JP3402501B2 - Gear ratio control device for 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 a gear ratio control device for a toroidal type continuously variable transmission, and more particularly to a gear ratio control device for changing the gear ratio by hydraulic control.

[0002]

2. Description of the Related Art A toroidal type continuously variable transmission mounted on an automobile or the like includes an input disk to which an engine output is input, an output disk coaxially arranged with the input disk, the output disk and the input disk. And a power roller arranged so as to be tiltable in a state of being in contact with both disks, and by tilting the power roller, a contact position with respect to both disks is changed to adjust the gear ratio steplessly. However, there is a toroidal type continuously variable transmission of this type in which the gear ratio is changed by hydraulic control.

According to Japanese Patent Laid-Open No. 61-119866, for example, a pair of left and right power rollers arranged in contact with each other between input and output disks are rotatably supported by roller supporting members (trunnions). The three-layer structure includes a hydraulic cylinder that slides each trunnion, a valve body, a sleeve that is axially movably inserted in the valve body, and a spool that is axially movably inserted in the sleeve. The gear ratio control valve is provided, and the gear shift actuator disposed in one extension direction of the gear ratio control valve is operated during gear shifting, thereby moving the sleeve in the axial direction and operating pressure to the hydraulic cylinder. And the amount of movement of the trunnion accompanying the tilting of the power roller is controlled by the gear ratio control valve. By transmitting to the spool via a transmission mechanism composed of an L-shaped link arranged in one extension direction, the supply and discharge of the working pressure is stopped when the target gear ratio corresponding to the movement amount is realized. The configuration is shown.

[0004]

However, when the gear ratio control valve has a three-layer structure of a valve body, a sleeve and a spool as in the prior art described in the above publication, there is a large amount of hydraulic oil leakage. Therefore, the drive loss of the oil pump increases.

Moreover, since the transmission ratio control valve, the transmission actuator and the transmission mechanism are arranged in series, the overall length becomes long and the layout is deteriorated. Also,
If the axis ratios of the gear ratio control valve and the gear shift actuator do not coincide with each other with high accuracy, the gear ratio control valve will not operate stably, and therefore a high degree of mounting accuracy will be required.

The present invention comprises a roller support member for supporting the power roller arranged between the input and output disks, and a gear ratio control valve for controlling the supply / discharge of the operating pressure to / from the hydraulic chamber for sliding the roller support member. , A gear ratio of a toroidal type continuously variable transmission in which the amount of movement of the roller support member associated with the feeding / discharging operation of the gear ratio control valve operated by the drive means is transmitted to the gear ratio control valve via transmission means. The present invention addresses the above problem in a control device, and an object thereof is to make a gear ratio control device of this type inexpensive and compact.

[0007]

That is, the invention according to claim 1 of the present application (hereinafter, referred to as the first invention) includes an input disk and an output disk that are coaxially opposed to each other, and is disposed between both disks. A power roller that changes a gear ratio between the two disks depending on a contact position with these disks, a roller support member that supports the power roller, and supply / discharge of operating pressure to / from a hydraulic chamber that slides the roller support member is controlled. In a toroidal type continuously variable transmission having a gear ratio control valve, the gear ratio control valve is
The sliding member is composed of a fixed member for switching the oil passage by relative movement of the both and one slide member, and the gear ratio control valve, a drive means for operating the slide member, and the amount of movement of the roller support member to the slide member. And a transmission means for transmitting the elements such that the action directions of the respective elements are substantially parallel to each other via the lever member , and one of these elements is a lever.
-In the middle of the member, the remaining two elements are
Opposite to the above-mentioned one element across the lever member
Are arranged so that they are located at both ends of the
The feature is that the end of each element is brought into contact with the lever member
And

[0008] The invention according to claim 2 of the present application (hereinafter,
In the structure of the first invention , the transmission means is arranged in the middle of the lever member, and the transmission ratio control valve and the driving means are arranged on both end sides, respectively. To the end of the gear ratio control valve that is also in contact with the lever member, and the distance from the end of the transmission unit to the end of the drive unit that is also in contact with the lever member are substantially the same. It is characterized by

The invention according to claim 3 of the present application (hereinafter,
Hereinafter, referred to as the third invention) is the same as the first invention or the second invention.
In the configuration, the transmission means is fixed to the roller support member at one end.
It comes into contact with the installed precess cam and the other end touches the lever member.
It is characterized in that it is composed of L-shaped links in contact with each other.

Further, the invention according to claim 4 of the present application (hereinafter,
Below, it is referred to as the fourth invention) is the first invention to the third invention.
In either configuration, the transmission ratio control valve
Slide the tip of the contact member so that it contacts the lever member.
Characterized by having a spring for biasing the member
It

[0011]

According to the above structure, the following effects can be obtained.

That is, in any of the first to fourth aspects of the invention, since the gear ratio control valve and the driving means are separately arranged so that the operating directions are substantially parallel, the gear ratio control valve and the driving means are arranged. The problem that the gear ratio control valve does not operate stably if the axis centers of and does not match with accuracy is reduced, and it is not necessary to unnecessarily increase the accuracy of the gear ratio control valve, and the manufacturing cost is reduced. It will be.

Since a two-layer valve with one slide member can be used as the gear ratio control valve, the amount of hydraulic oil leak is reduced and the controllability is improved.

Moreover, since it is not necessary to arrange the gear ratio control valve, the drive means and the transmission means in series, the overall length is shortened and the structure is made compact.

Further, one element of the gear ratio control valve, the driving means and the transmission means is arranged in the middle of the lever member, and the remaining two elements are opposite to the element on both sides of the lever member. Since the elements are arranged at both ends and the ends of each element are in contact with the lever member, the connection relationship with the lever member is simplified.

In particular, according to the second aspect of the invention , the transmission means is arranged in the middle of the lever member, and the transmission ratio control valve and the driving means are arranged on opposite sides of the transmission means with the lever member interposed therebetween. The distance between the end of the transmission means and the end of the transmission ratio control valve that are in contact with the lever member is substantially the same as the distance between the end of the transmission means and the end of the drive means. Therefore, there is an advantage that the stroke amount can be easily set.

According to the third invention, one end is a roller.
The precess cam fixed to the support member serves as a transmission means.
One end of the L-shaped link is brought into contact with the other end of the L-shaped link.
By bringing them into contact, and according to the fourth aspect of the invention,
The tip of the slide member touches the lever member on the ratio control valve.
A spring that presses and urges the slide member to contact
By providing the toroidal type continuously variable transmission,
Thus, the effects of the first and second inventions are more reliably realized.
It will be.

[0018]

Embodiments of the present invention will be described below with reference to the drawings.

As shown in FIG. 1, a power train 1 for an automobile according to this embodiment has an engine 2, a torque converter 3 connected to an engine output shaft 2a, and a deceleration to which the output of the torque converter 3 is transmitted. A device 10 and a toroidal type continuously variable transmission 30 into which the output of the engine 2 is input by bypassing the torque converter 3, and the output of the speed reducer 10 or the toroidal type continuously variable transmission 30 or both of them. Is transmitted to the drive wheels (not shown) via the output shaft 4.

The torque converter 3 has a pump 3b integrated with a casing 3a connected to the engine output shaft 2a.
And a turbine 3c that is arranged to face the pump 3b and is driven by the pump 3b via hydraulic oil, and a stator 3d that is interposed between the turbine 3c and the pump 3b to perform a torque increasing action. A front end side of a hollow shaft 3f, which is externally fitted to a turbine shaft 3e that rotates integrally with the turbine 3c, is connected to the stator 3d via a one-way clutch 3g. An intermediate portion of the hollow shaft 3f extending rearward is fixed to the transmission casing 60, and a rear end portion of the hollow shaft 3f and a rear end portion of the turbine shaft 3e are connected to the speed reducer 10.
Are linked to. Further, an oil pump 5 is provided at the shaft end of a pump shaft 3h which is fitted onto the hollow shaft 3f and has one end connected to the casing 3a. The oil pump 5 is provided via the casing 3a. It is driven by the engine 2.

The speed reducer 10 has a first planetary gear mechanism 11 and a second planetary gear mechanism 12 that are coaxially arranged in series with the turbine shaft 3e, and the first planetary gear mechanism 12 is arranged on the engine 2 side. The planetary gear mechanism 11 is for backward movement, and the second planetary gear mechanism 12 is for forward movement.

The first planetary gear mechanism 11 is of a single pinion type and has a sun gear 13 coupled to the turbine shaft 3e. A carrier 15 for rotatably supporting a pinion 14 meshing with the sun gear 13 is provided. The output shaft 4 is connected to the hollow shaft 3f fixed to the transmission casing 60, and the ring gear 16 meshing with the pinion 14 is arranged on the same axis as the turbine shaft 3e via the reverse clutch 17. Are linked to.

The second planetary gear mechanism 12 is of a double pinion type, and the inner pinion 18 has the first pinion.
It is integrated with the pinion 14 of the planetary gear mechanism 11, and the sun gear 13 of the first planetary gear mechanism 11 is shared by the sun gear of the second planetary gear mechanism 12. The carrier 20 that fixedly supports the inner pinion 18 and the outer pinion 19 is integrated with the carrier 15 of the first planetary gear mechanism 11 and is fixed to the transmission casing 60 via the hollow shaft 3f. Further, the ring gear 21 constituting the second planetary gear mechanism 12 is connected to the output shaft 4 via a forward clutch 22 and a one-way clutch 23. Therefore, when the reverse clutch 17 is engaged, the output of the turbine shaft 3e is transmitted to the output shaft 4 via the first planetary gear mechanism 11 and rotationally drives the output shaft 4 in the backward direction. When the forward clutch 22 is engaged, the output of the turbine shaft 3e is transmitted to the output shaft 4 via the second planetary gear mechanism 12, and the output shaft 4
Is driven to rotate in the forward direction.

On the other hand, the toroidal type continuously variable transmission 30
Has a pair of first and second continuously variable transmission mechanisms 31 and 32 arranged in series on the output shaft 4. These continuously variable transmission mechanisms 31 and 32 have the same structure, and are arranged such that an input disk 33 rotatably provided on the output shaft 4 with respect to the shaft 4 and the input disks 33 face each other. An output disk 34 that rotates integrally with the output shaft 4, and both disks 33, 34 between the output disk 34 and the input disk 33.
And a pair of power rollers 35, 35 which are arranged so as to be rotatable and tiltable in a state of being in contact with each other.

Then, the first and second continuously variable transmission mechanisms 3
Between the input discs 33, 33 of 1, 32, an intermediate disc 36 which is rotatable relative to the input discs 33, 33 is arranged, and the intermediate disc 36 and the respective input discs 33, 33 are arranged. A plurality of loading cams 37 ... 37 are respectively interposed between and. The loading cams 37 ... 37 are configured such that the larger the input torque input from the engine 2 to each input disk 33, the greater the pressing force of each cam 37 against each input disk 33.

Further, an input shaft 51 for inputting the output of the engine 2 to each input disk 33 via the intermediate disk 36 is arranged in parallel with the output shaft 4. A first gear 52 is provided on the front end side of the input shaft 51,
The first gear 52 is meshed with an intermediate gear 53, and the intermediate gear 53 is meshed with an output gear 55 connected to the pump shaft 3h via a power distribution clutch 54. Further, on the rear end side of the input shaft 51,
Input gear 5 provided integrally with the intermediate disc 36
A second gear 57 that meshes with the gear 6 is integrally provided.
Therefore, when the power distribution clutch 54 is engaged, the output of the engine 2 bypassing the torque converter 3 is output via the input gear 56 to the first and second continuously variable transmission mechanisms 31 of the toroidal continuously variable transmission 30. , 32 are input to the input disks 33, 33, and the rotation of the input disks 33, 33 is changed at a predetermined speed ratio (reduction ratio) according to the tilt angle of the power rollers 35, ... It is adapted to be transmitted to the output disks 34, 34.

Next, the structure of the first and second continuously variable transmission mechanisms 31 and 32 constituting the toroidal type continuously variable transmission 30 will be described more specifically. Since the first continuously variable transmission mechanism 31 and the second continuously variable transmission mechanism 32 have the same configuration as described above, the first continuously variable transmission mechanism 31 will be described as a representative.

That is, as shown in FIG. 2, the first continuously variable transmission mechanism 31 is provided with first and second trunnions 38, 39 arranged in the vertical direction, and these trunnions 38, 39 are provided. Power rollers 35, 35 are rotatably supported via pivot shafts 40, 40, respectively.

On the other hand, on the support member 62 attached to the transmission casing 60 via the link post 61, the upper ends of the first and second trunnions 38 and 39 rotate via spherical bearings 63 and 63, respectively. The lower ends of the first and second trunnions 38 and 39 are spherically supported by a support member 66 which is freely supported and is attached to a partition wall 64 integral with the transmission casing 60 via a link post 65. It is rotatably supported via bearings 67, 67. The trunnion shafts 41a and 41b extending in the direction orthogonal to the output shaft 4 are integrally attached to the first and second trunnions 38 and 39, respectively. These trunnion shafts 41a, 41
The front end sides of b respectively penetrate the partition wall 64 and project into the lower space covered with the oil pan 68.

Further, the partition wall 64 is provided with first and second hydraulic cylinders 71 and 72 for sliding the first and second trunnions 38 and 39 up and down. These hydraulic cylinders 71, 72 are divided into upper hydraulic chambers 71a, 72a and lower hydraulic chambers 71b, 72b by partition walls 64a, 64a formed on the partition wall 64, respectively. Of these, the upper and lower hydraulic chambers 71 in the first hydraulic cylinder 71 on the first trunnion 38 side
Annular speed change pistons 73a and 73b, which are loosely fitted to the trunnion shaft 41a, are inserted in the a and 71b, respectively.

A thrust bearing 42 is interposed between the speed change piston 73a inserted in the upper hydraulic chamber 71a and the lower end of the first trunnion 38. In addition, the speed change piston 7 inserted in the lower hydraulic chamber 71b.
On the lower surface of 3b, a thrust bearing 43 is provided adjacent to the lower end of the trunnion shaft 41a. At the lower end portion of the trunnion shaft 41a, a recess cam 81 constituting a gear ratio control device 80, which will be described later, is spline-fitted adjacent to the thrust bearing 43 and abuts the lower surface of the boss portion. In this state, the circlip 44 mounted on the trunnion shaft 41a supports the recess cam 81 and the speed change piston 73b.

On the other hand, upper and lower hydraulic chambers 72a, 72b in the second hydraulic cylinder 72 on the second trunnion 39 side.
Also in this case, annular speed change pistons 74a and 74b, which are respectively loosely fitted to the trunnion shaft 41b, are inserted. Even in this case, the upper hydraulic chamber 72
A thrust bearing 42 is interposed between the speed change piston 74a inserted in a and the lower end of the second trunnion 39. Further, the thrust bearing 4 externally mounted on the lower end portion of the trunnion shaft 41b is provided on the lower surface of the speed change piston 74b inserted in the lower hydraulic chamber 72b.
3 are arranged adjacent to each other, and by mounting the circlip 44 on the trunnion shaft 41b in a state of being in contact with the lower end of the collar 45 arranged adjacent to the thrust bearing 43, the collar 45 and the shift piston 74b are It is supported.

Therefore, for example, the first hydraulic cylinder 71
In the lower hydraulic chamber 71b.
If it is made relatively higher than the operating pressure of
The first trunnion 38 is pushed up by the speed change piston 73a inserted in and is slid upward.
On the other hand, if the operating pressure of the upper hydraulic chamber 71a is made relatively lower than the operating pressure of the lower hydraulic chamber 71b, the trunnion shaft 41a is pushed down by the shift piston 73b inserted in the lower hydraulic chamber 71b. As a result, the first trunnion 38 slides downward.

Here, the hydraulic chambers 71 of the first and second hydraulic cylinders 71 and 72 in the first continuously variable transmission mechanism 31.
The configuration of the gear ratio control device 80 that changes the gear ratio by controlling the supply and discharge of the operating pressure with respect to a, 71b, 72a, 72b will be described in detail.

As shown in FIGS. 2 and 3, the partition wall 64 is
The valve body 83 of the gear ratio control valve 82 is fixed to the lower surface of the intermediate body 69 fixed to the lower surface of the.
The intermediate body 69 and the valve body 83 are provided with a main passage 84a to which a line pressure is supplied from a hydraulic pressure source (not shown) adjusted to a predetermined pressure, an upper hydraulic chamber 71a in the first hydraulic cylinder 71, and Second hydraulic cylinder 7
2 for supplying / discharging the working pressure to / from the lower hydraulic chamber 72b in the second hydraulic cylinder 72, and a second passage for similarly supplying / discharging the working pressure to / from the lower hydraulic chamber 71b in the first hydraulic cylinder 71 and the upper hydraulic chamber 72a in the second hydraulic cylinder 72. Passage 8
4c and a drain passage 84d for discharging the hydraulic oil are formed respectively. A spool 85 is inserted into the valve body 83 so as to be movable in the axial direction.

Here, in the valve body 83, a main port 83a communicating with the main passage 84a,
First and second supply / discharge ports 83b, 83c are formed respectively, which are in communication with the first and second passages 84b, 84c, respectively. On the other hand, the spool 85 has an annular groove 85a for selectively communicating the main port 83a with the first supply / discharge port 83b or the second supply / discharge port 83c.
Is provided.

Further, the valve body 83 is formed with a communicating portion 83d for communicating the drain oil passage 85b bored in the axial direction of the spool 85 with the drain passage 84d. Then, the first and second drain ports 85 formed on the spool 85 so as to communicate with the drain oil passage 85b.
The c and 85d selectively communicate with either of the first and second supply / discharge ports 83b and 83c as the spool 85 moves relative to the valve body 83 in the axial direction.

In this case, the main port 83a passes through the groove 85a of the spool 85 and the first supply / discharge port 8
When communicating with 3b, the communication state between the first supply / discharge port 83b and the first drain port 85c is interrupted, and at the same time, the second drain port 85d communicates with the second supply / discharge port 83c. 83a is the groove 8
When communicating with the second supply / discharge port 83c via 5a, the second supply / discharge port 83c and the second drain port 85d.
The first drain port 85c is configured to communicate with the first supply / discharge port 83b at the same time when the communication state with is cut off.

Here, as shown in FIG. 4, a stepping motor 86, which constitutes a driving means, is arranged beside the transmission ratio control valve 82. A rotary member 87 is fixed to a rotary shaft 86a of the stepping motor 86, and a drive member 88 is screwed into a screw portion 87a integrally formed at the tip of the rotary member 87. A lever member 89 is disposed between the tip of the drive member 88 and the tip of the spool 85 protruding from the gear ratio control valve 82, straddling them. One end 89a of the lever member 89 has the drive member 8
8, the other end 89b of the lever member 89 is engaged with the slit 85e at the tip of the spool 85. As a result, the drive member 88 is prevented from rotating.

On the other hand, as shown in FIG. 3, between the precess cam 81 and the lever member 89 fixedly provided on the lower end of the first trunnion 38 side of the trunnion shaft 41a, L-shaped link of the transmission means 90 is provided. The L-shaped link 90 is swingably supported via a support shaft 91 provided between the gear ratio control valve 82 and the trunnion shaft 41a, and one end 90a of the link 90 is The cam surface 81a, which is provided on the lower surface of the recess cam 81 in an inclined shape, is in contact with the cam surface 81a. Then, the other end 90b bent downward of the link 90
Is the recess 8 formed in the intermediate portion of the lever member 89.
9c is arranged in contact with.

Here, the gear ratio control valve 82 includes
A spring 92 for biasing the base end side of the spool 85 is provided. As a result, the tip of the spool 85 is urged to come into contact with the lever member 89.

In such a structure, if the stepping motor 86 is driven to move the driving member 88 to the right side (direction a) in the drawing of FIG. 4, the other end 89b of the lever member 89 has a spool. Since the biasing force of the spring 92 is acting via 85, the lever member 89 is pushed by the spool 85, and the other end 90b of the L-shaped link 90 abutting against the concave portion 89c formed in the middle portion thereof.
It rotates in the clockwise direction (direction b) with the fulcrum as the fulcrum. As a result, the spool 85 of the gear ratio control valve 82 moves to the left side (direction c) in the drawing, and as shown in FIG. 5, the main port 83 provided in the valve body 83.
a and the second supply / discharge port 83c communicate with each other via the groove 85a of the spool 85, while the first supply / discharge port 83b is provided with the first drain port 85c provided on the spool 85.
Will be connected to.

Therefore, the line pressure from the main passage 84a passes through the main port 83a, the groove 85a, the second supply / discharge port 83c and the second passage 84c, and the first pressure
While being guided to the lower hydraulic chamber 71b of the hydraulic cylinder 71 and the upper hydraulic chamber 72a of the second hydraulic cylinder 72, the operating pressure of the upper hydraulic chamber 71a of the first hydraulic cylinder 71 and the lower hydraulic chamber 72b of the second hydraulic cylinder 72 is increased. , First passage 84b, first supply / discharge port 83b, first
After passing through the drain port 85c and the drain oil passage 85b, the pressure is finally discharged through the drain passage 84d.

As a result, the first trunnion 38 in the first continuously variable transmission mechanism 31 slides downward and the second trunnion 39 slides upward, so that the first and second trunnions 38, 39 can be attached. Further, the contact position between the power rollers 35, 35 changes, and a tilting force is generated. In this case, for example, if the input disk 33 is rotating in the d direction in FIG. 2, the power roller 35 on the first trunnion 38 side is rotated in the e direction in FIG. 1, and the second trunnion 39 side is rotated. The power roller 35 rotates in the f direction. This makes the first
Input / output disks 33, 34 in the continuously variable transmission 31
The gear ratio (reduction ratio) between them will increase.

[0045] and, accompanied by the tilting of the power rollers 35
To the trunnion shaft 4 via the first trunnion 38.
1a rotates, and the rotation causes the cam surface 8 of the precess cam 81 to rotate.
One end 90a in 1a is transferred to the L-shaped link 90 in contact with, it is rotated in the counter-clockwise direction (g direction) in FIG. 6 the L-shaped link 90 as a fulcrum shaft 91. In that case, as shown in FIG. 5, one end 89a of the lever member 89 is formed.
Is in contact with the tip of the drive member 88, the other end 89b is in contact with the tip of the spool 85, and the other end 90b of the L-shaped link 90 is in contact with the recess 89c formed in the middle of the lever member 89. The lever member 89 rotates in the counterclockwise direction (h direction) with the drive member 88 as a fulcrum. As a result, the spool 85 is pushed by the lever member 89 and moves to the right (i direction) against the biasing force of the spring 96.

Then, the shifting operation further progresses, and as shown in FIG.
When the spool 85 moves to the initial position and reaches the position where the supply and discharge of the operating pressure to the first and second hydraulic cylinders 71 and 72 is stopped, the movement is stopped and the shift control is finished, as shown in FIG. To do. As a result, a predetermined target gear ratio corresponding to the operation amount of the stepping motor 86 is realized.

In this case, according to this embodiment, since the gear ratio control valve 82 and the stepping motor 86 are separately arranged so that the operating directions are substantially parallel to each other, the gear ratio control valve 82 is attached. It is not necessary to increase the accuracy more than necessary, and the manufacturing cost is reduced.

Moreover, since the gear ratio control valve 82 is a two-layer valve in which the spool 85 is inserted in the valve body 83, the leak amount of hydraulic oil is reduced and the controllability is improved. Become.

Further, since it is not necessary to arrange the gear ratio control valve 82, the stepping motor 86 and the L-shaped link 90 in series, the overall length is shortened and the structure is made compact.

Further, one element 90 of the spool 85 of the gear ratio control valve 82, the stepping motor 86, and the L-shaped link 90 is arranged in the middle of the lever member 89, and the remaining two elements are provided for this element 90. Element 85,8
6 are arranged on opposite sides of the lever member 89 on opposite sides, and the ends of the respective elements 85, 86, 90 are in contact with the lever member 89, so that the connection relationship with the lever member 89 is simple. Will be realized.

Particularly, as in the embodiment, the L-shaped link 90 is arranged in the middle 89c of the lever member 89, and the gear ratio control valve 82 and the stepping motor 86 sandwich the lever member 89 with respect to this L-shaped link 90. On the opposite side on both ends 8
9b and 89a, and the lever members 89, respectively.
The distance between the end portion 90b of the L-shaped link 90 and the tip of the spool 85 of the gear ratio control valve 82, which is in contact with
By setting the distance between the end 90b of the shaped link 90 and the tip of the driving member 88 of the step motor 86 to be substantially the same, the stroke amount can be easily set.

In this embodiment, the L-shaped link 90 is arranged at the intermediate portion of the lever member 89, and the gear ratio control valve 82 and the stepping motor 86 are arranged at both ends, but the arrangement relations thereof are exchanged. Also, substantially the same effect can be obtained.

Next, with reference to FIGS. 8 and 9 illustrates another embodiment of a support structure of the power roller.

In this embodiment, the trunnion 111
A power roller 113 is rotatably supported on a pivot shaft 112 mounted through the shaft, and a dish plate 114 is provided between the power roller 113 and the trunnion 111.

According to this structure, when the load is light, the power roller 113 is pushed by the dish plate 114 and separated from the trunnion 111 as shown in FIG. 8 , so that it passes through the center of the trunnion shaft 115. The tilt center 116 and the rotation center 11 of the power roller 113
The half-vertical angle θ with respect to 7 becomes relatively small.

On the other hand, when the load is high, as shown in FIG.
As shown in, the deformation of the dish plate 114 causes the power roller 113 to move to the trunnion side. As a result, the half-vertical angle θ becomes relatively larger than that under a light load, and it becomes possible to cope with a large input torque.

[0057]

As described above, according to the present invention, the supply / discharge of the operating pressure to / from the roller supporting member for supporting the power roller arranged between the input and output disks and the hydraulic chamber for sliding the roller supporting member is controlled. A toroidal control valve for transmitting the amount of movement of the roller support member associated with the feeding / discharging operation of the gear ratio control valve operated by the driving means to the gear ratio control valve via the transmitting means. In a continuously variable transmission, the gear ratio control valve and the drive means are arranged separately so that the operating directions are substantially parallel, so there is no need to unnecessarily increase the accuracy of mounting the gear ratio control valve. Manufacturing costs will be reduced.

Since the two-layer valve having one slide member can be used as the gear ratio control valve, the amount of hydraulic oil leak is reduced and the controllability is improved.

Moreover, since it is not necessary to arrange the gear ratio control valve, the drive means and the transmission means in series, the overall length is shortened and the structure is made compact.

Also, a slide member of the gear ratio control valve,
One element of the drive means and the transmission means is arranged in the middle of the lever member, with respect to this element, the remaining two elements are arranged on opposite sides of the lever member on opposite sides.
And since the end of each element is in contact with the lever member,
The connection relationship with the lever member is simplified.

In particular, according to the second aspect of the invention , the transmission means is arranged in the middle of the lever member, and the transmission ratio control valve and the driving means are arranged on opposite sides of the lever member with respect to the transmission means. The distance between the end of the transmission means and the end of the transmission ratio control valve that are in contact with the lever member is substantially the same as the distance between the end of the transmission means and the end of the drive means. Therefore, there is an advantage that the stroke amount can be easily set.

According to the third invention, one end is a roller.
The precess cam fixed to the support member serves as a transmission means.
One end of the L-shaped link is brought into contact with the other end of the L-shaped link.
By bringing them into contact, and according to the fourth aspect of the invention,
The tip of the slide member touches the lever member on the ratio control valve.
A spring that presses and urges the slide member to contact
By providing the toroidal type continuously variable transmission,
Thus, the effects of the first and second inventions are more reliably realized.
It will be.

[Brief description of drawings]

FIG. 1 is a skeleton diagram of an automobile power train according to the present invention.

FIG. 2 is a cross-sectional view of a first continuously variable transmission mechanism constituting the toroidal type continuously variable transmission taken along the line AA in FIG.

FIG. 3 is an enlarged cross-sectional view showing a configuration around a gear ratio control device.

FIG. 4 is a bottom view of essential parts showing the configuration of the gear ratio control device and its surroundings as viewed from the direction of the line BB in FIG.

FIG. 5 is a bottom view of a main portion of a gear ratio control device and its surroundings during gear shift control.

FIG. 6 is a cross-sectional view of relevant parts of a gear ratio control device and its periphery during gear shift control.

FIG. 7 is a bottom view of a main portion of a gear ratio control device and its periphery at the end of gear shifting.

FIG. 8 is a cross-sectional view of essential parts showing a state at light load in another embodiment of the support structure for the power roller.

FIG. 9 is a cross-sectional view of relevant parts showing a state at high load in another embodiment of the same supporting structure for the power roller.

[Explanation of symbols]

33 Input disc 34 Output disc 35 Power Roller 38 1st trunnion 39 Second trunnion 41a trunnion shaft 71 1st hydraulic cylinder 71a Upper hydraulic chamber 71b Lower hydraulic chamber 72 Second hydraulic cylinder 72a Upper hydraulic chamber 72b Lower hydraulic chamber 80 Gear ratio control device 81 Precessum 82 Gear ratio control valve 83 valve body 85 spool 86 Stepping motor 87 Rotating member 88 Drive member 89 Lever member 90 L-shaped link

Claims (4)

(57) [Claims] 1. An input disk and an output disk that are coaxially opposed to each other, a power roller that is arranged between both disks and that changes a gear ratio between both disks depending on a contact position to these disks, and this power roller. A gear ratio control device for a toroidal type continuously variable transmission, comprising: a roller support member for supporting a roller support member; and a gear ratio control valve for controlling supply and discharge of operating pressure to and from a hydraulic chamber in which the roller support member slides. The ratio control valve is composed of a fixed member for switching the oil passage by relative movement of the two and one slide member, and the speed ratio control valve, a drive means for operating the slide member, and the roller support member. And a transmission means for transmitting the movement amount of the
Through the lever member, the operating directions of the respective elements are substantially parallel , and one of these elements is
In the middle, the remaining two elements are
Located on opposite sides of the lever member with respect to one element
It is arranged so that it is located on each side of the
A gear ratio control device for a toroidal-type continuously variable transmission, characterized in that an end of an element is in contact with a lever member . 2. A transmission means arranged in the middle of the lever member, and a gear ratio control valve and a drive means on both ends thereof, respectively, and a transmission gear which abuts against the lever member from the end portion of the transmission means abutting on the lever member. the distance to the end of the ratio control valve, according to claim 1, characterized in that the distance to the end of the drive means is in contact with the same lever member from an end portion of said transmission means is approximately the same Gear ratio control device for toroidal type continuously variable transmission. 3. The transmission means has one end fixed to the roller support member.
It comes into contact with the installed precess cam and the other end touches the lever member.
A contract characterized by being composed of L-shaped links in contact with each other
A gear ratio control device for a toroidal type continuously variable transmission according to claim 1 or claim 2 . 4. A gear ratio control valve is a tip of a slide member.
Press the slide member so that the end contacts the lever member
Claims characterized by comprising a spring for biasing
A gear ratio control device for a toroidal type continuously variable transmission according to any one of claims 1 to 3 .