary supply of excessive lubricating oil without causing a thermal problem or a drive loss problem.

[0014]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments for realizing the toroidal type continuously variable transmission of the present invention will be described below with reference to claims 1, 2, 3, and 4.
The first embodiment corresponding to the invention according to claim 1 and claims 1, 2,
A second embodiment corresponding to the invention according to claims 3 and 5, and claim 1
A third embodiment corresponding to the invention according to 2, 3, 6 and a fourth embodiment corresponding to the invention according to claims 1, 2, 7, 8 and an invention according to claims 1, 2, 7, 9 The fifth embodiment will be described below.

(First Embodiment) First, the structure will be described. FIG. 1 is a schematic side view showing a rolling surface lubrication system of a toroidal type continuously variable transmission according to a first embodiment, and FIG. 2 is a schematic view showing a power roller lubrication system of a toroidal type continuously variable transmission according to the first embodiment. It is a top view. 1 and 2, reference numeral 1 is an input disk, 2 is an output disk, 3 is a power roller, 4 is a trunnion, 5 is a power roller lubricating oil passage (first lubricating oil passage), and 6 is a rolling roller. The moving surface lubricating oil passage (second lubricating oil passage), 7 is a post base, 8 is an electromagnetic spool valve (lubricating oil amount control means and spool valve means), and 9 is a TCVT control unit (electronic control means).

Engine torque is input to the input disk 1 after passing through an engine, a torque converter, a forward / reverse switching mechanism, and an input shaft (not shown). A power roller 3 is interposed between the input disk 1 and the output disk 2 and is in contact with the rolling surfaces 1a and 2a of the disks 1 and 2 via an oil film. Then, the rotational driving torque from the input disk 1 is shifted at a gear ratio determined by the tilt angle of the power roller 3, and is output from the output disk 2 via an output gear or the like (not shown). In the toroidal type continuously variable transmission of the first embodiment, as shown in FIGS. 1 and 2, the input / output disks 1 and 2 having rolling surfaces facing each other and a toroidal transmission section formed by a power roller 3 are coaxially arranged. Two sets are arranged.

The power roller 3 is rotatably supported by the trunnion 4, and has a power roller inner ring 3a, a power roller outer ring 3b, and a power roller bearing 3c, as shown in FIG. Composed. The power roller inner ring 3a contacts the rolling surfaces 1a and 2a of the input / output disks 1 and 2. The power roller outer ring 3b supports the thrust load received by the power roller inner ring 3a on the power roller housing surface of the trunnion 4. The power roller bearing 3c is interposed between a raceway surface formed on the power roller inner ring 3a and a raceway surface formed on the power roller outer ring 3b.

The trunnion 4 rotatably supports the power roller 3. The upper end of the trunnion 4 is supported by an upper link (not shown) and the lower end thereof is supported by a lower link (not shown), and is slightly displaced vertically in the tilt axis direction by a hydraulic servo piston. That is, when the trunnion 4 is displaced in the tilt axis direction, the rotation center axis position of the power roller 3 is offset from the disk center axis position, and a side slip force is generated in the power roller 3. The side slip force is used as the tilting force, the tilting angle of the power roller 3 changes, and a gear shifting operation is performed to change the gear ratio determined by the tilting angle of the power roller.

As shown in FIG. 2, the power roller lubricating oil passage 5 lubricates the bearing portion of each power roller 3 via the trunnion 4, and the high temperature lubricating oil passing through the bearing portion is supplied to the power roller. It is discharged from the bearing gap between the inner ring 3a and the power roller outer ring 3b.

As shown in FIG. 1, the rolling surface lubricating oil passage 6 lubricates the rolling surfaces 1a, 2a of the input disk 1 and the output disk 2 via the post base 7. The rolling surface lubrication oil passage 6 has two systems of an input disc side lubrication oil passage 6a and an output disc side lubrication oil passage 6b for independently supplying lubrication oil to the input disc 1 side and the output disc 2 side, respectively. ing.

The post base 7 serves both as a support member for an upper link fixed to a transmission case (not shown) and a member for ejecting lubricating oil to the rolling surface, and hangs down to the intermediate upper position of the input / output disks 1 and 2. Arranged in a state. Open ends of the post base 7 which are respectively connected to the input disc side lubricating oil passage 6a and the output disc side lubricating oil passage 6b are opened toward the rolling surface 1a of the input disc 1 and the rolling surface 2a of the output disc 2. Has been done.

The electromagnetic spool valve 8 is provided in the rolling surface lubricating oil passage 6 having the input disc side lubricating oil passage 6a and the output disc side lubricating oil passage 6b, and the electromagnetic spool valve 8 of the input disc 1 is changed in accordance with the tilt angle of the power roller. The amount of lubricating oil to the rolling surface 1a and the amount of lubricating oil to the rolling surface 2a of the output disk 2 are adjusted, respectively.
That is, the electromagnetic spool valve 8 reduces the amount of lubricating oil to the rolling surface 2a of the output disk 2 when the gear ratio determined by the power roller tilt angle is near the maximum gear ratio (LOW). Further, the electromagnetic spool valve 8 reduces the amount of lubricating oil to the rolling surface 1a of the input disk 1 when the gear ratio determined by the power roller tilt angle is near the minimum gear ratio (HIGH). The gear ratio may be calculated not only by the tilt angle of the power roller but also by the ratio of input / output rotation speed.

The electromagnetic spool valve 8 is provided at an intermediate position of the rolling surface lubricating oil passage 6, and is provided with a valve hole 8a and a spool 8a.
b, the input port 8c, the first output port 8d, the second output port 8e, the solenoid 8f, and the spring 8g.
And. The spool 8b is slidably arranged in the valve hole 8a. The input port 8c communicates with the lubricating oil supply oil passage 6c. The first output port 8d is
It communicates with the lubricating oil passage 6a on the input disc side. The second output port 8e communicates with the output disk side lubricating oil passage 6b. The solenoid 8f applies a variable solenoid force that causes the spool 8b to stroke upward in the drawing. The spring 8g applies a constant spring force that causes the spool 8b to stroke downward in the drawing. That is, the input port 8c
The amount of oil from is distributed to the first output port 8d and the second output port 8e according to the position of the spool 8b.

The TCVT control unit 9 is
In the lubricating oil control unit, based on the gear ratio information such as the target gear ratio command read from the gear shift control unit, an electronic device that outputs an energization command for obtaining a solenoid force corresponding to the gear ratio to the solenoid 8f of the electromagnetic spool valve 8 is output. It is a control means.

Next, the operation will be described.

In the lubricating oil control section of the TCVT control unit 9, as shown in FIG. 3, in the LOW gear ratio range in which the gear ratio is larger than i1, the oil amount to the input disk 1 is increased and the oil amount to the output disk 2 is increased. In the HIGH gear ratio range in which the gear ratio is smaller than i2, a stepwise oil amount control is performed in which the oil amount to the input disk 1 is reduced and the oil amount to the output disk 2 is increased.

FIGS. 1 and 2 show the state in the LOW gear ratio region. In this state, the oil discharged from the power roller 3 hits only the input disc 1 and the input disc 1 is likely to reach a high temperature. The amount of oil supplied to the lubricating oil passage 6a is increased. That is, the solenoid 8f is not energized, the spring 8g presses the spool 8b to the lower side shown in FIG. 1, and the port opening of the electromagnetic spool valve 8 has a relationship of 8d> 8e.

On the other hand, in the HIGH gear ratio region, the oil discharged from the power roller 3 hits only the output disk 2 and the output disk 2 is likely to reach a high temperature.
Increase the amount of oil supplied to b. That is, the solenoid 8
By appropriately energizing f, the spring force is overcome and the spool 8b moves to the upper side shown in FIG.
The port opening of is in the relationship of 8d <8e.

Further, in the case of the intermediate gear ratio region, the oil discharged from the power roller 3 hits both the disks 1 and 2 in the same manner, and is placed in the same thermal environment between the input and output disks 1 and 2. , 8f solenoid to balance spring force
Energizing the spool 8 to the intermediate position shown in FIG.
b, and the port opening of the solenoid spool valve 8 is 8d =
The relationship is 8e.

Therefore, in the LOW gear ratio region in which the high temperature lubricating oil is discharged to the rolling surface 1a, sufficient lubricating oil is supplied to the necessary input disk 1 side, and the high temperature lubricating oil is supplied to the rolling surface 2a. In the HIGH gear ratio area to be discharged, the required output disc 2
By supplying sufficient lubricating oil to the side, thermal problems and drive loss problems due to insufficient amount of lubricating oil do not occur.

On the other hand, in the LOW gear ratio region where high temperature lubricating oil is discharged to the rolling surface 1a, unnecessary lubricating oil supply to the output disk 2 side which is not necessary is prevented, and the high temperature lubricating oil is In the HIGH gear ratio region discharged to 2a, by preventing unnecessary supply of lubricating oil to the input disk 1 side which is not necessary,
It is possible to reduce the size of the oil pump by reducing the amount of lubricating oil to one of the disk rolling surfaces, which requires less amount of lubricating oil, to reduce the total amount of lubricating oil.

The lubricating oil control section of the TCVT control unit 9 may perform proportional oil amount control as shown in FIG. 4 instead of the stepwise oil amount control shown in FIG.
As shown in FIG. 4, this proportional oil amount control is the same control as in FIG. 3 for the LOW gear ratio range and the HIGH gear ratio range, but in the intermediate gear ratio range from i2 to i1. Is controlled such that the oil amount is gradually decreased or increased. Therefore, as compared with the case of performing the stepwise oil amount control shown in FIG. 3, it is possible to perform finer optimization of disk cooling.

This point will be described in detail. In the case of LOW gear ratio, the position where the hot oil discharged from the power roller hits the disc is the innermost side, and as the gear ratio shifts to the HIGH side, the hit position shifts to the outer peripheral side. This means that the contact time and area become smaller toward the outer peripheral side, and the influence on the temperature of the disk rolling surface becomes smaller. In other words, even if the oil discharged from the power roller hits, the amount of lubrication required will decrease as it shifts to the HIGH side.Therefore, control the amount of lubricating oil in the intermediate gear ratio range between the LOW gear ratio range and the HIGH gear ratio range. By doing so, more efficient cooling can be performed, and it is possible to prevent the pump from increasing in size and driving loss.

Next, the effect will be described.

In the toroidal type continuously variable transmission of the first embodiment, the effects listed below can be obtained.

(1) Power roller lubricating oil passage 5 for lubricating the bearing portion of the power roller 3 via the trunnion 4.
And a rolling surface lubricating oil passage 6 for lubricating the rolling surfaces 1a and 2b of the input disk 1 and the output disk 2 via the post base 7, the toroidal type continuously variable transmission having the rolling surface lubrication. The oil passages 6 are two systems of an input disc side lubricating oil passage 6a and an output disc side lubricating oil passage 6b which supply lubricating oil to the input disc 1 side and the output disc 2 side independently.
In the rolling surface lubricating oil passage 6 having two systems, the amount of lubricating oil to the rolling surface 1a of the input disk 1 and the lubrication to the rolling surface 2a of the output disk 2 according to the tilt angle of the power roller. Since the electromagnetic spool valve 8 for adjusting the amount of oil is provided, the unnecessary excessive supply of lubricating oil is prevented, thereby achieving miniaturization of the oil pump without causing a thermal problem or a drive loss problem. be able to.

(2) The electromagnetic spool valve 8 reduces the amount of lubricating oil to the rolling surface 2a of the output disc 2 when the gear ratio determined by the power roller tilt angle is near the maximum gear ratio, and the power roller tilt angle When the gear ratio determined by is close to the minimum gear ratio, the amount of lubricating oil to the rolling surface 1a of the input disk 1 is reduced, so that the high temperature lubricating oil is discharged to the outside via the bearing portion of the power roller 3. The amount of lubricating oil to the input / output disks 1 and 2 on the side can be reduced.

(3) The electromagnetic spool valve 8 is interposed in the middle of the rolling surface lubricating oil passage 6 and communicates with the spool 8b slidably arranged in the valve hole 8a and the lubricating oil supply oil passage 6c. Input port 8c, a first output port 8d communicating with the input disc side lubricating oil passage 6a, and a second output port 8e communicating with the output disc side lubricating oil passage 6b. Is distributed to the first output port 8d and the second output port 8e according to the position of the spool 8b, so that the total lubricating oil amount supplied is kept constant and the input disk side lubricating oil is maintained. It is possible to control increase / decrease of the amount of oil to the passage 6a and the output disc side lubricating oil passage 6b. In addition, even if there are a plurality of sets of toroidal transmissions, as in the first embodiment, there are two sets of toroidal transmissions composed of the input / output disks 1 and 2 and the power roller 3. With this, the amount of oil can be adjusted easily and reliably.

(4) Since the spool valve means is the electromagnetic spool valve 8 driven by the TCVT control unit 9 which controls the valve based on the gear ratio information, it does not require any other component and is simple and easy. It is possible to control the amount of lubricating oil freely.

(Second Embodiment) In the second embodiment, the first spool valve 11 driven by the cam mechanism 10 and the link mechanism 12 provided on the trunnion shaft portion 4a of the trunnion 4.
This is an example using (lubricating oil amount control means and spool valve means).

That is, as shown in FIG. 5, the first spool valve 11 is provided at an intermediate position of the rolling surface lubricating oil passage 6, and has a valve hole 11a, a spool 11b, an input port 11c, and a first port 11c. It has one output port 11d, a second output port 11e, and a spring 11f. The spool 1
1b is slidably arranged in the valve hole 11a. The input port 11c communicates with the lubricating oil supply oil passage 6c.
The first output port 11d communicates with the input disk side lubricating oil passage 6a. The second output port 11e communicates with the output disk side lubricating oil passage 6b. The spring 11f
Applies a constant spring force that causes the spool 11b to stroke to the left in the drawing. That is, the amount of oil from the input port 11c is distributed to the first output port 11d and the second output port 11e according to the position of the spool 11b.

Then, the upper link 1 of the trunnion 4
Among the trunnion shaft portion 4a supported by 3 and the trunnion shaft portion 4b supported by the lower link 14, the trunnion shaft portion 4a on the upper end side is provided with the cam mechanism 10. The first end 12a that abuts along the cam surface 10a of the cam mechanism 10.
The link mechanism 12 having is arranged. The link mechanism 12 is swingable around the rotation shaft portion 12b,
The second end 12c on the side opposite to the first end 12a has the first end
The spool end 11g of the spool valve 11 of FIG. The rest of the configuration is the same as that of the first embodiment, so the explanation is omitted.

Next, the operation will be described.

First, the trunnion 4 rotates about the trunnion shaft portions 4a and 4b in response to the shift. The cam surface 10 of the cam mechanism 10 integrally fixed to the trunnion 4
The opening control by the first spool valve 11 can be performed via the link mechanism 12 according to the change in the gradient of a. That is, the spool operation of the first spool valve 11 is defined by setting the gradient of the cam surface 10a of the cam mechanism 10, and the rolling surface supply oil amount characteristic as shown in FIGS. 3 and 4 can be created.

Of course, the cam mechanism 10 and the link mechanism 12 may be provided in one trunnion 4, and in FIG. 5, the cam mechanism 10 is provided in the trunnion shaft portion 4a on the upper end side protruding upward. However, if the cam surface gradient can be formed according to the rotation of the trunnion 4 for the convenience of layout without using this set position, the trunnion shaft portion 4b may be provided, for example.

Next, the effect will be described.

In the toroidal type continuously variable transmission of the second embodiment, in addition to the effects of (1), (2) and (3) of the first embodiment,
The following effects can be obtained.

(5) The spool valve means is connected to the trunnion shaft 4
Since the first spool valve 11 driven by the cam mechanism 10 and the link mechanism 12 provided in a is used, the spool operation of the first spool valve 11 is performed by rotating the trunnion 4 (= power roller 3 This means that the amount of lubricating oil can be controlled mechanically and reliably without detecting the tilt angle of the power roller and the gear ratio.

(Third Embodiment) The third embodiment is a second spool valve driven by utilizing the thrust of oil scattered by the centrifugal force to the outer peripheral side along the rolling surface 2a of the output disk 2. 15
This is an example using (lubricating oil amount control means and spool valve means).

That is, as shown in FIG. 6, the second spool valve 15 is provided at an intermediate position of the rolling surface lubricating oil passage 6, and has a valve hole 15a, a spool 15b, an input port 15c, and a first port 15c. 1 output port 15d, 2nd output port 15e, spring 15f, oil receiving plate 15g,
Have. The spool 11b is slidably arranged in the valve hole 11a. The input port 15c communicates with the lubricating oil supply oil passage 6c. The first output port 15d
Communicates with the input disk side lubricating oil passage 6a. The second
Output port 15e communicates with the output disk side lubricating oil passage 6b. The spring 15f applies a constant spring force that causes the spool 15b to stroke downward in the drawing. The oil receiving plate 15g is fixed to the end of the spool 15b, and is arranged at the outer peripheral position on the rolling surface shape extension line of the output disk 2. That is, the oil amount from the input port 15c is changed to the first output port 15d according to the position of the spool 15b.
And the second output port 15e. The rest of the configuration is the same as that of the first embodiment, so the explanation is omitted.

Next, the operation will be described.

On the LOW side of the gear ratio, the oil discharged from the power roller 3 hits only the input disk 1 and the amount of oil scattered on the input disk 1 side is large, and on the output disk 2 side, the oil scattered by centrifugal force is small. The amount of thrust is small and the thrust received by the oil receiving plate 15g cannot overcome the spring force of the spring 15f, and the spool 15b of the second spool valve 15 is at the position shown in FIG. The amount of oil supplied is large, and the amount of oil supplied to the rolling surface 2a of the output disk 2 is maintained small.

Then, when the gear ratio shifts from the LOW side to the HIGH side and the oil discharged from the power roller 3 comes into contact with the rolling surface 2a of the output disk 2, the rolling surface 2a of the output disk 2 suddenly hits. The amount of oil scattered along increases, and the thrust received by the oil receiving plate 15g increases. That is,
When the gear ratio is higher and the oil discharge is closer to the inner peripheral side of the output disc 2, the amount of oil reaching the oil receiving plate 15g provided on the rolling surface shape extension line increases,
Based on the change in the thrust, the spool 15b strokes upward in FIG. 6, the amount of oil supplied to the rolling surface 1a of the input disk 1 decreases, and the amount of oil supplied to the rolling surface 2a of the output disk 2 increases. To do.

Next, the effect will be described.

In the toroidal type continuously variable transmission of the third embodiment, in addition to the effects of (1), (2) and (3) of the first embodiment,
The following effects can be obtained.

(6) Since the spool valve means is the second spool valve 15 driven by utilizing the thrust of the oil scattered by the centrifugal force to the outer peripheral side along the rolling surface 2a of the output disk 2, The oil amount control is realized with a simple configuration, and it has an advantage that it can be constructed at low cost.

(Fourth Embodiment) In the fourth embodiment, a rotary type first opening area control valve 16 (lubricating oil amount control means and opening area changing means) which moves in conjunction with rotation of the trunnion shaft portion 4a due to speed change. ) Is an example of controlling the amount of lubricating oil.

That is, as shown in FIGS. 7 and 8, the first opening area control valve 16 has two input disk side opening oil passages 6d (opening oil passages) branched from the rolling surface lubricating oil passage 6. A post base 7 in which an output disk side opening oil passage 6e (opening oil passage) is formed, a cylindrical member 17 (cylindrical member) provided at an outer peripheral position of the post base 7, and the cylindrical member 1
7 has two input disk-side lubricating oil outflow openings 17a (lubricating oil outflow openings) and an output disk-side lubricating oil outflow opening 17b (lubricating oil outflow openings). The cylindrical member 17 is positioned with respect to the post base 7 by a snap ring 18.

The trunnion shaft portion 4a is connected to the trunnion shaft portion 4a via a wire 19 (rotation transmitting element), and the input disc is rotated in accordance with the rotational displacement of the cylindrical member 17 utilizing the rotation of the trunnion shaft portion 4a due to the shift. Two opening areas determined by the relative positional relationship between the side opening oil passage 6d and the input disk side lubricating oil outflow opening 17a, and the output disk side opening oil passage 6e and the output disk side lubricating oil outflow opening 17b are changed.

At this time, the rotation angle width of the trunnion 4 is
Depending on the gear ratio range, it is generally 6 from LOW gear ratio to HIGH gear ratio.
Since it is 0 degree or more, the radius ratio of the wire 19 is set as (diameter of the trunnion shaft portion 4a) <(diameter of the cylindrical member 17), the supply direction of the lubricating oil does not change much, and
It is necessary to reduce the rotation angle of the rotary valve in order to avoid making the valve larger. As the rotation transmitting element, a belt or a chain may be used instead of the wire 19.

Next, the operation will be described.

7 and 8 show a LOW gear ratio state, in which case the input disc side opening oil passage 6d and the input disc side lubricating oil outflow opening 17a are in a fully opened state. On the other hand, the output disc side opening oil passage 6e and the output disc side lubricating oil outflow opening 17b are in a half-open state. Therefore, the amount of lubricating oil supplied to the rolling surface 1a of the input disk 1 is sufficiently secured, but the amount of lubricating oil supplied to the rolling surface 2a of the output disk 2 decreases.

When shifting from this position to the HIGH gear ratio side, that is, when the trunnion 4 rotates in the clockwise direction, the cylindrical member 17 also rotates in the clockwise direction, and the input disc side opening oil passage 6d is input. The opening area of the disk side lubricating oil outflow opening 17a changes to the closing side, and the opening area of the output disk side opening oil passage 6e and the output disk side lubricating oil outflow opening 17b changes to the opening side. And HIGH
When the gear ratio is reached, the input disc side opening oil passage 6d and the input disc side lubricating oil outflow opening 17a are in a half open state, while the output disc side opening oil passage 6e and the output disc side lubricating oil outflow opening 17b are fully opened. It becomes a state. Therefore, the amount of lubricating oil supplied to the rolling surface 1a of the input disk 1 is reduced, and the amount of lubricating oil supplied to the rolling surface 2a of the output disk 2 is sufficiently secured.

Next, the effect will be described.

The toroidal type continuously variable transmission of the fourth embodiment can obtain the following effects in addition to the effects (1) and (2) of the first embodiment.

(7) The lubricating oil amount control means is a post base 7 in which two input disc side opening oil passages 6d and an output disc side opening oil passage 6e branched from the rolling surface lubricating oil passage 6 are formed.
A cylindrical member 17 provided at the outer peripheral position of the post base 7, two input disk side lubricating oil outflow openings 17a and an output disk side lubricating oil outflow opening 17b formed in the cylindrical member 17. Since the first opening area control valve 16 has the first opening area control valve 16 that changes the two opening areas according to the displacement of the cylindrical member 17, the rotary valve is incorporated in the conventional post base to change the opening area at the most downstream end. Therefore, it is not necessary to newly provide a valve means in the oil passage as in the methods of the first to third embodiments, and it is not necessary to branch the oil passage into two in the middle of the housing or the like. Since it does not exist, it is advantageous in layout.

(8) The first opening area control valve 16 is connected to the trunnion shaft portion 4a through the wire 19, and the cylindrical member 1 which utilizes the rotation of the trunnion shaft portion 4a by shifting.
Along with the rotational displacement of 7, the input disk side opening oil passage 6d, the input disk side lubricating oil outflow opening 17a, the output disk side opening oil passage 6e, and the output disk side lubricating oil outflow opening 17b are determined by the relative positional relationship. Since the two opening areas are changed, the first opening area control valve 16 can be simply configured by utilizing the rotation of the trunnion 4 according to the shift.

(Fifth Embodiment) In the fifth embodiment, the second opening area control valve 20 (lubricating oil amount control means and opening) which moves by utilizing the thrust of scattered oil from the rolling surface 2a of the output disk 2 is used. This is an example in which the amount of lubricating oil is controlled by the area changing means).

That is, as shown in FIG. 9, the second opening area control valve 20 causes the cylindrical member 17 to disperse the oil scattered along the rolling surface 2a of the output disk 2 by the centrifugal force on the outer peripheral side. An oil receiving member 21 for receiving is integrally provided. The input disc side opening oil passage 6d, the input disc side lubricating oil outflow opening 17a, and the output disc side opening are accompanied by the vertical movement displacement of the cylindrical member 17 utilizing the thrust of the scattered oil received by the oil receiving member 21. The two opening areas determined by the relative positional relationship between the oil passage 6e and the output disk side lubricating oil outflow opening 17b are changed. Here, the input disc side opening oil passage 6
The d and the output disc side opening oil passage 6e are formed at vertically displaced positions. The rest of the configuration is similar to that of the fourth embodiment, so the explanation is omitted.

Next, the operation will be described.

FIG. 9 shows a LOW gear ratio state. In this case, the cylindrical member 17 is at the lower end position in contact with the snap ring 18 by its own weight (a spring member which opposes may be provided if necessary), The input disk side opening oil passage 6d and the input disk side lubricating oil outflow opening 17a are fully opened. On the other hand, the output disc side opening oil passage 6e and the output disc side lubricating oil outflow opening 17b are in a half-open state. Therefore, the amount of lubricating oil supplied to the rolling surface 1a of the input disk 1 is sufficiently secured, but the amount of lubricating oil supplied to the rolling surface 2a of the output disk 2 decreases.

Then, when shifting from this position to the HIGH gear ratio side, that is, when the power roller 3 rotates in the clockwise direction, the oil discharged from the power roller 3 is output from the output disc 2.
The oil receiving member 21 starts to hit the rolling surface 2a of the
The oil scattered by the centrifugal force is received on the outer peripheral side along a.
Due to the thrust of the scattered oil, the cylindrical member 17 moves upward, the opening area of the input disc side opening oil passage 6d and the input disc side lubricating oil outflow opening 17a changes to the closing side, and the output disc side opening oil The opening area of the passage 6e and the output disk side lubricating oil outflow opening 17b changes to the open side. Then, at the HIGH gear ratio, the cylindrical member 17 moves to the upper end position, and the input disc side opening oil passage 6d and the input disc side lubricating oil outflow opening 17a are in a half-open state, while the output disc side opening oil passage is formed. 6e and the output disk side lubricating oil outflow opening 17b are fully opened. Therefore, the amount of lubricating oil supplied to the rolling surface 1a of the input disk 1 is reduced, and the amount of lubricating oil supplied to the rolling surface 2a of the output disk 2 is sufficiently secured.

Next, the effect will be described.

In the toroidal type continuously variable transmission according to the fifth embodiment, in addition to the effects (1) and (2) of the first embodiment and the effect (7) of the fourth embodiment, The following effects can be obtained.

(9) The second opening area control valve 20 includes an oil receiving member 21 for receiving oil scattered by centrifugal force on the outer peripheral side of the cylindrical member 17 along the rolling surface 2a of the output disk 2. The input disk side opening oil passage 6d, the input disk side lubricating oil outflow opening 17a, and the output disk are provided integrally with the vertical movement displacement of the cylindrical member 17 utilizing the thrust of the scattered oil received by the oil receiving member 21. Since the two opening areas determined by the relative positional relationship between the side opening oil passage 6e and the output disk side lubricating oil outflow opening 17b are changed, the number of parts is small and the layout is reasonably easy and the oil amount control is very easy. Can be realized.

The toroidal type continuously variable transmission of the present invention has been described above based on the first to fifth embodiments, but the specific structure is not limited to these embodiments, and patents Modifications and additions of the design are allowed without departing from the gist of the invention according to each claim of the claims.

For example, the present invention can be applied to a toroidal transmission having one set of toroidal transmissions and a toroidal transmission having two or more sets of toroidal transmissions.

As the lubricating oil amount control means, the lubricating oil amount to the input disk rolling surface and the output disk rolling surface are provided in the rolling surface lubricating oil passage having two systems according to the tilt angle of the power roller. It is not limited to the means shown in the first to fifth embodiments as long as it can adjust the amount of lubricating oil.

[Brief description of drawings]

FIG. 1 is a schematic side view showing a rolling surface lubrication system of a toroidal type continuously variable transmission according to a first embodiment.

FIG. 2 is a schematic plan view showing a power roller lubrication system of the toroidal type continuously variable transmission according to the first embodiment.

FIG. 3 is a characteristic diagram of rolling surface supply oil amount with respect to a gear ratio in the toroidal continuously variable transmission according to the first embodiment.

FIG. 4 is a diagram showing rolling surface supply oil amount characteristics for a gear ratio different from that in FIG. 3;

FIG. 5 is a schematic view showing a rolling surface lubrication system in a toroidal type continuously variable transmission according to a second embodiment.

FIG. 6 is a schematic view showing a rolling surface lubrication system in a toroidal type continuously variable transmission according to a third embodiment.

FIG. 7 is a schematic side view showing a rolling surface lubrication system in a toroidal type continuously variable transmission according to a fourth embodiment.

FIG. 8 is a schematic plan view showing a rolling surface lubrication system in a toroidal type continuously variable transmission according to a fourth embodiment.

FIG. 9 is a schematic side view showing a rolling surface lubrication system in a toroidal type continuously variable transmission according to a fifth embodiment.

FIG. 10 is a diagram showing an oil discharge state from a power roller at a LOW gear ratio and an oil discharge state from a power roller at a HIGH gear ratio.

[Explanation of symbols]

1 Input Disc 1a Rolling Surface 2 Output Disc 2a Rolling Surface 3 Power Roller 4 Trunnion 4a Trunnion Shaft 5 Power Roller Lubricating Oil Path (First Lubricating Oil Path) 6 Rolling Surface Lubricating Oil Path (Second Lubricating Oil) 6a Input disc side lubricating oil passage 6b Output disc side lubricating oil passage 6c Lubricating oil supply oil passage 6d Input disc side opening oil passage (opening oil passage) 6e Output disc side opening oil passage (opening oil passage) 7 Post base 8 Electromagnetic spool valve (lubricating oil amount control means and spool valve means) 9 TCVT control unit (electronic control means) 10 Cam mechanism 11 First spool valve (lubricating oil amount control means and spool valve means) 12 Link mechanism 15 Second Spool valve (lubricating oil amount control means and spool valve means) 16 First opening area control valve (lubricating oil amount control means and opening area changing means) 17 Cylindrical member (cylindrical member) 17a Input disk side lubricating oil outflow opening (lubricating oil outflow opening) 17b Output disk side lubricating oil outflow opening (lubricating oil outflow opening) 18 Snap ring 19 Wire (rotation transmitting element) 20 Second opening area control valve (lubricating oil amount control means and opening area changing means)

Claims (9)

[Claims] 1. A first lubricating oil passage for lubricating a bearing portion of a power roller via a trunnion, and a second lubricating oil passage for lubricating a rolling surface of an input disc and an output disc via a post base. In the toroidal type continuously variable transmission having :, the second lubricating oil passage has two systems of an input disc-side lubricating oil passage and an output disc for independently supplying lubricating oil to the input disc side and the output disc side, respectively. A second lubricating oil passage having a side lubricating oil passage and having the two systems described above is provided with an amount of lubricating oil to the input disk rolling surface and an amount of lubricating oil to the output disk rolling surface according to the tilt angle of the power roller. A toroidal-type continuously variable transmission characterized in that it is provided with a lubricating oil amount control means for adjusting each of the above. 2. The toroidal type continuously variable transmission according to claim 1, wherein the lubricating oil amount control means moves to the output disk rolling surface when the gear ratio determined by the power roller tilt angle is near the maximum gear ratio. Of the toroidal type continuously variable transmission which reduces the amount of lubricating oil to the input disk rolling surface when the gear ratio determined by the power roller tilt angle is near the minimum gear ratio. 3. The toroidal type continuously variable transmission according to claim 1 or 2, wherein the lubricating oil amount control means is provided at an intermediate position of the second lubricating oil passage and slides in the valve hole. A spool movably arranged, an input port communicating with a lubricating oil supply oil passage, a first output port communicating with the input disk side lubricating oil passage, and a second output port communicating with the output disk side lubricating oil passage. Output port of the toroidal type continuously variable transmission, which is a spool valve means that distributes the amount of oil from the input port to the first output port and the second output port according to the spool position. . 4. The toroidal type continuously variable transmission according to claim 3, wherein the spool valve means is an electromagnetic spool valve driven by an electronic control means that performs valve control based on gear ratio information. Toroidal type continuously variable transmission. 5. The toroidal type continuously variable transmission according to claim 3, wherein the spool valve means is a first spool valve driven by a cam link mechanism provided on the trunnion shaft portion. A toroidal type continuously variable transmission. 6. The toroidal type continuously variable transmission according to claim 3, wherein the spool valve means utilizes thrust of oil scattered by centrifugal force to an outer peripheral side along a disk rolling surface. A toroidal type continuously variable transmission characterized by being a second spool valve that is driven. 7. The toroidal type continuously variable transmission according to claim 1 or 2, wherein the lubricating oil amount control means has two opening oil passages branched from a second lubricating oil passage. A post base, a tubular member provided at an outer peripheral position of the post base, and two lubricating oil outflow openings formed in the tubular member, and with displacement of the tubular member, A toroidal type continuously variable transmission characterized by being opening area changing means for changing two opening areas determined by a relative positional relationship between an opening oil passage and a lubricating oil outflow opening. 8. The toroidal type continuously variable transmission according to claim 7, wherein the opening area changing means uses a cylindrical member as the cylindrical member, and the cylindrical member is a rotation transmitting element with respect to the trunnion shaft portion. Changing the two opening areas determined by the relative positional relationship between the opening oil passage and the opening in association with the rotational displacement of the cylindrical member utilizing the rotation of the trunnion shaft portion due to the speed change. A toroidal-type continuously variable transmission characterized in that the opening area control valve is No. 1. 9. The toroidal type continuously variable transmission according to claim 7, wherein the opening area changing means is centrifugally dispersed on the tubular member along the disk rolling surface by oil due to centrifugal force. An oil receiving member for receiving the oil, and two opening areas determined by a relative positional relationship between the opening oil passage and the opening along with the vertical movement displacement of the tubular member using the thrust of the scattered oil received by the oil receiving member. A toroidal type continuously variable transmission characterized in that it is a second opening area control valve for changing each of the above.