JPH0788880B2 - Switching valve device for toroidal type continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention controls the axial movement of a trunnion by switching the flow of pressure fluid supplied to a trunnion drive mechanism of a toroidal continuously variable transmission. The present invention relates to a switching valve device that controls a gear ratio by adjusting a tilt angle of a roller.

[Conventional technology]

In the toroidal type continuously variable transmission, as shown in FIG. 9, an input disk 1 and an output disk 2 are coaxially opposed to each other in a housing (not shown). Both discs 1,
2 have a substantially identical shape and are arranged symmetrically, and their opposing surfaces cooperate with each other to form a toroidal surface so as to have a substantially semicircular shape when viewed in an axial cross section. And input disk 1
In the toroidal cavity formed by the toroidal surface of the output disk 2, a pair of transmission rollers 3 and 4 for transmitting motion are disposed in contact with both disks 1 and 2. In this case, these transmission rollers 3 and 4 are rotatably and tiltably attached to trunnions 5 and 6 which are concave supporting structures, and the center of the tilt is the toroidal of the input / output disks 1 and 2. It is the pivot axis O which is the center of the surface. Lubricating oil with large viscous friction resistance is supplied to the contact surfaces between the disks 1 and 2 and the transmission rollers 3 and 4, and the rotational force input to the input disk 1 is output via the lubricating oil film and the transmission rollers 3 and 4. It is transmitted to the disc 2.

When shifting, the two trunnions 5 and 6 are moved a minute distance in the direction of the pivot axis O. That is, the axial movement of the trunnion disengages the rotation shafts 3a, 4a of the transmission rollers 3, 4 from the intersections of the shafts 1a, 2a of the input / output disks. Therefore, the transmission rollers 3 and 4 tilt on the curved surfaces of the input and output disks 1 and 2, and as a result, the speed ratio changes and decelerates (Fig. 9 (a)) or speeds up (9th).
Figure (b)) is performed.

The movement of the trunnions 5 and 6 in the direction of the pivot shaft O is performed by moving the spool of the speed changeover valve device in the axial direction to switch the oil passage of the hydraulic cylinder that is the trunnion drive mechanism. The tilt angle θ of the transmission rollers 3 and 4 rolling on the 6 is adjusted to a value that provides a predetermined speed ratio, and continuously variable transmission is performed.

As the switching valve device, there is a device disclosed in, for example, Japanese Patent Application Laid-Open No. 61-197850 and Japanese Utility Model Application Laid-Open No. 61-145157 proposed by the present applicant.

In the former, at least one inclined cam surface is formed on a cam disk attached to the pivot end of the trunnion, and a cam follower engaging with the inclined cam surface is rotatably arranged in the extension direction of the inclined cam surface. The spool is connected to the cam follower. Then, by rotating the cam follower by a desired angle, the cam follower moves axially from the neutral position, and accordingly, the spool moves axially from the neutral position to shift the toroidal continuously variable transmission. Therefore, the spool movement amount can be shortened and the size can be reduced.

In the latter, a tubular sleeve is provided in the valve housing so as to be slidable in the axial direction, a tubular spool is provided in the sleeve, and the spool is attached to the pivot end of the trunnion. A cam follower that engages with the cam disk is provided, and an elastic body is interposed between the cam follower and the sleeve to urge the cam follower toward the cam disk and to allow the spool to move more than the required stroke. It is characterized by wearing.

With this configuration, the relative displacement amount of the spool with respect to the sleeve can be shortened, and accordingly, the valve device as a whole can be reduced in size and weight.

[Problems to be solved by the invention]

However, of the conventional transmissions for continuously variable transmissions disclosed in Japanese Patent Laid-Open No. 61-197850, a cam disk connected to a transmission roller support structure (trunnion) and a cam disk associated therewith are disclosed. Since the cam follower (cam follower) is fitted and the spool is connected to the cam follower to change the speed, a space for accommodating the cam disk is required. Also, in order to increase the sensitivity of the spool valve to the rotation of the cam, if the lead of the cam (cam lift amount per unit rotation angle) is increased, the lead angle of the slope of the cam is increased and the radial force acting on the valve is increased. Increase and valve operation becomes awkward. In order to prevent this, the diameter of the cam disk has to be increased, and there has been a problem that the valve structure is still insufficiently downsized.

Further, in the one disclosed in Japanese Utility Model Laid-Open No. 61-145157, a tubular spool is provided in a tubular sleeve slidable in the axial direction so that an excessive stroke of the cam follower is not directly transmitted to the spool. And a cam follower that engages with a cam disk mounted on the pivot end of the trunnion is disposed in the spool, and further, a movement more than the required stroke of the spool is allowed between the cam follower and the sleeve. Since the elastic body is interposed, a space for accommodating the cam disk is required as in the above case, and the device becomes large accordingly. Moreover, there is a problem that the structure of the switching valve device becomes complicated.

Therefore, the present invention has been made by paying attention to the problems of the above-mentioned conventional example, and has a simple structure, a small number of parts, and a switching valve device for a toroidal type continuously variable transmission that can be further reduced in size and weight. The purpose is to provide.

[Means for solving problems]

To achieve the above object, the present invention controls the axial movement of a trunnion supporting a transmission roller in contact with an input / output disk by supplying a pressure fluid to a trunnion drive mechanism to control the tilt angle of the transmission roller. In a switching valve device of a toroidal type continuously variable transmission that adjusts the variable speed, a setting rotating cylinder body that is connected to a rotating mechanism and sets a tilt angle of the transmission roller, and the rotating cylinder body. A rotating / sliding cylinder body slidably contacting an inner peripheral surface or an outer peripheral surface of the body and connected to the trunnion. Multiple spiral oil passage grooves are formed in the same phase on each surface, and when both spiral oil passage grooves are disengaged, the supply of pressure fluid to the trunnion drive mechanism is cut off, and both spiral oil passage grooves communicate with each other. Occasionally, pressure fluid is supplied to the trunnion drive mechanism. Characterized in that way the.

[Action]

Now, it is assumed that the gear ratio of the toroidal continuously variable transmission is 1. When pressure fluid is not supplied to the trunnion drive mechanism, the multiple spiral oil passage grooves formed on the peripheral surface of the rotating / sliding cylindrical body form the multiple spiral threads formed on the peripheral surface of the setting rotating cylindrical body. The pressure fluid passage is blocked by the oil passage groove and the disengagement land, and no gear shifting is performed. When the rotating mechanism is operated from this state to rotate the rotating cylinder in the speed increasing direction (deceleration direction), the spiral oil passage groove moves to rotate the spiral oil passage of the rotating and sliding cylinder. Communicating with the groove, the pressure fluid passage to the acceleration side (deceleration side) of the trunnion drive mechanism opens. As a result, the trunnion is displaced in the axial direction, and the rotation axis of the transmission roller intersects with the rotation axis of the input / output disk to increase speed (decelerate).
Therefore, the transmission roller and the trunnion supporting the transmission roller are tilted toward the speed increasing side (deceleration side) so as to follow the rotation of the setting rotating cylinder, and the rotation of the input shaft is increased via the transmission roller. It is speeded (decelerated) and transmitted to the output shaft. Then, when the trunnion is tilted by the same angle as the rotation angle of the setting rotation cylinder, the rotation axis of the transmission roller and the axis of the input / output disk intersect, and the rotation cylinder for setting the switching valve device is set. And the spiral oil passage groove of the rotating and sliding cylinder completely disengages, and the supply of pressure fluid to the trunnion drive mechanism is cut off. Thus, the tilting stops and the toroidal type continuously variable transmission finishes shifting to the speed increasing side (deceleration side).

That is, at the time of gear shifting, the setting rotary cylinder is only rotated by a predetermined angle, and it is not necessary to move it in the axial direction.

Thus, the length of the setting rotary cylinder and the valve housing are minimized, and the weight thereof is reduced to reduce the overall size and weight, and the driving force of the setting rotary cylinder at the time of shifting is reduced. It reduces and improves its responsiveness.

〔Example〕

1 to 7 are views showing a first embodiment of the present invention.

1 and 2, T is a toroidal type continuously variable transmission as a continuously variable transmission, and C is a control device when the toroidal type continuously variable transmission T is used in an automobile. Is.

The toroidal type continuously variable transmission T is arranged so as to be rotatable and tiltable in contact with an input disk 1 and an output disk 2 pivotally mounted in a housing H so as to face each other, and a toroidal surface formed by the facing surfaces thereof. And a pair of transmission rollers 3 and 4 that are formed. These transmission rollers 3, 4 are mounted on trunnions 5, 6. Further, the trunnions 5 and 6 are linked by tension members 8 at both upper and lower ends via posts 7 and can be tilted in opposite directions about a pivot axis O.

Thus, when the rotational force input to the input disk 1 is transmitted to the output disk 2 via the transmission rollers 3 and 4, the trunnions 5 and 6 are moved by a minute distance in the pivot axis OO direction, and the transmission rollers are moved. The speed ratio is changed by changing the tilt angles θ of 3 and 4. Trunnion in this case 5,6
Is moved in the axial direction by hydraulic cylinders 9a to 9d as trunnion drive mechanisms provided at both ends of each trunnion 5 and 6, respectively.
It is controlled by a gear shift actuating mechanism composed of a switching valve device 10 for controlling the hydraulic pressure supply to these hydraulic cylinders 9a-9d and a rotating mechanism 11 which is a switching drive device thereof.

Here, as shown in the enlarged view of FIG. 1, the switching valve device 10 has an upper surface of the housing H at a position where a rotation shaft of a spool 14 described later is coaxial with a pivot shaft O which is a rotation center of the trunnion 6. It is fitted to and fixed by bolts 15. Inside the sleeve 13, a setting rotation cylindrical body (hereinafter referred to as a sleeve) 13 rotatably arranged to set the tilt angles of the transmission rollers 3 and 4, and the sleeve 13 is rotated by sliding contact with the inner surface of the sleeve 13. A rotatable and sliding cylindrical body (hereinafter referred to as a spool) 14 which is arranged so as to be slidable in the axial direction.

On the upper end of the valve housing 12, a rotating mechanism 11 is provided with a bolt 16
It is fixed and fitted with. Further, four pipe connection ports (oil passage holes) 12a to 12d are formed on the outer peripheral side wall so as to deviate from the respective positions and open to the inner wall. And the pipe connection port
12a is connected to an external hydraulic source via hydraulic pipe 12e
12b is connected to the oil tank via hydraulic pipe 12f, and pipe connection port 12c
Is connected to the hydraulic cylinders 9a and 9d of the toroidal type continuously variable transmission T via the hydraulic pipe 12g, and the pipe connection port 12d is connected to the hydraulic cylinders 9b and 9c of the toroidal type continuously variable transmission T via the hydraulic pipe 12h. ing.

On the outer peripheral surface of the sleeve 13, four annular oil passage grooves 13a to 1 are provided at positions facing the pipe connection ports 12a to 12d of the valve housing 12.
3d is formed. On the other hand, on the inner peripheral surface of the sleeve 13,
Four independent spiral oil passage grooves 13e to 13h are formed by, for example, spiral broaching, and the groove ends are closed by collars 13i and 13j (Fig. 3). The annular oil passage grooves 13a to 13d, the spiral oil passage grooves 13e to 13h, and the lands 13k to 13n between the spiral oil passage grooves are respectively arranged in oil passage holes 13o to 13v as shown in Tables 1 and 2. I am communicating with.

The sleeve 13 is rotatably linked to the rotating mechanism 11. That is, the upper lid 13w is attached to the upper end of the sleeve 13 by the bolt 1
The support shaft 13x, which is fixed at 7, and extends upward from the center of the upper lid 13w, is projected into the chamber of the rotating mechanism 11 through the bearing 18, the gear mounting ring 19 is fitted, and the nut 20 is tightened. The gear 21 is inserted through the gear mounting ring 19 and, for example, a disc spring 22 as a clutch for preventing overload.
After being inserted, the nut 23 is tightened to an appropriate strength. The gear 21 is rotationally driven by meshing with a gear 25 attached to the rotary shaft of a sleeve driving pulse motor 24 driven by a control signal from the control device C.

As shown in FIG. 3, the spool 14 has spiral oil passage grooves 14a, 14b, 14c, 14d of the same phase formed on the outer peripheral surface thereof so as to correspond to the spiral oil passage grooves on the inner circumference of the sleeve 13. . Each of these grooves is independent, and the groove width is the land of the sleeve 13.
The width is approximately equal to 13k to 13n, and the groove ends do not reach the end of the spool 14. Land 14e between each groove
The width of 14h is approximately equal to the groove width of the spiral oil passage grooves 13e to 13h of the sleeve 13. As a result, when the two spiral oil passage grooves 13e to 13h and 14a to 14d are completely different,
The flow of the pressure fluid to the cylinders 9a to 9d, which is the trunnion drive mechanism, is blocked, and the fluid is supplied when they communicate with each other.

A through hole 14i is formed in the center of the spool 14 in the axial direction. A spring chamber is formed in the upper half of the through hole 14i to accommodate a compression coil spring 26. The upper end of the spring 26 is a spring seat 27. It is engaged with the center of the lower surface of the upper lid 13w of the sleeve 13 via the bear rig ball 28. As a result, the spool 14 is constantly urged by the compression coil spring 26 toward the piston 9D in the hydraulic cylinder 9d, and its axial movement is restricted by the upper lid 13w of the sleeve 13 and the upper surface of the housing H. There is.

As shown in FIGS. 1 and 4, a stopper pin 29 is embedded in the lower end of the spool 14 so as to project in the outer diameter direction, while the lower end of the sleeve 13 is loosely fitted with the stopper pin 29. A recess 30 is formed as a stopper groove for
The connection mechanism 3 between the sleeve 13 and the spool 14 is formed by the both 29 and 30.
Make up one. In the coupling mechanism 31, when the sleeve 13 and the spool 14 relatively rotate, the relative rotation angle becomes excessive, and the spiral oil passage grooves 13e to 1e-1 on the inner peripheral surface of the sleeve 13 are formed.
3h and the spiral oil passage grooves 14a to 14d on the outer peripheral surface of the spool 14 are
The relative rotation angle is regulated within a predetermined range in order to prevent malfunction due to communication with another oil passage groove beyond the mutual correspondence.

Further, a triangular groove 32 is formed at the lower end of the spool 14 as shown in FIG. 5, for example. On the other hand, trunnion 6
An engagement pin 34 is projected in the radial direction at the tip of the piston rod 33 of the piston 9D fitted in the hydraulic cylinder 9d. The head of this engaging pin 34 is spherical and the triangular groove 32 is formed.
, 32 and 34 constitute a connecting means 35 for connecting the trunnion 6 and the spool 14. The connecting means 35 prevents relative displacement of the trunnion 6 and the spool 14 in the radial direction from being transmitted to each other.

Thus, the above trunnion 6, piston 9D and spool
14 constitutes a mechanical feedback means.

The control device C detects the number of revolutions of the output disk 2 and outputs a detection signal corresponding to the vehicle speed as shift control information which is a reference for selecting a speed ratio, a vehicle speed detector 41, a throttle opening detector 42, and an operation mode selection. Various detection signals are supplied from the switch 43 and the shift position detector 44, and predetermined arithmetic processing is executed based on these signals to control the pulse motor 24 for driving the sleeve so as to obtain a desired gear ratio.

Next, the operation will be described.

Now, assuming that the vehicle is in a stopped state, in this state, in preparation for the start of the vehicle, the maximum deceleration position in which the transmission rollers 3 and 4 roll against the small diameter portion of the input disc 1 and the large diameter portion of the output disc 2 respectively. Controlled by.

At this maximum deceleration position, as shown in FIG.
Is held in the neutral position, and each spiral oil passage groove 13 of the sleeve 13 is
The e to 13h and the respective spiral oil passage grooves 14a to 14d of the sleeve 14 are completely different from each other, and the oil passage hole 13 formed in the sleeve 13 is formed.
o ~ 13v is in the cutoff state. In this state, the hydraulic cylinders 9a to 9d of the toroidal type continuously variable transmission T are in equilibrium, and the trunnions 5 and 6 are in the neutral position.

From this stopped state, for example, when the shift lever is selected in the drive range, the accelerator pedal is stepped on, and the clutch is in the half-clutch state, the vehicle is started, and the control device C causes the shift position detection signal S at that time.
, A driving mode selection signal P, a throttle opening detection signal U by depressing the accelerator pedal, and a continuously variable transmission T.
A pulse signal for driving the pulse motor 24, which is a sleeve driving motor, to the speed-up side by performing a predetermined calculation on the basis of the rotation speed detection signal V of the output disk 2 of FIG. Is output.

Therefore, the rotational force of the pulse motor 24 is transmitted to the sleeve 13 via the gears 25 and 21 provided in the rotating mechanism 11, and the sleeve 13 is rotated in the speed increasing direction (direction indicated by arrow A in FIG. 6). . In this case, the coupling mechanism 31 between the sleeve 13 and the spool 14
Since there is play in, only the sleeve 13 rotates.

In this way, when the sleeve 13 rotates in the speed increasing direction, the spiral oil passage grooves 13e, 13f, 13g, 13h on the inner peripheral surface of the sleeve are changed to the spiral oil passage grooves 14a, 14b, 14c, 14c on the outer peripheral surface of the spool. It communicates with 14d respectively. In response to this, hydraulic oil from the hydraulic source is transferred to the hydraulic pipe 12e → pipe connection port 12a → annular oil passage groove on the outer peripheral surface of the sleeve.
13b → oil passage hole 13p, 13t → spiral oil passage groove 13 on the inner peripheral surface of the sleeve
f, 13h → spiral oil passage grooves 14b, 14d on the outer peripheral surface of the spool → oil passage hole
13o, 13s → annular oil passage groove 13a → pipe connection port 12c → hydraulic pipe 1
It is supplied to the hydraulic cylinders 9a and 9d via a path of 2g. At the same time, the hydraulic oil in the hydraulic cylinders 9b and 9c is transferred to the hydraulic piping 12
h → pipe connection port 12d → annular oil passage groove 13c → oil passage holes 13u, 13q →
Spiral oil passage grooves 14a, 14c on the outer peripheral surface of the spool → spiral oil passage grooves 13e, 13g on the inner peripheral surface of the sleeve → oil passage holes 13r, 13v → annular oil passage groove 13d → pipe connection port 12b → hydraulic pipe 12f Through the oil tank. Therefore, the hydraulic cylinders 9a and 9d are extended, the trunnion 5 rises and the trunnion 6 descends. That is, the center 5a of the trunnion 5 is displaced upward from the axes 1a and 2a of the input / output disk, and
The center 6a of the trunnion 6 is offset below the axes 1a and 2a of the input / output disk. Therefore, assuming that the input disk 1 is rotating counterclockwise in FIG. 1, the transmission rollers 3 and 4 start tilting toward the speed-increasing side about the pivot shaft O of the trunnions 5 and 6.

As the trunnion 6 descends, the spool 14 is elastically pressed by the compression coil spring 26 and descends. At the same time, with the tilting of the trunnion 6, the rotation of the trunnion 6 starts synchronously via the connecting means 35.

In this case, the lowering of the spool 14 is the same as the relative rotation of the spool 14 in the counterclockwise direction.
The communication area formed between the spiral oil passage grooves 14a to 14d on the outer peripheral surface and the spiral oil passage grooves 13e to 13h on the inner peripheral surface of the sleeve decreases. Eventually, the spiral oil passage grooves 14a to 14d of the spool face the lands 13k to 13n of the spiral oil passage groove of the sleeve, the communication area becomes zero, and the oil passage holes 13o to 13v of the sleeve 13 are closed. As a result, the extension of the hydraulic cylinders 9a, 9d is stopped, and the trunnion 6 stops descending at the position displaced downward from the neutral position (the trunnion 5 displaced above the neutral position). However, the transmission rollers 3 and 4 continue to tilt in the speed-up direction, and the spool 14 tracks the sleeve 13 rotated by the pulse motor 24 by the rotation of the trunnion 6 accompanying the tilt of the transmission roller 4. To rotate.

As a result, the spiral oil passage grooves 13e, 13f, 13g, 13 of the sleeve 13
h is each spiral oil passage groove 14d, 14a, 1 on the outer peripheral surface of the spool
Communicates with 4b and 14c. Then, in response to this, the hydraulic oil from the hydraulic source is transferred to the hydraulic pipe 12e → the pipe connection port 12a → the annular oil passage groove 13b on the sleeve outer peripheral surface → the oil passage holes 13p, 13t → the spiral oil passage on the inner peripheral surface of the sleeve. Grooves 13f, 13h → Helical oil passage grooves 14a, 14c on the outer circumferential surface of the spool → Oil passage holes 13q, 13u → Annular oil passage groove 13c → Pipe connection port 12d → Hydraulic pipe 9h via the passage of hydraulic pipe 12h
Supplied to 9c. At the same time, the hydraulic oil in the hydraulic cylinders 9a and 9d is transferred to the hydraulic pipe 12g → the pipe connection port 12c → the annular oil passage groove 13
a → oil passage hole 13o, 13s → spiral oil passage groove 14b on the outer peripheral surface of the spool,
14d → spiral oil passage groove 13e, 13g on the inner peripheral surface of the sleeve → oil passage hole 13
r, 13v → annular oil passage groove 13d → pipe connection port 12b → hydraulic pipe 12f
Is discharged to the oil tank via. Therefore, the hydraulic cylinders 9b and 9c are extended, the trunnion 5 descends, and the trunnion 6 begins to rise.

The ascending and tilting directions of the trunnion 6 are transmitted from the piston 9D of the hydraulic cylinder 9d to the spool 14 via the connecting means 32, and the spool 14 rotates the sleeve motor 24 to set the rotation angle of the sleeve 13. Completed when rotated by the same angle as. At this time, the spool 14 reaches the neutral position and the oil passages 13o to 13v are shut off. Since the trunnions 5 and 6 also return to the neutral position, the central axes 3a and 4a of the transmission rollers 3 and 4 intersect the axes 1a and 2a of the input / output disks 1 and 2 to increase the speed of the toroidal continuously variable transmission T. Shift to the side is completed.

Further, when the toroidal type continuously variable transmission T is in the speed-increasing shift position and the accelerator pedal is released and the brake pedal is depressed to stop the vehicle, this is detected by the control device C. A control signal for returning the toroidal type continuously variable transmission T to the maximum deceleration position is output.

In response to this, the pulse motor 19 rotates the sleeve 13 in the deceleration direction (counterclockwise direction). By this rotation, the spiral oil passage grooves 13e, 13f, 13g, 13h on the inner peripheral surface of the sleeve communicate with the spiral oil passage grooves 14d, 14a, 14b, 14c on the outer peripheral surface of the spool, respectively.
Then, as described above, the hydraulic oil from the hydraulic source causes the hydraulic pipe 12e → the pipe connection port 12a → the annular oil passage groove 13b on the outer peripheral surface of the sleeve → oil passage holes 13p, 13t → the spiral on the inner peripheral surface of the sleeve. Oil passage grooves 13f, 13h → spiral oil passage grooves 14a, 14c on the outer peripheral surface of the spool → oil passage holes 13q, 13u → annular oil passage groove 13c → pipe connection port 12d → hydraulic cylinder 9b via the passage of hydraulic pipe 12h And 9c. At the same time, the hydraulic oil in the hydraulic cylinders 9a and 9d is transferred to the hydraulic pipe 12g → the pipe connection port 12c → the annular oil passage groove 13a → the oil passage hole 13
o, 13s → spiral oil passage grooves 14b, 14d on the outer peripheral surface of the spool → spiral oil passage grooves 13e, 13g on the inner peripheral surface of the sleeve → oil passage holes 13r, 13v → annular oil passage groove 13d → pipe connection port 12d → It is discharged to the oil tank via the hydraulic pipe 12f. Therefore, the hydraulic cylinder 9b and
9c is extended, the trunnion 5 descends from the neutral position, the trunnion 6 rises from the neutral position, and the transmission rollers 3 and 4 tilt toward the deceleration side.

As a result, the spool 14 rotates counterclockwise so as to follow the sleeve 13, and the transmission rollers 3 and 4 return to the maximum deceleration position.

When the spool 14 moves in the sleeve 13 in the axial direction within the stroke of the piston 9D of the hydraulic cylinder 9d and makes relative rotational movement, the sleeve spiral oil passage grooves 13e-1
If the 3h and the spool spiral oil passage grooves 14a to 14d communicate with other grooves beyond a predetermined relationship, the trunnions 5 and 6 malfunction, but in this embodiment, the coupling mechanism 3
Since the allowable movement amount of the stopper pin 29 of 1 is regulated by the stopper groove 30, such malfunction is prevented.

Further, the axial movement and the rotational movement around the axis of the trunnion 6 are smoothly transmitted to the spool 14 through the connecting means 35 synchronously and smoothly, and the trunnion 6 and the spool 14 have a relative radial direction. The dynamic displacement is absorbed by the connecting means 35. Therefore, even if the eccentricity is caused by a machining error of the trunnion 6, the spool 14 or the like, or a runout or the like due to elastic deformation of the seal member of the piston rod 33 connecting them, the operation of the spool valve device will not be abnormal.

Further, even if the sleeve 13 is rotated by the sleeve drive motor 24, the trunnion 6 is not tilted following the rotation (for example, when the input / output disks 1 and 2 are not rotating, or the hydraulic system is not rotated). If the trunnion 6 tilts irrespective of the valve operation due to a failure), the disc spring 22 as an overload clutch provided in the rotating mechanism 11 absorbs the abnormal operation. Damage is prevented.

Further, since the sleeve 13, the spool 14, and the trunnion 6 are assembled by using the connecting means 35 and the compression coil spring 26, they can be easily attached to and detached from the valve housing 12.

Regarding the processing of the spiral oil passage grooves 13e to 13h and 14a to 14d, the spool 14 has a shape corresponding to the tooth root of a helical gear and can be easily hobbed, and the sleeve 13 is easily processed by a spiral broach. The lap amount of the spiral oil passage groove can be easily changed by cutting the groove of the spool 14 or by the diameter of the fitting portion between the sleeve 13 and the spool 14.

Next, a second embodiment of the present invention will be shown.

FIG. 8 is an enlarged view of the essential parts of this embodiment.
This is different from the first embodiment in that the rotation center O _T of the trunnion 6 is eccentric with respect to the rotation center O _S of the spool 14.

According to the second embodiment, when the toroidal continuously variable transmission T is on the deceleration side and on the speed increasing side, the spool 14 rotates with respect to the rotation angle (tilt angle) Δθ _T of the trunnion 6. The angle Δθ _S is different, and the sensitivity of the spool valve, that is, the shift sensitivity, changes. In the illustrated example, the deceleration side rotation angle Δθ _{SL of} the spool 14 is larger than the speed increase side rotation angle Δθ _SH for the same trunnion tilt angle Δθ _T. Therefore, the rotation angle of the spool 14 is substantially changed according to the gear ratio,
You can change the sensitivity of the spool valve
It is possible to enhance the shift sensitivity on the deceleration side and simultaneously secure the shift stability on the acceleration side.

In addition, in each of the above-described embodiments, the spool 14 which is the rotating and sliding cylinder body is in sliding contact with the inner peripheral surface of the sleeve 13 which is the rotating cylinder body, but the invention is not limited to this. The spool 14 may be in sliding contact with the outer peripheral surface of the sleeve 13. In that case, of course, the spiral oil passage groove is formed on the inner peripheral surface of the sleeve and the outer peripheral surface of the spool.

〔The invention's effect〕

As described above, according to the present invention, the rotating cylindrical body that is connected to the rotating mechanism and sets the tilt angle of the transmission roller,
The rotating cylindrical body is provided with a rotating and sliding cylinder body that is in sliding contact with the inner peripheral surface or the outer peripheral surface of the rotating cylinder body and that is connected to the trunnion. The toroidal type continuously variable transmission is achieved by switching the oil passage to the hydraulic cylinder, which is the trunnion drive mechanism, only by forming the groove in the same phase and driving the rotating cylinder to rotate in the specified direction by a specified angle. It is assumed that the machine is operated to change gears. Therefore, the conventional precess cam and cam follower are not required, the structure is simple and the number of parts is small, unnecessary working space is not required around the switching valve device, and the height of the spool valve device is reduced, and the entire valve device is reduced. An effect that the structure can be further reduced in size and weight can be obtained.

[Brief description of drawings]

FIG. 1 is a sectional view showing a first embodiment of a switching valve device according to the present invention, FIG. 2 is a sectional view showing a state where the switching valve device according to the present invention is attached to a toroidal type continuously variable transmission, and FIG. An exploded perspective view showing a part of the component shown in FIG.
FIG. 4 is an explanatory view of the connecting mechanism shown in FIG. 1, and FIG.
6 is an explanatory view of the connecting means shown in FIG. 6, FIG. 6 is a sectional view taken along the line VI-VI of FIG. 1, FIG. 7 is a sectional view taken along the line VII-VII of FIG. 1, and FIG. 8 is a view of the second embodiment of the present invention. FIG. 9 is an enlarged cross-sectional view of a portion, and FIG. 9 is an explanatory view showing the relationship between tilting of the transmission roller with respect to the input / output disk and acceleration / deceleration in the toroidal type continuously variable transmission. Is during acceleration. T: toroidal type continuously variable transmission, C: control device, 1: input disk, 2: output disk, 3,4: transmission roller, 5,6
...... Trunnion, 9a ~ 9d ...... Trunnion drive mechanism (hydraulic cylinder), 10 ...... Switching valve device, H ...... Valve housing, 11 ...
… Rotation mechanism, 12 …… Valve housing, 12a to 12d …… Piping connection port, 13 …… Rotation cylinder (sleeve) for setting, 13a to 13d ……
Toroidal groove, 13e ~ 13h ... sleeve spiral oil passage groove, 13o ~ 1
3v …… Oil passage hole, 14 …… Rotating and sliding cylinder (spool), 14a
～14D ...... spiral oil passage groove of the spool, 14E～14h ...... land, O _S pivot axis ...... spool, O _T ...... rotation center of the trunnion, 24 ...... sleeve drive motor, 21, 25 ... … Gear, 29 …… Stopper pin, 30 …… Stopper groove, 31 …… Coupling mechanism, 32 ……
Triangular groove, 34 ... Engaging pin, 35 ... Connecting means.

Claims (5)

[Claims] 1. A continuously variable transmission by adjusting the tilt angle of the transmission roller by controlling the axial movement of a trunnion supporting a transmission roller in contact with an input / output disk by supplying a pressure fluid to a trunnion drive mechanism. In a switching valve device of a toroidal type continuously variable transmission that performs the above, a setting rotating cylinder body that is connected to a rotating mechanism and sets a tilt angle of the transmission roller, and an inner peripheral surface or an outer periphery of the rotating cylinder body. A swivel / sliding cylinder body slidably contacting the surface and connected to the trunnion, and the setting swivel cylindrical body and the swivel / sliding cylinder each have a plurality of spirals on their sliding surfaces. -Shaped oil passage grooves are formed in the same phase, the supply of pressure fluid to the trunnion drive mechanism is interrupted when both spiral oil passage grooves are inconsistent, and the trunnion drive mechanism is connected when both spiral oil passage grooves communicate. It is characterized in that pressure fluid is supplied. Switching valve device of the toroidal type continuously variable transmission. 2. A switching valve device for a toroidal type continuously variable transmission according to claim 1, wherein the rotating shaft of the rotating / sliding cylinder is coaxial with the rotating center of the trunnion. 3. The toroidal type stepless device according to claim 1, wherein the rotation shaft of the rotation / sliding cylinder is arranged at a position eccentric with respect to the rotation center of the trunnion. Transmission switching valve device. 4. A rotary cylinder for setting and a rotary and sliding cylinder,
The toroidal type continuously variable transmission according to claim (1), wherein the toroidal type continuously variable transmission is connected so as to be capable of relative rotation within an allowable relative rotation angle via a connection mechanism composed of a recess and a projection loosely fitted therein. Switching valve device. 5. The connection between the trunnion and the rotating / sliding cylinder is
The toroidal type continuously variable transmission according to claim (1), which is performed by a connecting means including an engaging pin protrudingly provided on the trunnion shaft portion and a triangular groove formed at the end portion of the rotating / sliding cylinder. Switching valve device.