JP3267196B2 - Transmission control device for toroidal type continuously variable transmission - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to 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 used in a vehicle such as an automobile, the shift control is performed by hydraulic pressure. In the toroidal-type continuously variable transmission, torque shift is suppressed. Proposed Japanese Patent Application Hei 8-30
No. 8331 and the like.

As shown in FIGS. 9 and 10, the speed change control is performed by independent speed change control valves at the time of forward movement and at the time of reverse movement. Power rollers 3 are provided on opposing surfaces of input / output disks 6A and 6B. The power roller 3 is supported by a trunnion as a roller support member (not shown), and a shaft portion 4A provided below the trunnion is connected to a hydraulic cylinder (not shown) in the axial direction (Z axis in the figure). Direction), and is supported so as to be rotatable about an axis, and continuously changes the tilt angle of the power roller 3. One shaft portion 4 of a plurality of trunnions supporting power roller 3
In A, the precess cam 2 for forward movement and the precess cam 2R for reverse movement are integrally provided, and the speed change control valve 7 for forward movement and the speed change control valve 7R for reverse movement are arranged in parallel.

[0004] At the lower end of the trunnion shaft 4A, an axial displacement and a displacement around the shaft are provided with a feedback link 5 for forward movement.
The precess cams 2 and 2R for transmitting the precess cam 4 and the reverse feedback link 154 'are integrally formed, and the inclined surfaces 20, 2 formed on the precess cam 2 are formed integrally.
OR guides engagement members 55a and 155a provided on feedback links 54 'and 154'. The forward feedback link 54 'supported by the swing shaft 60 along the Y axis displaces the ball 58 provided at the other end via the swing shaft 60 in the X axis direction in the drawing.

The ball 58 is engaged with an engagement portion 90 'formed at one end of a speed change link 9' connecting the speed control valve 7 for sucking and discharging hydraulic oil to and from the hydraulic cylinder when the vehicle advances, and a step motor 50. Engage.

On the other hand, the other end of the transmission link 9 'is provided with an engaging portion 91 which engages with a pin 52a protruding from a slider 52 driven in the axial direction by a step motor 50 as an actuator via a speed reduction mechanism 51. Is formed, and
At a predetermined position in the middle of the speed change link 9 ', the connecting member 53
The rod portion 80 of the spool 8 that slides on the inner periphery of the transmission control valve 7 is connected via the pin 53a.

On the other hand, the other end of the reverse feedback link 154 'for reverse is connected to the spool 8R of the reverse speed change control valve 7R via the swing shaft 60.

Here, when the power roller 3 tilts to the Lo side, the guide groove 20 of the precess cam 2 for forward movement also rotates the precess cam 2 attached to the shaft portion 4A of the trunnion to the Lo side in the drawing. While the joining member 55a is lowered, when the precess cam 2 is rotated to the Hi side, the engaging member 55a is raised, and the speed change link 9 'connected to the ball 58 at the other end is Lo in the figure according to the tilt of the power roller 3. Alternatively, it is driven to the Hi side.

Accordingly, the step motor 50 is driven by the slider 5 in accordance with the target speed ratio from a controller (not shown).
2, the spool 8 moves according to the displacement of one end of the transmission link 9 ′, and the supply pressure port 17 of the transmission control valve 7.
P is communicated with the port 17H or 17L, and pressurized oil is supplied to an oil chamber on the Hi or Lo side of a hydraulic cylinder (not shown) to drive the hydraulic cylinder.
Changes the gear ratio by tilting according to the axial displacement of the trunnion caused by the drive of the hydraulic cylinder, and this tilting motion is transmitted to the other end of the speed change link 9 'via the shaft portion 4A of the trunnion and the feedback link 54'. When the transmission is performed and the target speed ratio and the actual speed ratio match, the spool 8 is connected to the ports 17H and 17H.
It returns to the neutral position to seal L and the supply pressure port 17P. The speed change link 9 'performs the above operation every time the speed changes, and swings within the range of the angle α in FIG.

When the vehicle is moving backward, the hydraulic pressure is controlled by the precess cam 2R, the feedback link 154 ', and the shift control valve 7R in the same manner as when the vehicle is moving forward.

Here, between the connecting member 53 and the shift control valve 7, there is a play between the engaging portions 90 'and 91 of the shift link 9' and the ball 58 and the pin 53a, or a play of the feedback link 54 '. In order to accurately perform feedback control by eliminating the spring 81, a spring 81 for urging the connecting member 53 downward in FIG. 10 with a predetermined force F along the X-axis direction is interposed. Are always in contact with the ball 58 and the pin 52a, respectively, and the engaging portion 55 of the feedback link 54 'is changed according to the force acting on the ball 58.
a is pressed by the inclined surface 20 of the precess cam 2, and the influence of the play is eliminated as much as possible to improve the accuracy of the feedback control.

[0012]

However, in the above-mentioned conventional example, the transmission link 9 'has a structure in which the transmission link 9' is swingably supported about a pin 53a provided on the connecting member 53 as an axis. (Not shown) and pin 53
A predetermined gap is formed between the gap and a. On the other hand, as shown in FIG. 10 and FIG.
Is displaced in the X-axis direction in the drawing from the Lo side to the Hi side by the stepping motor 50, while the engagement portion 90 ′ driven by the ball 58 of the feedback link 54 ′ also depends on the actual speed ratio of the power roller 3. As shown in FIG. 11, the shifting movement of the transmission link 9 ′ is centered on the Y axis parallel to the rotation axis C of the input / output disks 6 A and 6 B. The joint 90 'moves up and down.

Here, the transmission link 9 'is connected to a spring 81.
As a result, the ball 58 is urged downward by the force F in FIG.
As shown in FIG. 11, the inclination of the transmission link 9 ', that is, the engagement portion 90'
A component force F1 in the Y-axis direction is generated according to the angle of contact with
When the actual gear ratio is at the maximum Lo, the ball 58 is at the position indicated by the solid line in the figure, and the component force at this time is −F toward the right side in the figure.
When the actual gear ratio is at the maximum Hi, the ball 5
8 is at the position 58H in the figure, and the component force at this time is F1 toward the left side in the figure. Then, the ball 58 is almost halfway between the highest Hi and the lowest Lo, and at a position of 58M where the axis of the transmission link 9 'is orthogonal to the X axis, the component force F1 = 0, and the intermediate position 58M is a boundary. Since the sign of the component force F1 applied to the transmission link 9 'is reversed, the transmission link 9' is displaced in the Y-axis direction in the figure according to the gap between the coupling member 53 and the pin 53a. 58 is X in the figure
Since this is equivalent to displacement in the axial direction, the feedback gain for transmitting the actual speed ratio from the precess cam 2 to the speed change control valve 7 fluctuates around the intermediate position 58M, and the accuracy of feedback control is reduced. there were.

SUMMARY OF THE INVENTION The present invention has been made in view of the above problems, and has as its object to suppress a play between a transmission link and a feedback link to prevent a change in a feedback gain.

[0015]

According to a first aspect of the present invention, a power roller sandwiched by an input / output disk and rotatably supported is rotatably supported, and is rotatable about a predetermined axis and axially displaceable. A roller support member, a shift control valve for controlling a hydraulic pressure to a hydraulic cylinder that drives the roller support member in the axial direction, a cam provided with a shaft portion that rotates around the axis of the roller support member, and a cam provided with the cam. Feedback means for transmitting an actual gear ratio to the shift control valve via a responsive feedback link; an actuator for driving a shift link engaged with the shift control valve and the feedback means; and shifting the shift link in a predetermined direction. A shift control device for a toroidal-type continuously variable transmission, comprising a biasing means for biasing to absorb backlash with at least a feedback means. And feedback means engages through the engagement member comprises a feedback gain stabilization means a component force of the urging means is set to be always constant direction generated in the engaging member.

According to a second aspect of the present invention, in the first aspect, the feedback gain stabilizing means is provided so that the component force of the urging means generated in the engagement member is always in a constant direction. Set the swing range.

According to a third aspect of the present invention, in the first aspect, the feedback gain stabilizing means is provided so that a component force of the urging means generated in the engaging member is always in a constant direction. It is composed of an inclined portion formed on the member.

In a fourth aspect based on the first aspect, the feedback gain stabilizing means includes a transmission link such that a component force of the urging means generated in the engaging member is always in a constant direction. Is formed by the bent portion provided in.

[0019]

According to the first aspect of the present invention, the feedback means engages with the speed change link to transmit the actual speed ratio according to the rotation of the roller support member to the speed change control valve. Are connected via an engagement member formed on the feedback link and the speed change link,
By urging the speed change link in a predetermined direction, the play of the engagement member and the feedback link is absorbed, but a component force of the urging means is generated in the engagement member. Here, since the feedback gain stabilizing means always sets the component force in a fixed direction, the connection or engagement portion between the shift control valve and the shift link is constantly pressed in a fixed direction. To
Since the direction of the component force does not change, it is possible to prevent the occurrence of backlash between the shift control valve and the shift link and change of the feedback gain, thereby improving the shift control accuracy of the toroidal type continuously variable transmission. It becomes possible.

According to a second aspect of the present invention, the speed change control valve and the speed change link are set by setting the swing range of the speed change link such that the direction of the component force of the urging means generated in the engagement member is constant. The backlash is reliably prevented from occurring during the period, and the fluctuation of the feedback gain can be prevented.

According to the third aspect of the present invention, the inclined portion is provided in the engaging member which engages with the feedback link so that the direction of the component force of the urging means can be always constant, and the shape of the engaging member can be reduced. Since only a change is required, the present invention can be easily applied to the same shift control device as in the conventional example, and there is no need to change the design of an oil pan or the like in which the shift control device is housed, thereby reducing manufacturing costs. .

According to the fourth aspect of the present invention, since the transmission link is provided with a bent portion, the component force received by the engaging member can be always constant, and only the shape of the transmission link needs to be changed. It can be easily applied to the same shift control device as the example,
It is not necessary to change the design of the oil pan or the like in which the shift control device is housed, and the manufacturing cost can be reduced.

[0023]

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

FIGS. 1 to 4 show an example in which the present invention is applied to a shift control device for a toroidal-type continuously variable transmission similar to the latter conventional example. And a duplicate description is omitted.

In one of the plurality of trunnions, a forward precess cam 2 and a reverse precess cam 2R are integrally formed at the lower end of the shaft portion 4A.

In FIGS. 1 and 2, a forward speed control valve 7 is disposed on the valve body 70 on the right side (the output disk 6B side) of the shaft 4A, and on the left side (the input disk 6A side) of the shaft 4A. ) Is provided with a reverse speed change control valve 7R. The precess cam 2 for forward movement is disposed on the side of the shift control valve 7 for forward movement, while the precess cam 2R for reverse movement is disposed facing the shift control valve 7R for reverse movement.

Each of the precess cams 2 and 2R is formed with an inclined surface which engages with engaging members 55a and 155a projecting from the forward feedback link 54 and the reverse feedback link 154, respectively. In the case of the precess cam 2 for advance, FIG.
As shown in (B), the slope 20 such that the engagement member 55a rises as the gear ratio changes from the Lo side to the Hi side.
Is formed, the ball 58 at the other end is displaced in the X-axis direction in the drawing, and as shown in FIG. 6B, the ball 58 is displaced from the Lo side position to the Hi side position on the precess cam 2 side. .

Similarly, the reverse precess cam 2R is similarly formed with an inclined surface (not shown) such that the engaging member 155a moves up and down as the speed ratio changes from the Lo side to the Hi side. The spool 8R of the connected reverse speed change control valve 7R is driven in the X-axis direction.

Here, as shown in FIGS. 1 to 4, the forward feedback link 54 is provided at one end with the precess cam 2.
And an arm 55 extending in the X-axis direction in the figure and an arm 56 also extending in the Z-axis direction through a cylindrical member 57. An engaging member 55a that engages with the precess cam 2 protrudes from the end of the arm 55 and is engaged with an engaging portion 90 of the transmission link 9 at the lower end of the arm 56. Ball 58 is fixedly mounted. The engaging portion 90 is formed in a U-shape in the XY plane, and is in sliding contact with the ball 58 on the inner periphery.

The feedback link 54 is swingably supported around the Y axis via a swing shaft 60 inserted through the inner periphery of the cylindrical member 57.

A swing shaft 60 arranged along the Y-axis direction
Are brackets 71, 72 formed on the valve body 70.
In addition to the L-shaped forward feedback link 54, the reverse feedback link 1
54 is also supported coaxially and swingably around the Y axis.

That is, as shown in FIG.
Are provided with different outer diameters via the stepped portion 60a, and a screw is formed at an end (left side in the figure) on the side with the smaller outer diameter to form a bracket 71.
And screwed to the valve body 70 via a nut screwed to the end penetrating the bracket 71, and the end (the right side in the figure) having a large outer diameter is inserted into the through hole of the bracket 72. Is fitted. The feedback links 54 and 154 are inserted between the brackets 71 and 72 via a collar 59 having a predetermined thickness. By adjusting the distance between the end face of the bracket 71 and the stepped portion 60a, the feedback link 54, 154 is supported swingably while minimizing backlash in the axial direction.

Here, as shown in FIGS. 1 and 5, the sign of the component force F1 acting on the engaging portion 90 of the speed change link 9 in the Y-axis direction is negative, Assuming that the sign of the component force toward the positive direction is positive, the relationship between the arms 55 and 56 constituting the feedback link 54 is such that the mounting angle θ around the axis is set to a predetermined obtuse angle as shown in FIG. Further, the displacement of the transmission link 9 by the feedback link 54 and the step motor 50 is determined when the ball 58 is displaced most toward the precess cam 2 as shown in FIGS. H
Y acting on the engaging portion 90 of the speed change link 9 at the time of the i speed ratio
While the axial component force F1 is set to be equal to or less than 0 (here, F1 = 0), when the ball 58 is farthest from the precess cam 2, that is, the position of the ball 58 is as shown by a solid line in the figure. At the time of the maximum Lo speed ratio, the speed change link 9
The component force F1 in the Y-axis direction acting on the engaging portion 90 is a predetermined negative value −
F1 is set.

The operation as described above will now be described.

When the stepping motor 50 drives the engaging portion 91 of the transmission link 9 in the X-axis direction toward the target transmission ratio,
Pressure oil is supplied to a hydraulic cylinder (not shown) by the displacement of the spool 8, and the power roller 3 is tilted in accordance with the axial displacement of the trunnion, and the engaging portion 90 of the speed change link 9 is moved through the X-axis When the target gear ratio and the actual gear ratio match, the spool 8 returns to the neutral position.

In this shifting operation, for example, when the gear ratio is the maximum L
When changing from o to the highest Hi, as shown in FIGS. 1 and 5, the spring 81 urges the speed change link 9 along the X-axis direction, so that the engagement portion 90 driven by the ball 58 of the feedback link 54. , A component force F1 in the Y-axis direction is generated in accordance with the inclination of the engagement portion 90. However, the component value F1 = 0 at the lowest Lo speed ratio and the component force F1 = 0 at the highest Hi speed ratio. .

As a result, unlike the prior art, the component force applied to the speed change link 9 in the Y-axis direction does not change from positive to negative or from negative to positive, and the pin 53a of the connecting member 53 and the speed change link 9 Since the connecting portion is always urged in a fixed direction, no play is caused, and it is possible to reliably prevent the feedback gain of the actual speed ratio from the precess cam 2, the feedback link 54 and the engaging portion 90 from changing, This makes it possible to improve the accuracy of the shift control.

In the above embodiment, the component force F1 at the maximum Hi gear ratio is set to be 0. However, if F1 <0, the component force F1 applied to the engaging portion 90 is always a negative value.
The play between the pin 53a and the speed change link 9 can be reliably prevented, and although not shown, even if the component force F1 applied to the engagement portion 90 is set to be always positive, the same applies. It is possible to reliably prevent rattling.

FIG. 7 shows a second embodiment, in which a ball 58 is used.
The inclined portion 90A is formed in the engaging portion 90 of the speed change link 9 which engages with the feedback link 54 through the other portion, and the other configuration is the same as that of the first embodiment.

The inclined portion 90A is formed at a predetermined angle so as to be in sliding contact with the ball 58 on the inner periphery of the engaging portion 90 formed of a U-shaped member. The angle of the inclined portion 90A is determined when the ball 58 is at the maximum Hi speed ratio at the position of 58H.
The component force F1 acting on the engaging portion 90 in the Y-axis direction is 0,
At the time of the gear ratio, the component force F1 is set to be a predetermined negative value -F1.

Therefore, similar to the first embodiment,
Transmission link 9 and coupling member 5 due to change in sign of component force F1
The play of the third pin 53a can be prevented, and the accuracy of the shift control can be improved.

In this case, the relative positional relationship between the transmission link 9 and the feedback link 54 and the slider 52 of the step motor 50 can be set in the same manner as in the conventional example. By setting the swing range of No. 9 to α similar to that of the conventional example, it is not necessary to change the design of an oil pan or the like in which the shift control device is housed, and it is possible to reduce the manufacturing cost.

FIG. 8 shows a third embodiment, in which an engaging portion 90 and a pin 5 are used instead of the inclined portion 90A of the second embodiment.
The transmission link 9 between 3a is provided with a bent portion 9A,
Other configurations are the same as those of the second embodiment.

The bent portion 9A is connected to the feedback link 54
When the ball 58 is at the highest Hi gear ratio at the position 58H in the figure, the component force F1 in the Y-axis direction acting on the engaging portion 90 formed by the U-shaped member is a negative value -F1. , And bends upward in the drawing such that the component force F1 becomes a predetermined negative value -F2 at the time of the maximum Lo speed ratio. Note that the component force is -F1> -F2.

Therefore, the component force F1 applied to the speed change link 9 via the engaging portion 90 is always a negative value, and similarly to the first embodiment, the speed change link 9 and the connecting member 53 are changed by changing the sign of the component force F1. The play of the pin 53a is reliably prevented, and the accuracy of the shift control can be improved.

Also in this case, the relative positional relationship between the transmission link 9 and the feedback link 54 and the slider 52 of the step motor 50 can be set in the same manner as in the conventional example. By setting the swing range of No. 9 to α similar to that of the conventional example, it is not necessary to change the design of an oil pan or the like in which the shift control device is housed, and it is possible to reduce the manufacturing cost.

[Brief description of the drawings]

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

FIG. 2 is a front view of a main part of the transmission control device, also viewed from the bottom side of the transmission.

FIG. 3 is a side view of FIG. 2;

FIG. 4 is a sectional view taken along the line AA of FIG. 2;

FIG. 5 is a schematic bottom view showing a relationship between a ball and a speed change link.

FIG. 6 is an explanatory view showing a relationship between a precess cam and a feedback link, wherein (A) is a bottom view of the precess cam;
(B) is a side view of arrow (B) of (A), showing the relationship between the forward precess cam and the feedback link.

FIG. 7 is a bottom view of an essential part showing a second embodiment and showing a relationship between a ball and a speed change link.

FIG. 8 is a schematic bottom view showing the third embodiment and showing a relationship between a ball and a speed change link.

FIG. 9 is a schematic perspective view of a shift control device for a toroidal-type continuously variable transmission, showing a conventional example.

FIG. 10 is a schematic bottom view of a transmission control device, similarly showing a conventional example.

FIG. 11 is a bottom view showing the relationship between the ball of the feedback link and the speed change link.

[Explanation of symbols]

 2, 2R Precess cam 3 Power roller 4A Shaft 6A Input disk 6B Output disk 7 Shift control valve 7R Reverse shift control valve 8, 8R Spool 9 Shift link 50 Step motor 53 Connecting member 54, 154 Feedback link 55, 56, 155, 156 Arm 55a, 155a Engagement member 58 Ball 60 Swing shaft 70 Valve body 81 Spring

Claims (4)

(57) [Claims] A roller support member rotatably supporting a tiltable power roller sandwiched by an input / output disk and rotatable about a predetermined axis and displaceable in an axial direction; and the roller support member. A shift control valve for controlling a hydraulic pressure to a hydraulic cylinder that drives the shaft in the axial direction; a cam provided on a shaft for rotating the roller support member around the axis; and a feedback link responsive to the cam. Feedback means for transmitting the actual speed ratio to the valve; an actuator for driving a speed change link engaged with the speed change control valve and the feedback means; and play of at least the feedback means by urging the speed change link in a predetermined direction. In the transmission control device for a toroidal-type continuously variable transmission provided with an urging means for absorbing the force, the transmission link and the feedback means are engaged. A toroidal-type continuously variable transmission including a feedback gain stabilizing unit that engages via a member and sets a component force of an urging unit generated in the engaging member to be always in a constant direction. Transmission control device. 2. The feedback gain stabilizing means sets a swing range of a speed change link such that a component force of an urging means generated in an engagement member is always in a constant direction. The shift control device for a toroidal-type continuously variable transmission according to claim 1. 3. The feedback gain stabilizing means is an inclined portion formed on the engaging member such that a component force of the urging means generated in the engaging member is always in a constant direction. The shift control device for a toroidal-type continuously variable transmission according to claim 1. 4. The feedback gain stabilizing means is a bent portion provided on a speed change link such that a component force of an urging means generated in an engaging member is always in a constant direction. Item 3. A shift control device for a toroidal-type continuously variable transmission according to item 1.