JPH11264450A - Transmission control device for toroidal type continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent a decrease in torque transmission capacity by preventing the backlash of feedback links an process cams. SOLUTION: This transmission control device for a toroidal type continuously variable transmission is provided with precess cams 2, 2R formed on one of a plurality of trunnion shafts 5A; a feedback link 54 for transmitting the around- the-shaft or axial displacement of the trunnion shaft 5A in accordance with the precess cam 2 to a transmission control valve 41 for advancement; and a feedback link 154 for transmitting the around-the-shaft or axial displacement of the trunnion shaft 5A in accordance with the precess cam 2R to a transmission control valve for retreat. A helical torsion coil spring 3 energizes the precess cams 2, 2R to press the precess cams 2, 2R against the feedback links 54, 154 by facing the feedback links 54, 154 in the reverse directions.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a shift control device for a toroidal type continuously variable transmission used in a vehicle or the like.

[0002]

2. Description of the Related Art In a toroidal-type continuously variable transmission employed in a vehicle such as an automobile, a shift control is performed by hydraulic pressure. JP-A-6-257661, JP-A-7-198015 and the like are known.

[0005] As shown in FIGS. 5 to 7, a trunnion 5 (roller support member) is connected via a pivot shaft 6.
A hydraulic cylinder 30 (hydraulic actuator) that controls the tilt angle of the power roller 1 that is supported by a shaft is provided in parallel with a forward shift control valve 41 and a reverse shift control valve 141.
At the end of the trunnion shaft 5A, which is connected to the piston 31 of the hydraulic cylinder 30 on the way, the displacement of the trunnion 5 around the axis = power roller 1
, That is, the actual gear ratio is changed by the shift control valve 41,
Precess cam 2 which feeds back to 141 respectively,
2R is formed.

[0004] The precess cam 2 for forward movement and the precess cam 2R for backward movement have guide grooves 2 formed respectively.
L-shaped feedback links 54, 15
4 is engaged, the forward feedback link 54 drives the valve body of the shift control valve 41 from the engagement portion 90 via the shift link 9, while the reverse feedback link 15
4 is a valve body 1 of the shift control valve 141 via the engagement portion 190.
43 is driven.

An engaging portion 90 formed at one end of the speed change link 9
The ball 58 provided at the end of the feedback link 54 is engaged with the engaging portion 91 formed at the other end.
Sliders 52 driven by a step motor 50 via a feed screw mechanism 51 are engaged with each other, and the valve element 43 connected in the middle of the speed change link 9 is driven in the X-axis direction in the figure, so that the trunnion 5 is pivoted. , And the gear ratio is continuously changed by the tilting movement of the power roller 1.

An engaging member 55a provided at an end of an arm 55 of an L-shaped feedback link 54 is engaged with the guide groove 21 formed in the precess cam 2 to connect the arms 55 and 56. The cylindrical portion 57 is pivotally supported by the swing shaft 4 along the Y axis in the figure, and displaces the ball 58 provided at the end of the arm 56 in the X axis direction in the figure.

The ball 58 is provided with a shift control valve 41 for sucking and discharging pressure oil to a hydraulic actuator for driving a trunnion.
And the stepping motor 50 are connected at an inner periphery of a concave engaging portion 90 formed at one end of the speed change link 9.

The feedback link 154 for reverse travel is similarly constructed, and has a guide groove 1 formed in the precess cam 2R.
21 has an L-shaped feedback link 1
The engagement member 155 a provided at the end of the arm 155 is engaged, and the cylindrical portion 157 connecting the arms 155 and 156 is pivotally supported by the swing shaft 4 and is connected to the valve body 143. Ball 15 provided at the end of arm 156 on the inner circumference of 190
8 engages to displace the valve body 143 in the X-axis direction in the figure.

At an engaging portion 91 at the other end of the speed change link 9, a pin 52a provided on a slider 52 driven in the X-axis direction in the drawing by a step motor 50 as an actuator via a feed screw mechanism 51 has an inner periphery. Engage.

Further, at a predetermined position in the middle of the transmission link 9, the transmission control valve 4 is connected via a pin 53a of the connecting member 53.
1 is connected to a rod portion of a valve body 43 that slides on the inner circumference of the hydraulic cylinder 3. The valve body 43 is displaced in accordance with the relative displacement between the step motor 50 and the feedback link 54.
By controlling the differential pressure applied to the zero piston 31, the tilting movement can be controlled while supporting the axial input torque applied to the trunnion 5 from the power roller 1.

As shown in FIG. 6A, a spring 70 is provided between the valve body 11 and a connecting member 53 connecting the valve body 43 of the forward speed change control valve 41 and the speed change link 9. The transmission link 9 is interposed, and a predetermined urging force F
Energize with sf. Therefore, the feedback link 54 connected to the speed change link 9 via the engaging portion 90 urges the end engaging member 55a downward in the drawing with the force of F1 to form the guide groove 21 of the precess cam 2. The engaging portion 55a is pressed against the inclined surface 21A, and the backlash between each part of the transmission link 9 and the feedback link 54 is reduced, so that the feedback link 54 can always follow the precess cam 2.

As shown in FIG. 6B, a spring 71 is provided between the valve body 11 and an engaging portion 190 connecting the valve body 143 of the reverse speed change control valve 141 and the feedback link 154. Is interposed, and the engaging portion 190 is provided.
At a predetermined urging force Fsr. Accordingly, the feedback link 154 connected to the engaging portion 190 urges the end engaging member 155a downward in the drawing with the force of F2,
The engaging portion 155a is pressed against the lower inclined surface 121A in the figure formed in the guide groove 121 of the precess cam 2R, and the valve body 14
The feedback link 154 can always follow the precess cam 2R by reducing the play between the feedback link 3 and the feedback link 54.

The speed change control during forward movement is performed by a step motor 50.
When the slider 52 is driven to expand and contract according to a target gear ratio from a controller (not shown),
The valve element 43 moves according to the displacement on the first side, and the shift control valve 41
Then, the trunnion 5 is displaced in the axial direction by sucking and discharging the pressurized oil into the oil chamber of the hydraulic cylinder 30, and the power roller 1 tilts.

This tilting motion is transmitted to the engaging portion 90 of the speed change link 9 via the feedback link 54 slidably in contact with the precess cam 2 provided on the trunnion 5, and if the desired target speed ratio matches the actual speed ratio. Then, the valve body 43 returns to the neutral position where the suction and discharge of the pressure oil is stopped again. In this manner, the speed change link 9 performs the above operation every time the speed change is performed and swings to perform the speed change control.

On the other hand, the shift control at the time of reverse travel is performed by switching the intake and discharge of hydraulic oil to and from the hydraulic cylinder 30 from the forward shift control valve 41 to the reverse shift control valve 141 by a switching valve (not shown). For example, by biasing the valve body 143 with a predetermined force, the pressure oil is sucked and discharged according to a predetermined target gear ratio for reverse movement, and the feedback link 154 slidably in contact with the precess cam 2R is actually applied to the valve body 143. When the target gear ratio and the actual gear ratio match,
The valve body 143 returns to the neutral position where the suction and discharge of the pressure oil is stopped again.

[0016]

In the toroidal-type continuously variable transmission, torque is transmitted by a plurality of power rollers, and each trunnion 5 has a structure shown in FIG. As described above, the thrust of the piston 31 according to the differential pressure of the hydraulic cylinder 30 is equally applied upward in the drawing, and the input torque transmitted by each power roller 1 is uniformly supported.

However, in the above-mentioned conventional example, the urging force Fs of the spring 70 for reducing the backlash of each part of the speed change link 9 and the feedback link 54 and the precess cam 2 is used.
f is an urging force F1 corresponding to the lever ratio between the transmission link 9 and the feedback link 54.
The urging force Fsr of the spring 71 that urges downward in FIG. 6A and reduces the play of the reverse feedback link 154 and the precess cam 2R is an urging force F2 corresponding to the lever ratio of the feedback link 154, and is a trunnion. In order to urge the shaft 5A downward in FIGS. 5 and 6 (A), a thrust Fz = F1 + F2 is applied to the trunnion shaft 5A provided with the precess cams 2 and 2R toward the lower side of the Z axis in the figure. Become.

For this reason, only the trunnion shaft 5A provided with the precess cams 2 and 2R has the axial thrust Fz by the springs 70 and 71 in addition to the thrust of the hydraulic cylinder 30.
= F1 + F2, the thrust of the trunnion 5 supporting the power roller 1 is shifted from that of the trunnion having no precess cam, and the torque transmission of each power roller 1 varies according to the shift. As a result, as compared with the case where the piston thrust applied to each trunnion 5 is uniform, the limit of slippage of the power roller 1 sandwiched between the input and output disks is reduced, that is, the torque transmission capacity of the continuously variable transmission. However, there was a problem that was reduced.

The present invention has been made in view of the above problems, and has as its object to prevent a torque transmission capacity from lowering while preventing a backlash between a feedback link and a precess cam.

[0020]

According to a first aspect of the present invention, a plurality of power rollers sandwiched between an input / output disk are supported, and a plurality of power rollers are rotatable around a predetermined axis and axially displaceable. A roller support member, a forward and reverse shift control valve for controlling hydraulic pressure to a hydraulic actuator for driving the roller support member in the axial direction, and one of the plurality of roller support members. A cam, first feedback means for transmitting an axial or axial displacement of the roller support member to the forward speed control valve in response to the cam, and an axial or axial direction of the roller support member in response to the cam; A shift control device for a toroidal-type continuously variable transmission, comprising: a second feedback means for transmitting a displacement to the reverse shift control valve. Feedback means toward the opposite direction to each other comprises biasing means for biasing to press the cam.

According to a second aspect of the present invention, in the first aspect, the urging means includes an absolute value of a force by which the first feedback means and the second feedback means press the cam in mutually opposite directions. Set the values equal.

In a third aspect based on the first aspect, the biasing means includes a first biasing means for biasing the first feedback means and the second feedback means in mutually opposite directions.
Of elastic members.

In a fourth aspect based on the third aspect, the first feedback means contacts the cam at one end and the first feedback means is connected to the forward shift control valve at the other end.
The second feedback means includes a second link that abuts the cam at one end and connects to the reverse speed change control valve at the other end, and coaxially connects the first and second links. And the first elastic member is disposed between the first link and the second link.
Torsional moments in mutually opposite directions are applied to the first link and the second link.

In a fifth aspect based on the first aspect, the biasing means includes a second elastic member for biasing the first feedback means, and a third elastic member for biasing the second feedback means. And an elastic member.

[0025]

Therefore, the first aspect of the present invention is to provide a toroidal type continuously variable transmission having a plurality of roller supporting members, in which axial thrust from a hydraulic actuator is applied to each roller supporting member, and the cam is further moved. In the roller support member provided, the play between the first feedback means, the second feedback means, and the cam is reduced, and the feedback means follows the displacement of the roller support member. In addition, the force from this biasing means
Since the first feedback means and the second feedback means act to press the cams in mutually opposite directions,
The axial thrust for reducing the backlash applied to the roller supporting member with the cam is offset and reduced, and the difference between the axial thrust of the roller supporting member without the cam and the axial thrust can be reduced. It is possible to suppress a decrease in the limit at which the held power roller slides, and to suppress a decrease in the torque transmission capacity of the toroidal-type continuously variable transmission.

According to a second aspect of the present invention, the first feedback means and the second feedback means have the same absolute value of the force pressing the cam in opposite directions, so that the play applied to the roller supporting member provided with the cam is reduced. Axial thrust can be offset to reduce the gap, eliminating the difference between the axial thrust of the roller support member without cam and preventing the lower limit of the slippage of the power roller sandwiched between the input and output disks. do it,
It is possible to prevent a reduction in the torque transmission capacity of the toroidal-type continuously variable transmission.

In the third invention, the first feedback means and the second feedback means are urged in opposite directions by the first elastic member. Therefore, the urging means is constituted by a single elastic member. It is possible to suppress a decrease in the torque transmission capacity of the toroidal-type continuously variable transmission while reducing the number of parts.

According to a fourth aspect of the present invention, the first elastic member is connected to the first link and the second link on the same axis by a torsional moment.
In order to urge the links in mutually opposite directions, the urging means is constituted by a single elastic member to reduce the number of parts, and the first and second links are opposite to the cam when they are in contact with the cam. Since the force from the urging means is not applied to the side end, for example, when the forward speed change control valve and the driving means are connected to the end of the first link, the driving The required driving force can be reduced by the force urging the first link to the cam, and the miniaturization of the device can be promoted.

According to a fifth aspect of the present invention, the second and third biasing means for biasing the first and second feedback means in mutually opposite directions.
Since the elastic members are provided respectively, the axial thrust of the roller supporting member provided with the cam can be reduced while the first and second feedback means follow the cam simply by changing the arrangement of the elastic member easily from the conventional example. By approaching the thrust of the other roller supporting member in the axial direction, it is possible to suppress a decrease in the torque transmission capacity of the toroidal type continuously variable transmission.

[0030]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the accompanying drawings.

FIGS. 1 and 2 show an example in which the present invention is applied to a transmission control device for a toroidal-type continuously variable transmission similar to that of the above-mentioned conventional example. And a duplicate description is omitted.

In FIGS. 1 and 2, similarly to the conventional example, the forward shift control valve 41 and the reverse shift control valve 141 are arranged in parallel so as to sandwich the trunnion shaft 5A having the precess cams 2 and 2R. And the forward speed change control valve 41
Is connected to the speed change link 9 driven by the step motor 50 in response to a command from a controller (not shown).
A feedback link 5 formed of an L-shaped member that feeds back the tilting of the power roller 1 and the axial displacement of the trunnion 5 from the guide groove 21 of the advancing precess cam 2.
4 (first feedback means), the valve body 143 of the reverse speed change control valve 141 feeds back the tilting of the power roller 1 and the axial displacement of the trunnion from the guide groove 121 of the reverse process cam 2R. It is connected to a feedback link 154 (second feedback means) formed of an L-shaped member.

Then, the forward feedback link 5
4 and the feedback link 154 for reverse travel are swingably supported on the same axis as the swing shaft 4 supported on the valve body 11 side.

On the outer periphery of the swing shaft 4 between the feedback link 54 and the feedback link 154, the torsion coil springs 3 (which urge the feedback links 54 and 154 in mutually opposite directions by a torsional moment about the Y axis in the figure). A first elastic member is interposed.

The torsion coil spring 3 has both ends 3a, 3b
Are engaged in the middle of the arms 56 and 156, respectively.
The end 3a urges the arm 56 in a direction approaching the trunnion shaft 5A, while the end 3b urges the arm 156 in a direction away from the trunnion shaft 5A.

Accordingly, the engaging member 55a of the forward feedback link 54 is pressed by the upper inclined surface 21B of the guide groove 21, while the engaging member 155a of the reverse feedback link 154 is guided by the guide groove. Of the 121, it is pressed by the lower inclined surface 121A in the figure.

Here, in FIG. 1, if the direction of the axial force applied to the trunnion shaft 5A disposed along the Z axis in the figure is positive in the lower part in the figure and negative in the upper part in the figure, the feedback link The biasing force of the torsion coil spring 3 for reducing the play between the precess cam 54 and the precess cam 2 is such that the engaging member 55a urges the precess cam 2 upward in the drawing with the biasing force -F1 corresponding to the lever ratio of the feedback link 54, and The biasing force of the torsion coil spring 3 for reducing the play of the feedback link 154 and the precess cam 2R is the biasing force + F2 according to the lever ratio of the feedback link 154, and the engaging member 155a biases the precess cam 2R downward in the drawing.

Therefore, the axial thrust Fz applied to the trunnion shaft 5A having the precess cams 2 and 2R is the resultant of the urging force of the torsion coil spring 3, so that Fz = -F1
+ F2.

Therefore, each of the engaging members 55a, 155a
Feedback links 54 and 15 such that the absolute value of the force in the Z-axis direction applied to the motor becomes equal to | F1 | = | F2 |
4 and the ends 3a, 3b and the arms 56, 156.
By setting the engagement position and the like of the precess cam 2,
The axial thrust Fz, which is the resultant force of backlash applied to the trunnion shaft 5A having the 2R, can be set to 0, and the axial thrust of each trunnion 5 supporting each power roller 1 Equal to the thrust,
As in the conventional example, it is possible to prevent the axial thrust of the trunnion shaft 5A having the precess cams 2 and 2R from being different only by the urging force of the backlash torsion coil spring 3, thereby preventing the thrust of the trunnion 5 supporting the power roller 1 from being different. Since the deviation is eliminated, the limit of slippage of the power roller 1 held between the input and output disks is prevented from lowering, and the torque transmission capacity of the continuously variable transmission can be improved.

A spring interposed between the valve body 11 and the connecting member 53 to reduce the play of the connecting member 53 of the transmission link 9 and the engaging portions 90 and 91 from the valve body 43 of the shift control valve 41. The urging force Fsf of 70 does not need to press the engagement member 55a against the precess cam 2 as in the above-described conventional example, and only the force for reducing the play around the speed change link 9 is sufficient. The urging force Fsf can be set extremely small, and the driving force of the step motor 50 can be reduced by the reduction of the urging force Fsf of the spring 70, so that downsizing of the step motor can be promoted.

Similarly, the urging force Fsr of the spring 71 for reducing the backlash of the engaging portion 190 connecting the valve body 143 of the shift control valve 141 and the feedback link 154 causes the engaging member 155a to be moved to the precess cam as in the prior art. Since there is no need to press to the 2R, it is only necessary to reduce the play of the engaging portion 190, so that the urging force Fsr can be set extremely small as compared with the conventional example.

Since the minute biasing force from the springs 70, 71 is applied to the feedback links 54, 154 via the engaging portions 90, 190, the engagement members 55
a and 155a press the precess cams 2 and 2R to set the biasing forces -F1 and + F2.
It is sufficient to take into account the minute biasing force from the springs 70 and 71 acting on the spring.

FIG. 2 shows a second embodiment in which the positional relationship between the ends 3a and 3b of the torsion coil spring 3 of the first embodiment is reversed, and the other configuration is the same as that of the first embodiment. The same is true.

The torsion coil spring 3 has both ends 3a, 3b
Are engaged in the middle of the arms 56 and 156, respectively.
The end 3a urges the arm 56 in a direction away from the trunnion shaft 5A, while the end 3b urges the arm 156 in a direction approaching the trunnion shaft 5A.

Therefore, the engaging member 55a of the forward feedback link 54 is pressed by the lower inclined surface 21A in the drawing of the guide groove 21, while the engaging member 155a of the reverse feedback link 154 is the guide groove. 121, the biasing force of the feedback link 54 and the torsion coil spring 3 that closes the play of the precess cam 2 is equal to the biasing force + F1 according to the lever ratio of the feedback link 54. On the other hand, the biasing force of the torsion coil spring 3 for reducing the play of the reverse link 154 and the precess cam 2R is as follows.
Since the biasing force + F2 according to the lever ratio of the feedback link 154 is obtained, and the axial thrust Fz applied to the trunnion shaft 5A including the precess cams 2 and 2R is the resultant of the biasing force of the torsion coil spring 3, Fz = F1− F2
Becomes

Therefore, in the same manner as in the first embodiment, the feedback link 54 is set so that the absolute value of the force in the Z-axis direction applied to each of the engaging members 55a and 155a becomes | F1 | = | F2 | By setting the lever ratio 154, the engagement positions of the ends 3a, 3b and the arms 56, 156, etc., the axial thrust Fz, which is the resultant force of looseness applied to the trunnion shaft 5A having the precess cams 2, 2R, is reduced. 0, and the axial thrust of each trunnion 5 supporting each power roller 1 is:
All of them are equal to the thrust of the hydraulic cylinder 30, and it is possible to prevent the trunnion shaft 5A provided with the precess cams 2 and 2R from having different axial thrusts by the urging force of the backlashed torsion coil spring 3, as in the conventional example. It is.

In the first and second embodiments, an example is shown in which the torsion coil spring 3 is employed as an elastic member for urging the feedback links 54 and 154 around the swing shaft 4 in opposite directions. Although not shown, the swing shaft 4 is formed of a torsion bar, or a coil spring that urges the engaging portions 90 and 190 in opposite directions along the X-axis direction. The same operation and effect can be obtained.

FIGS. 3A and 3B show a third embodiment, in which the reverse feedback link 154, the play of the precess cam 2R and the shift control valve 141 shown in FIG. Valve body 143 and feedback link 15
The biasing direction of the spring 71 for reducing the play of the engaging portion 190 with the engaging portion 4 is reversed, and the other configuration is the same as the above-described conventional example.

In FIG. 3 (B), the valve body 143
A spring 71 ′ (third elastic member) for urging the engaging portion 190 toward the valve body 11 is disposed between the engaging portion 190 connected to the end of the casing 10 and the casing 10. Reverse feedback link 154 connected at section 190
Of the ball 158 is urged toward the valve body 11 by the spring 71 '.

Here, the balls 5 of the feedback links 54 and 154 which are supported coaxially by the swing shaft 4 and are swingable.
8, 158, the force toward the left side in the figure is positive, and the force toward the right side in the figure is negative, the biasing force is applied to the ball 158 of the feedback link 154 for backward movement by the spring 71 '. −Fsr, while FIG.
(A) As shown in FIG.
The fourth ball 58 has a spring 70 (second elastic member).
And a force corresponding to Fsf.

Therefore, the reverse feedback link 154 is urged counterclockwise about the swing shaft 4 in FIG. 3B, and the engaging member 155a provided at the end is inclined upward in the figure. While being pressed by the surface 121B, the forward feedback link 54 is urged clockwise about the pivot shaft 4 and provided at the end, as in the conventional example, as shown in FIG. The engagement member 55a is a lower inclined surface 2 in the figure.
1A.

The precess cams 2 and 2R formed at the ends of the trunnion shaft 5A have + F in the Z-axis direction in FIG.
Since the thrust force of 1, -F2 is applied, the axial thrust force Fz applied to the trunnion shaft 5A is the resultant of the urging forces of the springs 70, 71 ', so that Fz = F1-F2.

Therefore, in the same manner as in the second embodiment, the springs 70, 71 are set so that the absolute value of the force in the Z-axis direction applied to each of the engagement members 55a, 155a is | F1 | = | F2 |. 'Urging force Fs
f, Fsr, lever ratio of the feedback links 54, 154, or the ends 3a, 3b and the arms 56, 156.
By setting the engagement position and the like of the precess cam 2,
The axial thrust Fz, which is the resultant force of backlash applied to the trunnion shaft 5A having the 2R, can be set to 0, and the axial thrust of each trunnion 5 supporting each power roller 1 Equal to the thrust,
As in the conventional example, the trunnion shaft 5A having the precess cams 2 and 2R can prevent the axial thrust from being different by the urging force of the torsion coil spring 3 packed with play.

FIGS. 4A and 4B show a fourth embodiment, in which the forward feedback link 54, the play of the precess cam 2 and the shift control valve 41 shown in FIG. The biasing direction of the spring 70 for reducing the backlash of each part of the valve body 43 and the transmission link 9 is reversed, and the other configuration is the same as that of the conventional example.

In FIG. 4A, a connecting member 53 for connecting the end of the forward-moving valve element 43 and the speed change link 9 to the casing 10 is connected with the connecting member 53 by the valve body 1.
A spring 70 ′ biasing to the first side is provided,
The forward feedback link 154 ball 58 connected at 0 is urged toward the valve body 11 via the speed change link 9 and the connecting member 53 urged by the spring 70 '.

Here, the balls 5 of the feedback links 54 and 154 which are supported coaxially by the swing shaft 4 and are swingable.
8 and 158, the force in the X-axis direction in the drawing is positive in the same manner as described above, and the force in the right direction in the drawing is negative.
4B, a force corresponding to the biasing force −Fsf by the spring 70 ′ is applied to the ball 1 of the feedback link 154 for reverse movement as shown in FIG.
A biasing force + Fsr is applied to 58 by a spring 71.

Therefore, the forward feedback link 54 is urged counterclockwise around the pivot shaft 4 in FIG. 4A, and the engaging member 55a provided at the end is inclined upward in the figure. While being pressed by the surface 21B, the reverse feedback link 154 is urged clockwise about the swing shaft 4, as in the conventional example, as shown in FIG.
The engaging member 155a provided at the end is the lower inclined surface 12 in the figure.
1A.

The precess cams 2 and 2R formed at the end of the trunnion shaft 5A have + F in the Z-axis direction in the drawing.
1 and −F2 are applied, respectively, so that the axial thrust Fz applied to the trunnion shaft 5A is reduced by the springs 70 ′ and 7 ′.
Fz = −F1 + F2, because the resultant force is the urging force due to 1.

Therefore, in the same manner as in the first embodiment, the spring 70 ', the absolute value of the force in the Z-axis direction applied to each of the engaging members 55a and 155a is | F1 | = | F2 | 71 urging force Fs
f, Fsr, lever ratio of the feedback links 54, 154, or the ends 3a, 3b and the arms 56, 156.
By setting the engagement position and the like of the precess cam 2,
The axial thrust Fz, which is the resultant force of backlash applied to the trunnion shaft 5A having the 2R, can be set to 0, and the axial thrust of each trunnion 5 supporting each power roller 1 Equal to the thrust,
As in the conventional example, the trunnion shaft 5A provided with the precess cams 2 and 2R can prevent the axial thrust from being different by the urging force of the backlashed torsion coil spring 3.

In the third and fourth embodiments, one end of each of the springs 70 ′ and 71 ′ is connected to the casing 10.
However, the present invention is not limited to this, and any fixing member may be used.

[Brief description of the drawings]

FIG. 1 is a schematic perspective view of a shift control device according to an embodiment of the present invention.

FIG. 2 is a schematic perspective view of a transmission control device according to a second embodiment.

FIGS. 3A and 3B are cross-sectional views of a shift control device according to a third embodiment, wherein FIG. 3A shows a forward shift control valve, and FIG. 3B shows a reverse shift control valve;

4A and 4B are cross-sectional views of a shift control device according to a fourth embodiment, wherein FIG. 4A shows a forward shift control valve, and FIG. 4B shows a reverse shift control valve.

FIG. 5 is a schematic perspective view of a shift control device, showing a conventional example.

6A and 6B are cross-sectional views showing a conventional example, wherein FIG. 6A shows a forward shift control valve, and FIG. 6B shows a reverse shift control valve.

FIG. 7 is a conceptual diagram showing the vicinity of a trunnion of a toroidal-type continuously variable transmission in a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Power roller 2, 2R Precess cam 3 Torsion coil spring 4 Oscillating shaft 5 Trunnion 5A Trunnion shaft 6 Pivot shaft 9 Shift link 10 Casing 21 Guide groove 30 Hydraulic cylinder 31 Piston 33H, 33L Oil chamber 34H, 34L Oil chamber 41 Shift control valve 42 43 valve body 50 step motor 51 lead screw mechanism 52 slider 53 connecting member 53a pin 54 feedback link 55, 56 arm 57 cylinder portion 58 ball

Claims (5)

[Claims] 1. A plurality of roller supporting members each rotatably supporting a plurality of power rollers sandwiched by an input / output disk, being rotatable about a predetermined axis, and capable of being displaced in an axial direction. Forward and reverse speed change control valves for controlling hydraulic pressure to hydraulic actuators respectively driven in the axial direction, a cam formed on one of the plurality of roller support members, and a roller responsive to the cam. First feedback means for transmitting a displacement about the axis of the support member or in the axial direction to the forward shift control valve; and transmitting a displacement about the axis of the roller support member or the axial direction of the roller support member to the reverse shift control valve in response to the cam. A transmission control device for a toroidal-type continuously variable transmission, comprising: a first feedback unit and a second feedback unit. Shift control system of the toroidal type continuously variable transmission characterized by comprising biasing means toward the opposite direction to bias so as to press the cam. 2. The biasing means according to claim 1, wherein said first feedback means and said second feedback means set an equal absolute value of a force pressing said cam in mutually opposite directions. 3. The shift control device for a toroidal-type continuously variable transmission according to claim 1. 3. The apparatus according to claim 1, wherein said urging means comprises a first elastic member which urges said first feedback means and said second feedback means in mutually opposite directions. Shift control device for toroidal type continuously variable transmission. 4. The first feedback means includes a first link that abuts the cam at one end, and a first link that is connected to the forward speed change control valve at the other end, and wherein the second feedback means is connected to the cam at one end. A second link connected to the reverse gearshift control valve at the other end while supporting the first and second links coaxially and swingably, and the first elastic member includes: The toroidal-type continuously variable transmission according to claim 3, wherein the torsional moment is provided between the first link and the second link to apply a torsional moment in opposite directions to the first link and the second link. Gear shift control device. 5. The device according to claim 1, wherein the urging unit includes a second elastic member for urging the first feedback unit, and a third elastic member for urging the second feedback unit. The shift control device for a toroidal-type continuously variable transmission according to claim 1.