JPH0140367Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] This invention relates to a shift spool valve device for adjusting the shift operation of a toroidal continuously variable transmission, that is, the tilt angle of a power roller.

[Conventional technology]

As a conventional speed change control device for a continuously variable transmission, there is one disclosed in US Pat. No. 4,434,675, for example.

The housing is mounted oppositely on the input and output shafts to form a toroidal cavity between the housing and coaxial input and output shafts rotatably supported within the housing. an input/output disk; a motion transmission power roller disposed radially symmetrically within the toroidal cavity with respect to the axes of the input and output shafts; and a motion transmission power roller that transmits motion between the input and output disk and the power roller. means for pressing into engagement with each other for transmission; a support structure for each power roller movable in the direction of its pivot axis; and a support structure disposed in communication with each power roller support structure. at least one hydraulically actuated means coupled thereto for transmitting precess motion thereto, and at least one of said power roller support structures is mounted for integral axial and rotational movement therewith. A main control valve is disposed in connection with a cam surface of the cam disk, the control valve has a control member and a cam follower in contact with the cam surface, and the cam follower has a control member and a cam follower in contact with the cam surface. the cam follower has a predetermined position with respect to said cam face for each transmission ratio of the transmission and for supplying pressure fluid to said hydraulic actuating means, or when said cam follower is not in its predetermined position. The main control valve is characterized in that the main control valve is coupled to a source of pressurized fluid and to each of the hydraulic actuating means for respectively releasing pressure fluid from the actuating means. With this configuration, a mechanical feedback mechanism is formed by the precess cam connected to the power roller support structure and the main control valve having a cam follower that engages with the cam surface, thereby producing a toroidal continuously variable transmission. The gear ratio of the machine can be changed reliably with a simple configuration.

[Problem that the invention seeks to solve]

However, in the conventional continuously variable transmission described above, the cam follower that engages with the cam disk connected to the power roller support structure (trunnion) is configured to handle the rotation of the trunnion and the axial movement. communicate,
The valve housing was slidably disposed on a threaded support column, and the valve housing was configured to change speed by sliding in the axial direction.
Since the valve housing itself slides in the axial direction of the support column, the hydraulic piping connected to the valve housing needs to be flexible and follow the movement, which requires a large space to allow this movement. The dot was hot.

In addition, the spool of the main control valve is configured to directly engage the cam surface of the cam disk and move in accordance with the rotation and axial sliding of the cam disk. There was also the problem that the movement stroke became large, and the required stroke of the valve housing also had to be made large in order to prevent abnormal operation of the control valve.

That is, for example, if the transmission is at the maximum speed increase position and the trunnion is at one end of the vertical stroke and is stopped, the valve housing is moved from this state to the maximum deceleration position by the speed change operation, and the valve housing is started in that state. Required stroke of the spool to shift the power roller to the deceleration side
TS is expressed by the following equation (1), where S ₁ is the cam lift in the speed change range, S ₂ is the valve operating stroke to prevent abnormal valve operation, and S ₃ is the trunnion movement stroke.

TS = S ₁ + S ₂ + S ₃ ... (1) To give an example, the cam lift S ₁ is 6.5 mm, the valve operating stroke S ₂ is ±0.5 to 1 mm, and the trunnion stroke S ₃ is 2 mm on one side, so the spool The required stroke TS is 9.5mm, which requires a larger stroke than a normal spool valve.

In this way, as the required stroke TS increases, the length of the spool becomes longer and its weight increases, so in order to obtain stable operation, it is necessary to increase the pressing force of the spool against the cam disc.
Additionally, the need to increase the length of the valve housing increases its weight. As a result, the driving force required to drive the valve housing increases in order to perform a speed change operation, and the spool becomes heavier, resulting in decreased responsiveness and increased processing costs.

Therefore, this invention was made by focusing on the problems of the conventional example described above, and is a toroidal type stepless device that is small and lightweight including peripheral equipment, improves responsiveness, and can be constructed at low cost. An object of the present invention is to provide a spool valve device for changing speeds of a transmission.

[Means for solving problems]

In order to achieve the above object, this invention cooperates with a cam disk attached to the pivot of the trunnion to control the axial movement of the trunnion, thereby controlling the tilting angle of the power roller rolling in contact with the trunnion. In a gear shifting spool valve device for a toroidal type continuously variable transmission that adjusts the speed and continuously variable speed, a cylindrical sleeve is disposed inside the valve housing so as to be slidable in the axial direction of the valve housing. A cylindrical spool is disposed within the required minimum range of movement, and a cam follower having an engaging portion that engages with the cam disc and engages with the spool is slid within the spool. A first elastic body is movably disposed between the cam follower and the sleeve and biases the cam follower toward the cam disk, and the spool is disposed between the spool and the sleeve. a second biasing member toward the engaging portion of the cam follower;
It is characterized by interposing an elastic body.

[Effect]

This invention consists of a speed change spool valve consisting of a valve housing, a sleeve that can slide on the valve housing, and a spool that can slide inside the sleeve. The spool and the cam follower that engages with the cam surface of the cam disc are separated from each other, and the spool and the cam follower that engage with the cam surface of the cam disc are separated from each other. The first and second elastic bodies reduce the stroke of the spool due to rotation and axial movement of the cam disk, thereby shortening the lengths of the spool, sleeve and valve housing. At the same time, by reducing its weight, the driving force of the sleeve during gear shifting is reduced and its responsiveness is improved.

〔Example〕

1 to 5 are diagrams showing an embodiment of this invention.

First, the configuration of a toroidal continuously variable transmission to which this invention can be applied will be explained with reference to FIG. 2. In the figure, T is a toroidal continuously variable transmission as a continuously variable transmission, and C is a control device.

The toroidal continuously variable transmission T has an input disk 2 and an output disk 3 coaxially opposed to each other and pivotally mounted in a housing 1. The input disk 2 and the output disk 3 have substantially the same shape, are arranged symmetrically, and are formed into toroidal surfaces such that their opposing surfaces cooperate to form a substantially semicircular shape when viewed in axial cross section. A pair of power rollers 4 and 5 are rotatably disposed in a toroidal cavity formed by the toroidal surfaces of the input disk 2 and output disk 3, and are in rolling contact with both the disks 2 and 3. . In this case, the power rollers 4 and 5 are
It is rotatably pivotally connected to the trunnions 6 and 7 and is supported so as to be tiltable about a pivot axis O that is the center of the toroidal surfaces of the input disk 2 and output disk 3.

Lubricating oil with high viscous frictional resistance is supplied to the contact surfaces between the input disk 2 and output disk 3 and the power rollers 4 and 5, and the rotational force input to the input disk 2 is transferred to the lubricating oil film and the power rollers. 4 and 5 to the output disk 3, and the change in the transmission ratio, that is, the gear ratio, moves the trunnions 6 and 7 a minute distance in the direction of the pivot axis O-O, thereby changing the tilt angle θ of the power rollers 4 and 5. This is done by changing. In this case, the movement of trunnions 6 and 7 is as follows:
Hydraulic cylinders 9a to 9d provided at both ends of the trunnions 6 and 7, and these hydraulic cylinders 9a to 9d.
Shift spool valve device 1 for controlling hydraulic pressure supply to
0 and a precess cam 11 as a cam disc formed integrally with the trunnion 6.

As shown in an enlarged view in FIG. 1, the speed change spool valve device 10 includes a cylindrical sleeve 14 that is disposed within a center opening 13a of a cylindrical valve housing 13 so as to be slidable only in the axial direction. A cylindrical spool 15 is disposed within the center opening 14a of the spool 14, and a cam follower 16 is slidably disposed within the center opening 15a of the spool 15.

A cylindrical bearing housing 17 is screwed onto the upper end of the valve housing 13, and four oil holes 13b to 13e are bored in the middle part, and the sleeve 14 is prevented from rotating in the circumferential direction. A female thread 13f is formed at the lower end into which a locking screw 19 that engages with an oil passage groove 14c' serving as a long groove for locking the sleeve 14, which will be described later, is screwed in order to prevent the rotation of the sleeve 14.
8 is formed in a protruding manner, and this attachment member 18 is attached to the housing 1 of the toroidal continuously variable transmission T. The oil passage hole 13b is connected to the hydraulic pipe 1.
3g to an external hydraulic source, oil passage hole 13c to oil tank through hydraulic piping 13h, oil passage hole 13d
is connected to the hydraulic cylinders 9b, 9c of the toroidal continuously variable transmission T via the distribution pipe 13i through the oil passage hole 13e.
are connected to hydraulic cylinders 9a and 9d of the toroidal continuously variable transmission T via distribution pipes 13j, respectively.

The sleeve 14 has oil passage holes 13b to 13e of the valve housing 13 on its outer peripheral surface and a female thread 13.
Oil passage long grooves 14b to 14e and 1 extending in the axial direction at positions opposite to f and axially symmetrical positions, respectively.
4b' to 14e' are bored, and two annular grooves 14g and 14h are bored in the inner peripheral surface at a predetermined interval in the axial direction, and the long grooves 14b and 14b' and the annular groove 1
As shown in FIG. 4, oil passage holes 14i, 14i' are provided between the inner walls of the central part between 4g and 14h, and the long grooves 14c, 1
4c' and the outer inner walls of the annular grooves 14g and 14h, as shown in FIG. As shown, oil holes 14l, 14
As shown in FIG. 3, oil passage holes 14m and 14m' are bored between the long grooves 14e and 14e' and the annular groove 14h, respectively.

The spool 15 has a position facing the annular grooves 14g and 14h of the sleeve 14 and an oil passage hole 14.
Lands 15b and 1 are placed at the outer positions of j and 14k, respectively.
5c, 15d, and 15e are formed. Therefore, the oil passage long grooves 14b to 14e and the symmetrically located long grooves 14b' to 14e' correspond to the annular grooves 15f and 15h of the spool 15, the annular grooves 14g and 14h of the sleeve 14, and the oil passage holes 14i to 14m, respectively. ，
They communicate with each other through 14i' to 14m'.

Further, a rolling bearing 17a is fitted into the inner circumferential surface of the bearing housing 17, and a stopper 1 for restricting upward movement of the sleeve 14 is fitted inside the bearing housing 17.
7b is fitted inside.

A nut 20 is fitted into the inner ring of the rolling bearing 17a, and a control gear 23 that meshes with a gear 22 connected to a rotating shaft of a pulse motor 21 is fixed to the upper surface of the nut 20, for example.

A screw shaft 24 is screwed into the nut 20,
The lower end of the screw shaft 24 is integrally screwed onto the upper end of the sleeve 14, and the upper end of the cam follower 16 is slidably supported within a center hole 24a bored inside the screw shaft 24. A cam follower pressing spring 25 as a first elastic body is interposed between the step portion 24b of the center hole 24a and the flange 16a of the cam follower 16.

A spool stopper 26 is screwed onto the inner peripheral surface of the lower end of the sleeve 14, and the upper surface of the spool stopper 26 and the spool 1
6, connect the upper end of the spool 15 to the cam follower 1
A spring 27 is interposed as a second elastic body which is brought into contact with the lower surface of the flange 16a as the engaging portion of the flange 16a. In this case, the cam follower pressing spring 25 and the spring 27 are selected such that the former is stronger than the latter.

Here, the movement of the spool 14 in the axial direction is restricted by the lower end surface of the screw shaft 24 and the upper end surface of the spool stopper 26, and the lower end of the cam follower 16 engages with the cam surface of the precess cam 11, and the spool 14 With the valve in the neutral position, its top surface and the screw shaft 2
The gap length t ₁ between the bottom surface of the spool stopper 26 and the gap length _{t 2} between the bottom surface and the top surface of the spool stopper ₂₆ are selected to be approximately equal. With the upper end in contact with the lower surface of the screw shaft 24 or the lower end of the spool with the upper surface of the spool stopper 26, the hydraulic piping 13g from the hydraulic power source, the oil passage hole 13b of the valve housing 13, and the oil path of the sleeve 14 are connected. Long grooves 14b, 14b', oil passages 14i, 14
i' The annular groove 1 of the sleeve 14 is passed through the annular groove 15f between the lands 15b and 15c of the spool 15.
The length is selected to be sufficient to saturate the flow rate characteristics of the hydraulic oil supplied for 4g or 14h.

The trunnion 6, precess cam 11, cam follower 16, and spool 15 constitute mechanical feedback means.

The control device C includes a vehicle speed detector 3 that detects the rotational speed of the output disk 3 as shift control information serving as a reference for selecting a gear ratio and outputs a detection signal corresponding to the vehicle speed.
0, various detection signals are supplied from the throttle opening degree detector 31, the operation mode selection switch 32, and the shift position detector 33, and based on these, predetermined arithmetic processing is executed and pulses are generated to obtain the desired gear ratio. The motor 21 is controlled.

Next, the effect will be explained. Assuming that the vehicle is now in a stopped state, in this state, the power rollers 4 and 5 are at the maximum deceleration position where they roll into contact with the small diameter portion of the input disk 2 and the large diameter portion of the output disk 3, respectively, in preparation for starting the vehicle. is controlled by.

In this state, as shown in FIG. 1, the cam follower 16 is engaged with the highest cam surface 11b of the precess cam 11, and the land 15b of the spool 15
The annular groove 15f between the annular grooves 14g and 15c of the sleeve 14 is closed by the inner wall between the annular grooves 14g and 14h of the sleeve 14.
h is closed by lands 15b and 15c of spool 15. Therefore, the hydraulic oil from the hydraulic source is not supplied to the distribution pipes 13i and 13j, and the trunnions 6 and 7 are held at neutral positions.

When the vehicle is started from this stopped state by, for example, selecting the shift lever in the drive range, depressing the accelerator pedal, and leaving the clutch in the half-clutch state, the control device C detects the shift position detection signal S at that time. The operation of the sleeve 14 is performed by performing a predetermined calculation based on the driving mode selection signal P, the throttle opening detection signal U due to depression of the accelerator pedal, and the rotation speed detection signal V of the output disk 3 of the continuously variable transmission T. The amount is calculated, and a pulse signal for driving the pulse motor 21 to the speed increasing side is output in accordance with the amount.

Therefore, since the rotational force of the pulse motor 21 is transmitted to the nut 20 via the gears 22 and 23, the screw shaft 24 moves downward, and the sleeve 14 descends accordingly.

In this state, assuming that the power rollers 4 and 5 have not yet started tilting, the cam follower 16 will be
Maintain the raised position shown in Figure 1, but spool 1
5 comes into contact with the lower end surface of the screw shaft 24 for the first time when the sleeve 14 has descended by a predetermined distance t ₁ , so that it then descends as the sleeve 14 descends.

In this way, when the upper end of the spool 15 moves in the direction of engaging the lower end of the screw shaft 24 due to the lowering of the sleeve 14, the annular groove 15f of the spool 15 and the annular groove 14g of the sleeve 14 communicate with each other. The hydraulic oil from the hydraulic source is supplied to the distribution pipe 13i, and the annular groove 15h and the annular groove 14
The hydraulic oil in the distribution pipe 13j is returned to the hydraulic tank via the hydraulic pipe 13h, and the hydraulic cylinders 9b and 9c of the toroidal continuously variable transmission T are extended, and the hydraulic cylinders 9a and 9d are contracted. Accordingly, the trunnion 6 is lowered and the trunnion 7 is raised. Therefore, the precess cam 11 is lowered and the cam follower 16 is also lowered,
When the amount of descent of the sleeve 14 is greater than the amount of movement of the trunnions 6 and 7, the flange 16a of the cam follower 16 is separated from the upper end surface of the spool 15, and the spool 15 maintains a position displaced upward from the neutral position with respect to the sleeve 14. . In this state, if the input disk 2 starts rotating counterclockwise as shown by the chain line in FIG. rotate in the direction.

Due to this rotation of the precess cam 11, the cam follower 16 is gradually lowered along the cam surfaces 11b to 11a by the force of the cam follower pressing spring 25. In this case, when the cam follower 16 initially descends, the spool 1
Since there is a gap between the cam follower 16 and the screw shaft 24 by subtracting the gap length t ₁ , the spool 1 is
5 is not lowered and its relative position with respect to the sleeve 14 does not change. After that, the flange 16 of the cam follower 16
When a comes into contact with the spool 15, the spool 15 starts to descend for the first time, and the power rollers 4 and 5 move to the maximum deceleration position (cam follower 16
When the lower end reaches the position immediately before engaging the low cam surface 11a of the precess cam 11, the lands 15b, 15c of the spool 15 close the annular grooves 14g, 14h of the sleeve 14, and the hydraulic cylinders 9b,
Cut off the pressure oil supply to 9c.

However, in this state, the trunnion 6,
7 is at a position deviated from the neutral position, the power rollers 4 and 5 continue to tilt further, and the cam follower 16 further descends. Therefore, the annular groove 15f of the spool 15 and the annular groove 14h of the sleeve 14 are brought into communication, the hydraulic cylinders 9a and 9d are expanded, and the annular groove 15g and the annular groove 14g are communicated with each other. Since the hydraulic cylinders 9b and 9c contract and the trunnions 6 and 7 rise accordingly, the cam follower 16 also rises and the spool 15
The lands 15b, 15c close the annular grooves 14g, 14h of the sleeve 14, and by repeating this, the trunnions 6, 7 return to the neutral position, and the shift to the maximum speed increase position shown in FIG. 5 is completed. in fact,
Annular groove 14g, 14h, 15f, 15g, 15
By providing underlaps that slightly communicate with each other at the neutral position, this repetition is almost eliminated, and the neutral position is achieved in one operation.

Furthermore, when the power rollers 4 and 5 are at the maximum speed increase position shown in FIG. 5, when moving the power rollers 4 and 5 to the maximum deceleration position to bring the vehicle to a halt, the control device C is used. A control signal is generated to rotate the pulse motor 21 in the opposite direction, thereby raising the screw shaft 24 and the sleeve 14.

When the sleeve 14 rises in this way, the cam follower 16 is urged toward the precess cam 11 side by the cam follower pressing spring 25, so that the lower end surface of the spool 15 moves toward the spool stopper 2.
6, the spool 15 maintains the position shown in FIG.
It is spaced upward from the cam surface 11a of No. 1. Therefore, as the sleeve 14 rises, the annular groove 15f of the spool 15 and the annular groove 14h of the sleeve 14
and the annular groove 15g of the spool 15 and the sleeve 1
The annular grooves 14g of No. 4 are in communication with each other, and the hydraulic pipe 13g and the distribution pipe 13j are in communication with each other, and the hydraulic pipe 13h and the distribution pipe 13i are in communication with each other, so that hydraulic oil is supplied to the hydraulic cylinders 9a and 9d, and the hydraulic oil is supplied to the hydraulic cylinders 9b and 9d. The hydraulic oil 9c is discharged, the trunnion 6 rises, and the trunnion 7 rises.
As the trunnions 6, 7 move up and down, the power rollers 4, 5 start tilting in the deceleration side, that is, in the counterclockwise direction when viewed from the plane. This power roller 4, 5
As the trunnions 6 and 7 also rotate as the
The precess cam 11 rotates counterclockwise. Then, when the power rollers 4 and 5 reach the vicinity of the maximum deceleration position, the cam surface of the precess cam 11 comes into engagement with the cam follower 16, and the cam follower 16 rises against the cam follower pressing spring 25, and in response, the spool 15 is spring 27
rise by the force of When the power rollers 4 and 5 rotate to a predetermined tilt angle θ position, the spool 15 rotates the distribution pipe 13j and the hydraulic pipe 13g.
Then, the distribution pipe 13i and the hydraulic pipe 13h are respectively cut off, and the movement of the trunnions 6 and 7 is stopped. However, since the moving positions of the trunnions 6 and 7 are shifted from the neutral position, the power rollers 4 and 5 are further tilted in the direction of deceleration. As it further rises beyond the neutral position, the hydraulic piping 13g and the distribution piping 13i and the hydraulic piping 13j and the distribution piping 13j communicate with each other, and hydraulic oil is supplied to the hydraulic cylinders 9b and 9c, and the hydraulic oil of the hydraulic cylinders 9a and 9d is connected. is discharged, and the trunnions 6 and 7 move toward the neutral position in opposite directions. And trunnion 6,
7 returns to the predetermined neutral position, the tilting of the power rollers 4 and 5 is stopped, and the spool 1 at this time
At position 5, the hydraulic piping 13g and the distribution piping 13i and the hydraulic piping 13h and the distribution piping 13j are respectively cut off, and the shift to the maximum deceleration position shown in FIG. 1 is completed. Here too, in reality, the spool 15 almost exceeds the neutral position due to the underlap of the annular groove.
The gear shift is almost completed in one operation without increasing.

During the above speed change operation, the oil passage long groove 14b~
14e and a long oil passage groove 14 located symmetrically to these.
b' to 14e' are in communication with each other as described above, so the same hydraulic pressure always acts on the grooves at symmetrical positions, and the radial hydraulic pressure applied between the sleeve 14 and the housing 13 is balanced. , smooth operation between the sleeve 14 and the housing 13 is maintained.

As described above, the amount of relative displacement of the spool 15 with respect to the sleeve 14 when performing a speed change operation of the toroidal type continuously variable transmission T is, at most, between the upper end of the spool 15 in the neutral state shown in FIG. 1 or FIG. The gap length t ₁ between the lower end surface of the shaft 24 and the gap length t 2 between the lower end surface of the spool 15 and the upper surface of the spool stopper ₂₆
, that is, the minimum displacement amount sufficient to saturate the fluid characteristics of the working fluid supplied to the hydraulic cylinders 9a to 9d through the spool 15.
It becomes possible to reduce the amount of displacement of the spool 15, and accordingly, the length of the spool 15 can be shortened and its weight can also be reduced, making the entire configuration including the spool smaller and lighter. In addition, since the movable part can be made smaller and lighter, responsiveness can be improved and the driving force required for control can be reduced.

Moreover, if one of the long grooves for the oil passage of the sleeve 14 is also used as a long groove for preventing rotation, there is an advantage that there is no need to separately provide a groove for preventing rotation.

Furthermore, as in the above embodiment, by making the long groove 14f of the sleeve 14 have a different shape from the other long grooves 15b to 15e, it is possible to prevent a phase shift due to incorrect attachment of the sleeve 14 and spool 15 during assembly. There are advantages that can be achieved. In this case, when one of the oil passage long grooves also serves as the anti-rotation long groove, the oil passage long groove located symmetrically with the anti-rotation long groove is used to balance the radial force between the sleeve 14 and the housing 13. It is desirable that they have the same shape.

In addition, in the above embodiment, the cam follower 1
Although the case has been described in which the cam follower pressing spring 25 is applied as the elastic body that biases the cam follower 6 toward the precess cam 11 side, the present invention is not limited to this, and any elastic body such as a rubber-like elastic body can be applied. Of course.

Further, in the above embodiment, the sleeve 14
The explanation has been made of a case in which the drive mechanism is configured to move up and down by a drive mechanism that converts rotational motion to linear motion, which is composed of gears, nuts, and screw shafts, but the structure is not limited to this. ,
Various drive mechanisms such as a rack and pinion can be used, as long as they can slide the sleeve 15 in the vertical direction based on a speed change control signal from a speed change control device.

[Effect of idea]

As explained above, according to this invention, a sleeve that slides only in the axial direction is disposed within the valve housing, a spool is slidably disposed within this sleeve, and a cam disk is disposed within this spool. Since the gear shifting spool valve device is configured by disposing the engaging cam follower so as to be slidable and connecting the cam follower to the spool through the first elastic body and the second elastic body, the spool As a result of separating the cam follower from the cam follower, it is possible to minimize the amount of relative displacement of the spool with respect to the sleeve while maintaining a large stroke of the cam disk, and it is also possible to shorten the overall length of the spool. Accordingly, the structure of the entire valve device can be made smaller and lighter, reducing the driving force required for its control, and the spool itself can be made smaller and lighter, resulting in improved responsiveness and a lighter weight. Since the housing does not operate, rigid hydraulic piping can be used, and an unnecessary operating space around the speed change spool valve device is not required.

[Brief explanation of the drawing]

Fig. 1 is a sectional view showing an embodiment of this invention in the maximum deceleration state, Fig. 2 is a partial cross-sectional view showing an example of a toroidal continuously variable transmission to which this invention can be applied, and Fig. 3 Figures and Figures 4 are respectively - of Figure 1.
FIG. 5 is a cross-sectional view of the vehicle in the maximum speed increase state, which serves to explain the operation of this invention. T...Toroidal continuously variable transmission, C...Control device, 1...Housing, 2...Input disk, 3
...Output disk, 4,5...Power roller,
6, 7... Trunnion, 10... Speed change spool valve device, 11... Precess cam, 13... Valve housing, 14... Sleeve, 14b to 14e...
Long groove for oil passage, 14c'...Long groove for rotation prevention, 15...
...Spool, 15b-15e...Land, 16...
...Cam follower, 17...Bearing housing, 20
... Nut, 21 ... Pulse motor, 22, 23
... Gear, 24 ... Spiral shaft, 25 ... Return spring, 26 ... Spool stopper, 27 ... Spring.

Claims (1)

[Claims for Utility Model Registration] (1) By controlling the axial movement of the trunnion in cooperation with a cam disc attached to the pivot of the trunnion, the tilting angle of the power roller rolling in contact with the trunnion can be adjusted. In a speed change spool valve device for a toroidal continuously variable transmission that adjusts and continuously changes speed, a cylindrical sleeve is disposed within the valve housing so as to be slidable in the axial direction of the valve housing, and the sleeve can be slid within the sleeve. A cylindrical spool is disposed within a required minimum movement range, and a cam follower having an engaging portion that engages with the cam disc and engages with the spool is slid within the spool. A first elastic body is interposed between the cam follower and the sleeve to urge the cam follower toward the cam disk, and the spool is disposed between the spool and the sleeve. A speed change spool valve device for a toroidal continuously variable transmission, characterized in that a second elastic body is interposed to bias the engagement portion of the cam follower. (2) For shifting of the toroidal continuously variable transmission described in claim (1) of the utility model registration claim, in which a long groove for an oil passage and a long groove for preventing rotation are bored in the outer circumferential surface of the sleeve that extends in the axial direction. Spool valve device. (3) Utility model registration claim No. (2) in which the oil passage long groove and the anti-rotation long groove are formed in different shapes.
A spool valve device for shifting a toroidal continuously variable transmission as described in 2.